WO2013065792A1 - クロスフローファン - Google Patents
クロスフローファン Download PDFInfo
- Publication number
- WO2013065792A1 WO2013065792A1 PCT/JP2012/078353 JP2012078353W WO2013065792A1 WO 2013065792 A1 WO2013065792 A1 WO 2013065792A1 JP 2012078353 W JP2012078353 W JP 2012078353W WO 2013065792 A1 WO2013065792 A1 WO 2013065792A1
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- WIPO (PCT)
- Prior art keywords
- arc
- pressure surface
- blade
- peripheral side
- radius
- 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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
- F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
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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
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
- F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
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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
- F24F1/0025—Cross-flow or tangential 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
- 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
- F05D2240/304—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 trailing edge of a rotor blade
Definitions
- the present invention relates to a cross flow fan and an air conditioner including the cross flow fan.
- FIG. 15 shows the cross-sectional shape of the blades of the crossflow fan disclosed in Patent Document 1 and Patent Document 2.
- the cross-sectional shape of the blade 500 is a crescent shape that is bilaterally symmetric about the center line (dashed line), thick at the center, and thin at both ends.
- the radii of the outer peripheral side arc Ro and the inner peripheral side arc Ri of the blades are equal, and the convex surface side arc Rs and the concave surface side arc Rp of the blade are each constituted by a single circular arc, Rp> Rs.
- the cross-flow fan blade has a crescent-shaped cross section, as shown in FIG. 16, in the flow passage between the plurality of blades, the diameter Di of the flow passage on the inner peripheral side of the blade is the outer periphery of the blade. Since the change in the flow path width from the inner peripheral side to the outer peripheral side of the blade is large, the fluctuation of the air flow speed becomes large. Specifically, as shown in FIG.
- the flow path width on the outer peripheral side is narrowed by 24.3%, and the flow velocity is increased on the blowout side. Therefore, the turbulence of the air flow is large, the air flow becomes difficult to flow along the flow path, and the flow separation occurs on the discharge side negative pressure surface. As a result, power loss due to the fan increases.
- the problem of the present invention is to increase the flow path width between adjacent blades on the outer peripheral side of the fan, and to reduce the reduction rate of the flow path width between adjacent blades from the inner peripheral side to the outer peripheral side of the blades.
- An object of the present invention is to provide a cross-flow fan in which fluctuations in the air speed from the inner periphery side to the outer periphery side of the blades are reduced and power loss by the fan is small.
- the cross flow fan according to the first aspect includes a support plate portion and a wing portion formed by a plurality of blades.
- the plurality of blades are arranged on the support plate portion at a predetermined interval.
- the cross-sectional shape in the longitudinal direction of the blade includes a suction surface arc that forms a convex suction surface, a pressure surface arc that forms a concave pressure surface, a first end of the suction surface arc, and a first end of the pressure surface arc.
- an outer peripheral arc connecting the second end of the negative pressure surface arc and the second end of the pressure surface arc.
- the radius of the pressure surface arc is larger than the radius of the suction surface arc
- the radius of the inner circumferential arc is larger than the radius of the outer circumferential arc
- the maximum thickness portion of the blade thickness is 40 from the inner circumferential arc in the longitudinal direction. It is at the position of ⁇ 60%.
- the blades are arranged so that the inner circumference side arc is located on the inner circumference side of the support plate and the outer circumference side arc is located on the outer circumference side of the support plate, and the flow path width between the plurality of blades is supported. It gradually decreases from the inner peripheral side to the outer peripheral side of the plate.
- wing becomes thin and the flow path width between adjacent blades in the outer peripheral side of a fan can be enlarged.
- the flow path width between adjacent blades gradually decreases from the inner peripheral side to the outer peripheral side of the blades, and fluctuations in the air speed from the inner peripheral side to the outer peripheral side of the blades can be reduced, resulting in a decrease in fan blowing performance. Can be suppressed.
- the crossflow fan according to the second aspect of the present invention is the crossflow fan according to the first aspect of the present invention, wherein the suction surface of the blade is configured by a single suction surface arc Rs, and the pressure surface is a plurality of pressure surface arcs.
- Rpn is constituted by Rp1, Rp2,... Rpn, and radii rp1, rp2,... Pn of the plurality of pressure surface arcs Rp1, Rp2,.
- the pressure surface of the blade is composed of a plurality of arcs, and the radius of the plurality of arcs is larger than the radius of the suction surface arc.
- the reduction rate of the flow path width between the plurality of blades on the inner peripheral side of the blades becomes smaller, fluctuations in the air speed from the inner peripheral side to the outer peripheral side of the blades can be reduced, and the fan blowing performance The decrease can be suppressed.
- the crossflow fan according to the third aspect of the present invention is the crossflow fan according to the second aspect of the present invention, wherein the sizes of the radii rp1, rp2, ... rpn of the plurality of pressure surface arcs Rp1, Rp2, ... Rpn are , Rp2>rp3>...>Rpn> rp1, and the thickness of the blade is gradually reduced from the maximum thickness portion toward the outer peripheral arc Ro.
- the pressure surface of the blade is composed of a plurality of arcs, and the thickness of the blade is gradually reduced from the maximum thickness portion toward the outer peripheral arc Ro.
- the reduction rate of the flow path width between the plurality of blades from the inner peripheral side to the outer peripheral side of the blades becomes smaller, and fluctuations in the air speed from the inner peripheral side to the outer peripheral side of the blades can be reduced. And the fall of the ventilation performance of a fan can be suppressed.
- a crossflow fan according to a fourth aspect of the present invention is the crossflow fan according to any one of the first to third aspects of the present invention, wherein the maximum reduction rate of the channel width between the plurality of blades is 20 % Or less.
- An air-conditioned indoor unit includes the cross-flow fan according to claim 4, a heat exchanger, and a casing.
- the air conditioner according to the sixth aspect of the present invention includes the indoor unit according to the fifth aspect of the present invention, the outdoor unit, and a pipe connecting the indoor unit and the outdoor unit.
- the crossflow fan according to the present invention by reducing the reduction rate of the flow path width between the plurality of blades, it is possible to reduce fluctuations in the air speed from the inner peripheral side to the outer peripheral side of the blades, and the fan blowing performance Can be suppressed.
- FIG. 1 is an external perspective view of a cross flow fan according to an embodiment of the present invention.
- the perspective view which shows an impeller. 1 is a schematic cross-sectional view of a blade of Example 1.
- FIG. 3 is a schematic cross-sectional view illustrating a flow path between a plurality of blades including the blades of Example 1. Schematic showing the change of the flow path width between several blades provided with the blade
- FIG. FIG. 4 is a schematic cross-sectional view of a blade of Example 2.
- FIG. 6 is a schematic cross-sectional view of a blade of Example 3. Schematic showing the change of the flow path width between several blades provided with the blade
- FIG. 6 Schematic showing the absolute speed between several blades provided with the conventional crescent moon-shaped blade
- wing The schematic sectional drawing showing the flow path between several blades provided with the conventional crescent moon-shaped blade
- FIG. 1 shows the appearance of an air conditioner equipped with a cross flow fan according to an embodiment of the present invention.
- This air conditioner is a device for supplying conditioned air into the room.
- the air conditioner includes an indoor unit 1 attached to an indoor wall surface and the like, and an outdoor unit 2 installed outside the room.
- An indoor heat exchanger is accommodated in the indoor unit 1, and an outdoor heat exchanger (not shown) is accommodated in the outdoor unit 2.
- a refrigerant circuit is configured by connecting the indoor heat exchanger and the outdoor heat exchanger by the refrigerant pipe 3.
- An indoor unit 1 shown in FIG. 2 is a wall-mounted indoor unit that is attached to an indoor wall surface or the like, and mainly includes an indoor unit casing 5, an indoor heat exchanger 8, and a cross flow fan 10.
- the indoor unit casing 5 accommodates an indoor heat exchanger 8, a cross flow fan 10, and the like.
- the indoor unit casing 5 is formed with an air intake 6 and an air outlet 4 for air conditioning.
- the air intake 6 is provided in the upper part and the front part of the indoor unit casing 5 and is an opening for taking indoor air into the indoor unit casing 5.
- the air outlet 4 is provided in the lower front part of the indoor unit casing 5.
- a horizontal flap 7 is provided in the vicinity of the air outlet 4 so as to cover the air outlet 4.
- the horizontal flap 7 is rotationally driven by a flap motor (not shown) to change the air guiding direction and open / close the air outlet 4.
- the indoor heat exchanger 8 includes a heat transfer tube that is bent back and forth at both ends in the longitudinal direction and a plurality of fins that are inserted through the heat transfer tube, and performs heat exchange with the air that is in contact therewith.
- the indoor heat exchanger 8 functions as a condenser during the heating operation, and functions as an evaporator during the cooling operation.
- the cross flow fan 10 has a motor (not shown) as a drive mechanism, and an impeller 11 that rotationally drives air in the A1 direction shown in FIG. 4 by the motor.
- the cross flow fan 10 sucks air into the indoor unit casing 5 from the air intake 6 and passes the indoor heat exchanger 8, and then blows air out of the indoor unit casing 5 through the air outlet 4. Arranged to be able to.
- the cross flow fan 10 is disposed between the indoor heat exchanger 8 and the air outlet 4 in the air flow direction in the indoor unit casing 5.
- a guide portion 9 is disposed on the back side of the impeller 11. The guide portion 9 air-flows the air flow blown into the space S2 between the impeller 11 and the air outlet 4 after flowing through the impeller 11 from the space S1 between the indoor heat exchanger 8 and the impeller 11.
- a tongue portion 15 is provided on the front side of the impeller 11 for preventing the airflow blown into the space S2 from flowing back into the space S1.
- the air in the indoor unit casing 5 flows so as to be orthogonal to the rotational axis O of the impeller 11 by rotationally driving the impeller 11 of the cross flow fan 10.
- An air flow from the space S ⁇ b> 1 to the space S ⁇ b> 2 that is a flow blown out from the air outlet 4 can be generated.
- air is sucked into the indoor unit casing 5 from the air intake 6, and the air sucked into the indoor unit casing 5 passes through the indoor heat exchanger 8.
- the air is cooled or heated by the air and is blown out of the indoor unit casing 5 from the air blowout port 4 through the impeller 11 of the cross flow fan 10.
- the configuration of the impeller 11 of the cross flow fan 10 will be described.
- the cross flow fan 10 has a rotor-like external shape elongated in the rotation axis direction that is the rotation axis O direction of the cross flow fan 10.
- the cross flow fan 10 mainly includes a disk-shaped circular support plate 12 provided on the first end surface, a disk-shaped circular support plate 50 provided on the second end surface, a plurality of impellers 11, And a disc-like circular support plate 51 provided between the plurality of impellers 11, and these are joined to each other.
- the circular support plate 12 constitutes the first end in the rotation axis direction
- the disc-shaped circular support plate 50 constitutes the second end in the rotation axis direction.
- the circular support plate 12 rotates around the rotation axis (that is, the rotation axis O) of the impeller 11.
- a shaft portion 58 as a rotation shaft of the cross flow fan 10 is provided in the center of the circular support plate 12.
- one or more impellers 11 are provided between the disc-shaped circular support plate 12 provided on the first end surface and the disc-shaped circular support plate 50 provided on the second end surface (here, 9) are arranged.
- the disc-shaped circular support plate 50 is provided with a plurality of blades 100, and the circular support plate 50 has a rotation axis (that is, a rotation axis O) of the cross flow fan 10. ).
- the plurality of blades 100 are arranged in the circumferential direction of the circular support plate 50.
- each blade 100 is arranged on the circular support plate 50 so as to be inclined at a predetermined angle toward the rotation direction of the cross flow fan 10 (here, the A1 direction shown in FIG. 4).
- other configurations except for the blades have the same structure in any of the embodiments. Therefore, in each of the following embodiments, description regarding the other configurations is omitted, and only the configuration of the blades is described.
- a plurality of blades 100 according to the first embodiment are arranged on the support plate 50 at a predetermined interval.
- the cross-sectional shape in the longitudinal direction of the blade is that the suction surface arc Rs that forms a convex suction surface, the pressure surface arc Rp that forms a concave pressure surface, the first end of the suction surface arc Rs, and the pressure surface arc Rp.
- An inner circumferential side arc Ri that connects the first end, and an outer circumferential side arc Ro that connects the second end of the suction surface arc Rs and the second end of the pressure surface arc Rp are provided.
- the radius rp of the pressure surface arc Rp is larger than the radius rs of the suction surface arc Rs, and the radius ri of the inner circumference side arc Ri is larger than the radius ro of the outer circumference side arc Ro. Further, the maximum thickness portion of the blade thickness is at a position of 40 to 60% from the inner circumferential side arc Ri in the longitudinal direction.
- the blades 100 are arranged such that the inner circumference side arc Ri is located on the inner circumference side of the support plate and the outer circumference side arc Ro is located on the outer circumference side of the support plate.
- the support plate has a structure that gradually decreases from the inner peripheral side toward the outer peripheral side.
- the radius rp of the pressure surface arc Rp is larger than the radius rs of the suction surface arc Rs
- the radius ri of the inner circumferential arc Ri is larger than the radius ro of the outer circumferential arc Ro. That is, ri> ro and rp> rs.
- the blade 100 shown in FIG. 5 has a part of the thickness of the pressure surface on the outer peripheral side thinner, and the cross section shown in FIG. The thickness is cut.
- the channel diameter Di on the inner peripheral side of the blade 100 is reduced to the channel diameter Do on the outer peripheral side of the blade.
- the diameter Do of the flow channel on the outer peripheral side of the blade 100 is the diameter of the flow channel on the outer peripheral side of the conventional crescent-shaped blade 500. Larger than Do '. Therefore, the change in the channel width from the inner peripheral side to the outer peripheral side of the blade 100 according to the first embodiment is smaller than the change in the channel width from the inner peripheral side to the outer peripheral side of the conventional crescent moon-shaped blade 500, and the speed The fluctuation of is also reduced. Specifically, as shown in FIG.
- the maximum reduction rate of the channel width between the plurality of blades on the outer peripheral side of the blade 100 according to the first embodiment is 20% or less, and the inner peripheral side of the blade 500 13.7% larger than the flow path width from the outer periphery to the outer periphery.
- the pressure surface arc Rp is configured by two arcs.
- the pressure surface Rp is composed of a first pressure surface arc Rp1 located on the inner peripheral side and a second pressure surface arc Rp2 located on the outer peripheral side, and the radius of the first pressure surface arc Rp1 located on the inner peripheral side.
- the radius rp2 of the second pressure surface arc Rp2 positioned on the outer peripheral side is larger than the radius rs of the negative pressure surface arc Rs, and the radius rp1 of the first pressure surface arc Rp1 positioned on the inner peripheral side is positioned on the outer peripheral side.
- the maximum thickness portion of the blade thickness is at a position of 40 to 60% from the inner circumferential side arc Ri in the longitudinal direction.
- the blades 100 are arranged such that the inner circumference side arc Ri is located on the inner circumference side of the support plate and the outer circumference side arc Ro is located on the outer circumference side of the support plate.
- the support plate has a structure that gradually decreases from the inner peripheral side toward the outer peripheral side.
- the pressure surface arc Rp is configured by two arcs.
- the pressure surface arc Rp is cut so that the thickness of the pressure surface on the outer peripheral side of the blade 200 is thinner than that of the blade 100 according to the first embodiment in which the pressure surface arc Rp is configured by a single arc.
- the change in the flow path width from the inner peripheral side to the outer peripheral side of the blade 200 according to the second embodiment is even smaller than the change in the flow path width from the inner peripheral side to the outer peripheral side of the conventional crescent-shaped blade 500.
- the fluctuation in speed becomes smaller. Specifically, as shown in FIG.
- the maximum reduction rate of the flow path width between the plurality of blades on the outer peripheral side of the blade 200 according to the second embodiment is 20% or less, and the inner peripheral side of the blade 500 13.7% larger than the flow path width from the outer periphery to the outer periphery.
- the decrease in the channel width is smaller on the inner peripheral side than the blade 100 according to the first embodiment.
- the pressure surface Rp is configured by three arcs. It is composed of a first pressure surface arc Rp1 located on the inner circumference side, a third pressure surface arc Rp3 located on the outer circumference side, and a second pressure surface arc Rp2 located between the inner circumference side and the outer circumference side.
- the radius rp2 of the second pressure surface arc Rp2 located between the peripheral side and the outer peripheral side is larger than the radius rp3 of the third pressure surface arc Rp3 located on the outer peripheral side.
- the maximum thickness portion of the blade thickness is at a position of 40 to 60% from the inner circumferential side arc Ri in the longitudinal direction.
- the blades 100 are arranged such that the inner circumference side arc Ri is located on the inner circumference side of the support plate and the outer circumference side arc Ro is located on the outer circumference side of the support plate.
- the support plate has a structure that gradually decreases from the inner peripheral side toward the outer peripheral side.
- the pressure surface arc Rp is configured by three arcs.
- the thickness of the pressure surface on the outer peripheral side becomes thinner. So that it is cut.
- the change in the flow path width from the inner peripheral side to the outer peripheral side of the blade 300 according to the third embodiment is smaller than the change in the flow path width from the inner peripheral side to the outer peripheral side of the conventional crescent moon shaped blade 500.
- the fluctuation in speed becomes smaller.
- the maximum reduction rate of the channel width between the plurality of blades on the outer peripheral side of the blade 300 according to the third embodiment is 20% or less, and the inner peripheral side of the blade 500 13.7% larger than the flow path width from the outer periphery to the outer periphery.
- the decrease in the channel width is smaller on the inner peripheral side than the blade 100 according to the first embodiment and the blade 200 according to the second embodiment.
- the turbulence of the air flow is reduced over the entire length direction from the inner peripheral side to the outer peripheral side of the blades, and the flow separation is less likely to occur on the discharge side negative pressure surface.
- power loss due to the fan is reduced.
- the present invention has a structure in which the thickness of the pressure surface on the outer peripheral side of the blades of the crossflow fan is cut, and the flow path width between the plurality of blades gradually decreases from the inner peripheral side to the outer peripheral side of the support plate. ing.
- the turbulence of the air flow is reduced over the entire length direction from the inner peripheral side to the outer peripheral side of the blades, and the flow separation is less likely to occur on the discharge side negative pressure surface. As a result, power loss due to the fan is reduced.
- the cross flow fan 10 has an outer diameter of 90 mm, the rotational speed of the cross flow fan 10 is 1200 rpm, and the maximum air flow rate is 10.4 m 3 / min.
- the crescent-shaped blades 500 of the above experiments are performed on the absolute velocity and relative velocity of the airflow between the plurality of blades on the blowout side of the crossflow fan 10, and the motor input to the crossflow fan and the airflow I also examined the relationship.
- FIG. 12b When the distribution state of the fluid velocity vector obtained from the calculation result of the air flow between the plurality of blades is represented by an absolute velocity vector diagram, the result when the conventional crescent-shaped blade 500 is adopted is shown in FIG.
- FIG. 12b The result of employing such a blade 100 is as shown in FIG. 12b.
- the flow velocity between the plurality of blades is lower than when the conventional crescent moon blade 500 is employed, and thus the air flow velocity at the outlet is reduced.
- the loss in the outlet channel can be reduced.
- the distribution state of the fluid velocity vector obtained from the calculation result of the air flow between the plurality of blades is represented by a relative velocity vector diagram
- the result when the conventional crescent-shaped blade 500 is adopted is shown in FIG.
- FIG. 13b The result when employing the blade 100 according to No. 1 is as shown in FIG. 13b.
- the flow velocity between the blades is reduced because the width of the plurality of blade passages is wider than when the conventional crescent-shaped blades 500 are employed. It is possible to reduce the friction and loss due to the reduction of the flow path.
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- General Engineering & Computer Science (AREA)
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- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Abstract
Description
このような構造により、羽根の外周側が薄くなり、ファンの外周側における隣接羽根間の流路幅を大きくすることができる。また、羽根の内周側から外周側の全般において隣接羽根間の流路幅が漸次減少し、羽根の内周側から外周側にかけての空気の速度の変動を低減でき、ファンの送風性能の低下を抑制することができる。
この場合、羽根の圧力面は複数の円弧により構成され、これらの複数の円弧の半径は、それぞれ負圧面円弧の半径より大きい。従って、羽根の内周側における複数の羽根の間の流路幅の減少率がより小さくになり、羽根の内周側から外周側にかけての空気の速度の変動を低減でき、ファンの送風性能の低下を抑制することができる。
この場合、羽根の圧力面は複数の円弧により構成され、羽根の厚さは最大肉厚部位から外周側円弧Ro側に向けて段階的に小さくなっている。従って、羽根の内周側から外周側に向けての複数の羽根の間の流路幅の減少率がより小さくになり、羽根の内周側から外周側にかけての空気の速度の変動を低減でき、ファンの送風性能の低下を抑制することができる。
<空気調和装置の全体構成>
本発明の一実施形態であるクロスフローファンを搭載した空気調和装置の外観を図1に示す。
この空気調和装置は、調和された空気を室内に供給するための装置である。空気調和装置は、室内の壁面などに取り付けられる室内機1と、室外に設置される室外機2とを備えている。
室内機1内には室内熱交換器が収納され、室外機2内には図示しない室外熱交換器が収納される。また、室内熱交換器と室外熱交換器が冷媒配管3により接続されることにより冷媒回路を構成している。
図2に示す室内機1は、室内の壁面等に取り付けられる壁掛け型の室内機であって、主として、室内機ケーシング5と、室内熱交換器8と、クロスフローファン10とを備えている。
室内機ケーシング5には、室内熱交換器8およびクロスフローファン10等が収納されている。また、室内機ケーシング5には、空調のための空気取込口6と空気吹出口4とが形成されている。
空気取込口6は室内機ケーシング5の上部および前部に設けられており、室内の空気を室内機ケーシング5の内側に取り込むための開口である。
空気吹出口4は、室内機ケーシング5の前面下部に設けられている。また、空気吹出口4近傍には、空気吹出口4を覆うように水平フラップ7が設けられている。水平フラップ7は、フラップモータ(図示せず)によって回転駆動され、空気の案内方向を変更したり、空気吹出口4を開閉したりする。
クロスフローファン10は、駆動機構としてのモータ(図示せず)と、モータにより空気を図4に示すA1方向に回転駆動する羽根車11とを有している。また、クロスフローファン10は、空気取込口6から室内機ケーシング5内に空気を吸入し、室内熱交換器8を通過させた後に、空気吹出口4から室内機ケーシング5外に空気を吹き出すことができるように配置されている。具体的には、クロスフローファン10は、室内機ケーシング5内における空気の流れ方向において、室内熱交換器8と空気吹出口4との間に配置されている。また、羽根車11の背面側には、案内部9が配置されている。案内部9は、室内熱交換器8と羽根車11との間の空間S1から羽根車11を貫流した後に羽根車11と空気吹出口4との間の空間S2に吹き出された空気流を空気吹出口4に案内する。さらに、羽根車11の前面側には、空間S2に吹き出された空気流が空間S1に逆流することを防止するための舌部15が設けられている。
次に、クロスフローファン10の羽根車11の構成について説明する。
クロスフローファン10は、図3に示すように、クロスフローファン10の回転軸線O方向である回転軸方向に細長いロータ状の外観形状を有している。また、クロスフローファン10は、主として、第1端面に設けられた円板状の円形支持プレート12、第2端面に設けられた円板状の円形支持プレート50と、複数の羽根車11と、複数の羽根車11の間に設けられた円板状の円形支持プレート51と、を有しており、これらが相互に接合されて構成されている。なお、円形支持プレート12は、回転軸方向の第一端を構成しており、円板状の円形支持プレート50は、回転軸方向の第2端を構成している。円形支持プレート12は、羽根車11の回転軸(すなわち、回転軸線O)を中心として回転する。また、円形支持プレート12の中央には、クロスフローファン10の回転軸としての軸部58が設けられている。
図3および図4に示すように、円板状の円形支持プレート50には、複数の羽根100が設けられたおり、円形支持プレート50は、クロスフローファン10の回転軸(すなわち、回転軸線O)を中心として回転する。また、複数の羽根100は、円形支持プレート50の円周方向に配置されている。また、各羽根100は、円形支持プレート50において、クロスフローファン10の回転方向(ここでは、図4に示すA1方向)に向かって所定角度傾斜するように配置されている。
本願発明において、羽根を除く他の構成はいずれかの実施例でも同じ構造であるため、下記の各実施例では、他の構成に関する記載は省略し、羽根の構成のみについて記載する。
図4~図6に示すように、実施例1に係る羽根100は、支持プレート50に所定の間隔で複数配置されている。羽根の長手方向の断面形状は、凸状の負圧面を形成する負圧面円弧Rsと、凹状の圧力面を形成する圧力面円弧Rpと、負圧面円弧Rsの第一端と圧力面円弧Rpの第一端とを連結する内周側円弧Riと、負圧面円弧Rsの第二端と圧力面円弧Rpの第二端とを連結する外周側円弧Roと、を備えている。圧力面円弧Rpの半径rpは負圧面円弧Rsの半径rsより大きく、内周側円弧Riの半径riは外周側円弧Roの半径roより大きい。また、羽根の厚さの最大肉厚部位が長手方向において内周側円弧Riから40~60%の位置にある。羽根100は、内周側円弧Riが支持プレートの内周側に位置し、外周側円弧Roが支持プレートの外周側に位置するように配置されており、複数の羽根の間の流路幅が支持プレートの内周側から外周側に向かって漸次減少する構造になっている。
実施例1に係る羽根100は、圧力面円弧Rpの半径rpは負圧面円弧Rsの半径rsより大きく、内周側円弧Riの半径riは外周側円弧Roの半径roより大きい。即ち、ri>ro、rp>rsである。その結果、図5に示す羽根100は、外周側の圧力面の厚さの一部が薄くなり、図13で示す断面が三日月形状の羽根500と比べて、羽根100の外周側の圧力面の厚さがカットされている。その結果、図6に示すように、羽根100の内周側においての流路の直径Diが羽根の外周側における流路の直径Doに減少されている。しかし、羽根100の外周側の圧力面の厚さがカットされているため、羽根100の外周側における流路の直径Doは、従来の断面が三日月形状の羽根500の外周側における流路の直径Do’に比べて大きい。従って、実施例1に係る羽根100の内周側から外周側にかけての流路幅の変化は、従来の三日月形状の羽根500の内周側から外周側にかけての流路幅の変化より小さく,速度の変動も小さくなる。具体的には、図7に示すように、実施例1に係る羽根100の外周側の複数の羽根の間の流路幅の最大減少率は20%以下であり、且つ羽根500の内周側から外周側にかけての流路幅より13.7%大きくなっている。その結果、吹出し側では流速の増大が小さくなり、よって、空気流の乱れが小さくなり、吹出し側負圧面で流れの剥離が発生し難くなっている。その結果、ファンによる電力の損失が減少する。
<羽根の構成>
実施例2に係る羽根200は、図8に示すように、圧力面円弧Rpが二円弧により構成されている。圧力面Rpは、内周側に位置する第1圧力面円弧Rp1と、外周側に位置する第2圧力面円弧Rp2により構成されており、内周側に位置する第1圧力面円弧Rp1の半径rp1、外周側に位置する第2圧力面円弧Rp2の半径rp2は、それぞれ負圧面円弧Rsの半径rsより大きく、内周側に位置する第1圧力面円弧Rp1の半径rp1は外周側に位置する第2圧力面円弧Rp2の半径rp2より小さい。即ち、ri>ro、rp2>rp1>rsである。また、羽根の厚さの最大肉厚部位が長手方向において内周側円弧Riから40~60%の位置にある。羽根100は、内周側円弧Riが支持プレートの内周側に位置し、外周側円弧Roが支持プレートの外周側に位置するように配置されており、複数の羽根の間の流路幅が支持プレートの内周側から外周側に向かって漸次減少する構造になっている。
実施例2に係る羽根200は、圧力面円弧Rpが二円弧により構成されている。その結果、圧力面円弧Rpが単一円弧により構成されている実施例1に係る羽根100と比べて、羽根200の外周側の圧力面の厚さがより薄くなるようにカットされている。その結果、実施例2に係る羽根200の内周側から外周側にかけての流路幅の変化は、従来の三日月形状の羽根500の内周側から外周側にかけての流路幅の変化よりさらに小さくなり、速度の変動もより小さくなる。具体的には、図9に示すように、実施例2に係る羽根200の外周側の複数の羽根の間の流路幅の最大減少率は20%以下であり、且つ羽根500の内周側から外周側にかけての流路幅より13.7%大きくなっている。しかし、実施例2に係る羽根200は内周側においては実施例1に係る羽根100より流路幅の減少が小さくなっている。その結果、羽根の内周側から外周側までの長さ方向全体において、空気流の乱れが小さくなり、吹出し側負圧面で流れの剥離が発生し難くなっている。その結果、ファンによる電力の損失が減少する。
<羽根の構成>
実施例3に係る羽根300は、図10に示すように、圧力面Rpは、三円弧により構成されている。内周側に位置する第1圧力面円弧Rp1と、外周側に位置する第3圧力面円弧Rp3と、内周側と外周側との間に位置する第2圧力面円弧Rp2により構成されており、内周側に位置する第1圧力面円弧Rp1の半径rp1、内周側と外周側との間に位置する第2圧力面円弧Rp2の半径rp2、外周側に位置する第3圧力面円弧Rp3の半径rp3は、それぞれ負圧面円弧Rsの半径rsより大きく、内周側に位置する第1圧力面円弧Rp1の半径rp1は外周側に位置する第3圧力面円弧Rp3の半径rp3より小さく、内周側と外周側の間に位置する第2圧力面円弧Rp2の半径rp2は外周側に位置する第3圧力面円弧Rp3の半径rp3より大きい。即ち、ri>ro、rp2>rp3>rp1>rsである。また、羽根の厚さの最大肉厚部位が長手方向において内周側円弧Riから40~60%の位置にある。羽根100は、内周側円弧Riが支持プレートの内周側に位置し、外周側円弧Roが支持プレートの外周側に位置するように配置されており、複数の羽根の間の流路幅が支持プレートの内周側から外周側に向かって漸次減少する構造になっている。
実施例3に係る羽根300は、圧力面円弧Rpが三円弧により構成されている。その結果、圧力面円弧Rpが単一円弧、二円弧により構成されている実施例1に係る羽根100、実施例2に係る羽根200と比べて、外周側の圧力面の厚さがより薄くなるようにカットされている。その結果、実施例3に係る羽根300の内周側から外周側にかけての流路幅の変化は、従来の三日月形状の羽根500の内周側から外周側にかけての流路幅の変化よりさらに小さくなり、速度の変動もより小さくなる。具体的には、図11に示すように、実施例3に係る羽根300の外周側の複数の羽根の間の流路幅の最大減少率は20%以下であり、且つ羽根500の内周側から外周側にかけての流路幅より13.7%大きくなっている。しかし、実施例3に係る羽根300は内周側においては実施例1に係る羽根100、実施例2に係る羽根200より流路幅の減少が小さくなっている。その結果、羽根の内周側から外周側までの長さ方向全体において、空気流の乱れが小さくなり、吹出し側負圧面で流れの剥離が発生し難くなっている。その結果、ファンによる電力の損失が減少する。
本発明は、クロスフローファンの羽根の外周側の圧力面の厚さがカットされ、複数の羽根の間の流路幅が支持プレートの内周側から外周側に向かって漸次減少する構造になっている。その結果、羽根の内周側から外周側までの長さ方向全体において、空気流の乱れが小さくなり、吹出し側負圧面で流れの剥離が発生し難くなっている。その結果、ファンによる電力の損失が減少する。
クロスフローファン10の外径が90mm、クロスフローファン10の回転速度が1200rpm、最大送風量が10.4m3/minの場合を例として、実施例1に係る羽根100を採用した場合と、従来の三日月形状の羽根500を採用した場合とにおける、クロスフローファン10の吹き出し側の複数の羽根間の空気流の絶対速度、相対速度について実験を行い、クロスフローファンへのモータ入力と風量との関係についても調べた。
また、複数の羽根間の空気流の計算結果から得られた流体速度ベクトルの分布状態を相対速度ベクトル図で表すと、従来の三日月形状の羽根500を採用した際の結果は図13a、実施例1に係る羽根100を採用した際の結果は図13bに示す通りである。ここでは、実施例1に係る羽根100を採用した際は、従来の三日月形状の羽根500を採用した際と比べて、複数の羽根間流路幅が広がっているため、羽根間における流速を低下させることができ、摩擦や流路の縮小による損失などが低減できる。
2 室外機
3 配管
4 空気調和装置
6 室内機のケーシング
8 室内機の熱交換器
10 クロスフローファン
11 羽根車
50 円盤状支持プレート
100,200,300,500 羽根
Rp 圧力面円弧
Rs 負圧面円弧
Ri 内周側円弧
Ro 外周側円弧
Claims (6)
- 支持プレート部(50)と、
所定の間隔で前記支持プレートに複数配置した羽根(100)で形成され、前記羽根の長手方向の断面形状は、凸状の負圧面を形成する負圧面円弧(Rs)と、凹状の圧力面を形成する圧力面円弧(Rp)と、前記負圧面円弧(Rs)の第一端と前記圧力面円弧(Rp)の第一端とを連結する内周側円弧(Ri)と、前記負圧面円弧(Rs)の第二端と前記圧力面円弧(Rp)の第二端とを連結する外周側円弧(Ro)と、を備え、前記圧力面円弧(Rp)の半径(rp)は前記負圧面円弧(Rs)の半径(rs)より大きく、前記内周側円弧(Ri)の半径(ri)は前記外周側円弧(Ro)の半径(ro)より大きく、前記羽根の厚さは、最大肉厚部位が長手方向において前記内周側円弧(Ri)から40~60%の位置にある翼部(11)と、を備え、
前記羽根(100)は、前記内周側円弧(Ri)が前記支持プレートの内周側に位置し、前記外周側円弧(Ro)が前記支持プレートの外周側に位置するように配置され、
前記複数の羽根の間の流路幅が前記支持プレートの内周側から外周側に向かって漸次減少する、
クロスフローファン。 - 前記負圧面は単一負圧面円弧(Rs)で構成され、
前記圧力面は、複数の圧力面円弧(Rp1、Rp2、…Rpn)により構成され、
前記複数の圧力面円弧(Rp1、Rp2、…Rpn)の半径(rp1、rp2、…rpn)はそれぞれ前記負圧面円弧(Rs)の半径(rs)より大きい、
請求項1に記載のクロスフローファン。 - 前記複数の圧力面円弧(Rp1、Rp2、…Rpn)の半径(rp1、rp2、…rpn)の大きさは、rp2>rp3>…>rpn>rp1であり、
前記羽根の厚さは、前記最大肉厚部位から前記外周側円弧(Ro)側に向けて段階的に小さくなっている、
請求項2に記載のクロスフローファン。 - 前記複数の羽根の間の流路幅の最大減少率は、20%以下である、
請求項1~3のいずれかに記載のクロスフローファン。 - 請求項4に記載のクロスフローファン(10)と、
熱交換器(8)と、
ケーシング(6)と、
を備えた空気調和装置の室内機(1)。 - 請求項5に記載の室内機(1)と、
室外機(2)と、
前記室内機と前記室外機とを連結する配管(3)と、
を備えた空気調和装置(4)。
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JP2013541840A JP5806327B2 (ja) | 2011-11-04 | 2012-11-01 | クロスフローファン |
ES12844871.9T ES2664543T3 (es) | 2011-11-04 | 2012-11-01 | Ventilador de flujo cruzado |
US14/354,902 US9638195B2 (en) | 2011-11-04 | 2012-11-01 | Cross flow fan |
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AU2003101030A4 (en) * | 2001-08-15 | 2004-02-12 | Torin Industries Pty Ltd | Blower wheel |
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EP2775146B1 (en) | 2018-02-28 |
US20140301825A1 (en) | 2014-10-09 |
US9638195B2 (en) | 2017-05-02 |
CN103089661A (zh) | 2013-05-08 |
AU2012333534A1 (en) | 2014-05-29 |
JP5806327B2 (ja) | 2015-11-10 |
KR101607791B1 (ko) | 2016-03-30 |
ES2664543T3 (es) | 2018-04-19 |
JPWO2013065792A1 (ja) | 2015-04-02 |
KR20140121814A (ko) | 2014-10-16 |
AU2012333534B2 (en) | 2015-12-24 |
CN103089661B (zh) | 2015-04-01 |
EP2775146A1 (en) | 2014-09-10 |
EP2775146A4 (en) | 2015-07-22 |
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