EP2131041B1 - Sirocco fan and air conditioner - Google Patents

Sirocco fan and air conditioner Download PDF

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Publication number
EP2131041B1
EP2131041B1 EP08722746.8A EP08722746A EP2131041B1 EP 2131041 B1 EP2131041 B1 EP 2131041B1 EP 08722746 A EP08722746 A EP 08722746A EP 2131041 B1 EP2131041 B1 EP 2131041B1
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EP
European Patent Office
Prior art keywords
sirocco fan
blade
air
fan
revolutions
Prior art date
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Application number
EP08722746.8A
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German (de)
French (fr)
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EP2131041A1 (en
EP2131041A4 (en
Inventor
Hiroki Okazawa
Ryouji Abe
Hiroshi Tsutsumi
Takahiro Yamatani
Kazunobu Nishimiya
Yukihiko Kawanori
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/007—Ventilation with forced flow
    • 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
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Definitions

  • the present invention relates to a sirocco fan, more particularly a sirocco fan in which a noise is reduced and an air-blowing characteristic is improved, and to an air-conditioning apparatus provided with the same.
  • sirocco fans are often used.
  • the sirocco fan is composed of a whorl-shaped scroll and a large number of proclinated blades rotatably disposed in the scroll and arranged in a cylindrical manner.
  • the air-conditioning apparatus provided with such a sirocco fan, for example, the sirocco fan of a window-type air conditioner that is disclosed in a patent document 1 exists.
  • the blade is formed to have a blade exit angle of from 125 to 137 degrees, a blade inlet angle of from 58 to 63 degrees, a solidity of from 0.75 to 0.85, an inner/outer diameter ratio of from 0.82 to 0.86, and a maximum warp position of from 0.3 to 0.4, the maximum warp position being defined as a ratio of the most warped position to a blade length in Reference Document 1.
  • the blade By forming the blade to have a configuration as described above, it is specified that a noise of the sirocco fan is not increased even when a rotation speed is increased with an air-blowing amount being preserved.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2001-323895 (Claim 1, Fig. 1 through Fig. 3 )
  • EP 1 632 725 A1 discloses an air conditioner.
  • an object of the present invention is to provide a sirocco fan capable of obtaining a large air-blowing amount at a time of a predetermined noise occurrence, in other words, capable of reducing a noise value and a number of revolutions when obtaining a predetermined air-blowing amount, and an air-conditioning apparatus provided with the same.
  • a blade shape of a sirocco fan when a fan diameter is defined as D, a maximum camber height is defined as H, a blade chord length is defined as L, a radius of a front edge of an inner circumferential side of the blade is defined as R, a blade inlet angle is defined as ⁇ 1 , and a blade exit angle is defined as ⁇ 2 , by making 0.18 ⁇ H/L ⁇ 0.26, R/L ⁇ 0.11, 100° ⁇ ⁇ 1 ⁇ 130°, and 26° ⁇ ⁇ 2 ⁇ 32°, an air-blowing amount at the time of a predetermined noise occurrence can be increased and in the case of an air-conditioning apparatus, the COP can be improved.
  • 1 sirocco fan 2 fan motor, 3 heat exchanger, 4 suction inlet, 5 blowing-out exit, 6 scroll, 7 rotation shaft, 8 blade, 9 warped line, 9a inner circumferential end, 9b outer circumferential end, 10 indoor unit, 11 straight line (blade chord length L), 12 perpendicular line, 13 inner circumferential tangent, 14 warped line tangent, 15 outer circumferential tangent, 16 warped line tangent, 100 conventional sirocco fan, D fan-diameter, H maximum camber height, L blade chord length, R radius of a front edge, ⁇ incidence angle, ⁇ 1 blade inlet angle, ⁇ 2 blade exit angle.
  • Fig. 1 is a schematic plan view (a) and a schematic side elevation (b) illustrating an inner constitution of an indoor unit of an air-conditioning apparatus provided with a sirocco fan of a first embodiment of the present invention.
  • the indoor unit 10 constitutes an indoor air-conditioning apparatus, and is provided with a pair of sirocco fans 1, a fan motor 2 that simultaneously rotationally drives these sirocco fans 1, and a heat exchanger 3 that performs heat-exchanging operation with air that is blown out from the sirocco fans 1.
  • the sirocco fan 1 is provided with a whorl-shaped scroll 6, and a large number of blades that are rotatably disposed in the scroll 6 and arranged in a cylindrical manner.
  • a reference numeral 4 denotes a suction inlet of the air
  • a reference numeral 5 denotes a blowing outlet for cold air or warm air
  • a reference numeral 7 denotes a rotation shaft of the fan motor 2.
  • the aforementioned indoor unit 10 is provided with a refrigerating circuit for a refrigerant, which is constituted by a compressor, a condenser, an expansion valve, and an evaporator, all of which being not shown, and is configured so as to perform cooling heating operations in a room, or the like.
  • a refrigerating circuit for a refrigerant which is constituted by a compressor, a condenser, an expansion valve, and an evaporator, all of which being not shown, and is configured so as to perform cooling heating operations in a room, or the like.
  • the sirocco fan 1 is configured to have a fan-diameter D of 160 mm, a width of 190 mm, the number of the blades of 40, and the heat exchanger 3 is provided with a heat transmission pipe of 12 steps, and an array pitch thereof is 12.7 mm and a step pitch thereof is 20.4 mm, a length in an axial direction of the heat transmission pipe is 700 mm, and a draft resistance ⁇ P1 is 23.1 V 1.3 [Pa] (V: velocity[m/s]).
  • the indoor unit 10 is configured to have a depth of 680 mm, a height of 210 mm, and a width of 960 mm.
  • the air in the room is sucked in from the suction inlet 4 of the indoor unit 10, and is further sucked in from a suction inlet of the scroll 6 in an axial direction.
  • the air to which a dynamic pressure and a static pressure is applied by a cylindrical blade array that is rotating in the scroll 6 by means of the fan motor 2 is blown out from a blowing outlet that opens to an air trunk in the indoor unit 10 to be heat-exchanged with the heat exchanger 3 installed in the air trunk, then blown out from the blowing outlet 5 into the room while being turned into cool or warm air.
  • Fig. 2 is an explanatory view of parameters indicating a blade shape of the sirocco fan.
  • Fig. 3 is a view illustrating a blade shape of the sirocco fan in the first embodiment.
  • Fig. 4 is a comparative view illustrating a conventional blade shape by superimposing Fig. 3 .
  • An air-blowing amount of the sirocco fan 1 at a predetermined noise value is decided by relations of parameters D, L, H, ⁇ 1 , ⁇ 1 , and R of the sirocco fan 1, where a fan-diameter is defined as D, a blade chord length is defined as L, a maximum camber height is defined as H, a radius of a front edge of an inner circumferential side of the blade is defined as R, a blade inlet angle is defined as ⁇ 1 , and a blade exit angle is defined as ⁇ 2 , respectively.
  • a fan-diameter D and the radius R of the front edge of an inner circumferential side of the blade illustrations are omitted.
  • the fan-diameter D is a diameter of an outer circumferential circle of the blade 8 of the sirocco fan 1.
  • the blade chord length L is a length of a straight line 11 that connects an inner circumferential end 9a and an outer circumferential end 9b of a warped line 9 of the blade 8.
  • the maximum camber height H is a maximum length of a perpendicular line 12 for the warped line 9 of the blade 8 from the straight line 11.
  • the blade inlet angle ⁇ 1 is an angle formed by an inner circumferential tangent 13 and a warped line tangent 14 at the inner circumferential end 9a of the warped line 9 of the blade 8.
  • the blade exit angle ⁇ 2 is an angle formed by an outer circumferential tangent 15 and a warped line tangent 16 at the outer circumferential end 9b of the warped line 9 of the blade 8.
  • An incidence angle ⁇ is an angle formed by the camber line tangent 14 and an inflow direction of airflow at the inner circumferential end 9a of the warped line 9 of the blade 8.
  • the radius R of the front edge at the inner circumferential side of the blade is a radius of a circular arc portion formed at the front edge of the blade 8.
  • the sirocco fan 100 has a shortcoming such that the air-blowing amount is small at a time of a predetermined noise occurrence compared with that of the sirocco fan 1. This is because the air-blowing amount becomes small at the time of a predetermined noise occurrence because H/L is small, R/L is large, angles of ⁇ 1 and P 2 are inappropriate, and so forth.
  • the sirocco fan 100 is mounted on the indoor unit 10, performance of the heat exchanger 3 is reduced, loads of the compressor being increased, and the COP being lowered.
  • the warp of the blade increases and the airflow is peeled off from a blade surface at a negative pressure surface side, so that a stall occurs to cause an increase in the noise value and the number of revolutions.
  • the warp of the blade is reduced and a lifting power of the blade is lowered to cause an increase in the noise value and the number of revolutions.
  • ⁇ 1 is greater than 130°, an area of an inflow portion between the blades is reduced to cause an increase in the noise value and the number of revolutions.
  • ⁇ 2 is smaller than 100°, the incidence angle ⁇ of the blade is increased to bring about the stall to cause an increase in the noise value and the number of revolutions.
  • the warp of the blade is reduced and the lifting power is reduced to cause an increase in the noise value and the number of revolutions.
  • the ⁇ 2 is smaller than 26°, an area of an outflow portion between the blades is reduced to cause an increase in the velocity of the airflow at the outflow portion between the blades. Since the airflow between the blades of the sirocco fan is in a stall state to some extent, when the velocity at the outflow portion between the blades is increased, a re-adhesion of the flow that has stalled in the vicinity of the front edge occurs in the vicinity of the rear edge. When the re-adhesion occurs, a fluctuation in the static pressure on a blade surface is increased to cause an increase in the noise.
  • a sirocco fan 1X is defined in such a way that the negative pressure surface side of the front edge is almost linearly cut off as illustrated in Fig. 5 .
  • the front edge of the sirocco fan 1 has a shape composed of a semicircular arc.
  • Figs. 6 and 7 a relative velocity distribution of the airflow inside of the fan in the vicinity of a main plate at 1100 rpm is shown.
  • Table 11 the static pressure of the fan under a single operation is shown (1100 rpm, and the air-blowing amount 8 m 3 /min).
  • the velocity distribution in the vicinity of the front edge at the negative pressure surface side of the sirocco fan 1X is greater. This is because, primarily, the velocity of the blowing air on the negative pressure surface side of the front edge where the a wind easily blows is increased by cutting off the negative pressure surface side, and the number of revolutions and the noise value are reduced as shown in Table 10.
  • the highest static pressure can be obtained at the same number of revolutions and air-blowing amount by the sirocco fan 1X in which the negative pressure surface side of the front edge is cut off, and an effect appears that the wind is easier to blow by cutting off the negative pressure surface side of the front edge.

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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)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Description

  • The present invention relates to a sirocco fan, more particularly a sirocco fan in which a noise is reduced and an air-blowing characteristic is improved, and to an air-conditioning apparatus provided with the same.
  • Hitherto, in air-conditioning apparatuses, air purification systems, and so forth, sirocco fans are often used. The sirocco fan is composed of a whorl-shaped scroll and a large number of proclinated blades rotatably disposed in the scroll and arranged in a cylindrical manner. As the air-conditioning apparatus provided with such a sirocco fan, for example, the sirocco fan of a window-type air conditioner that is disclosed in a patent document 1 exists. That is, in the sirocco fan of the window-type air conditioner, which is formed by including a shroud and a large number of blades disposed on the shroud at constant intervals, the blade is formed to have a blade exit angle of from 125 to 137 degrees, a blade inlet angle of from 58 to 63 degrees, a solidity of from 0.75 to 0.85, an inner/outer diameter ratio of from 0.82 to 0.86, and a maximum warp position of from 0.3 to 0.4, the maximum warp position being defined as a ratio of the most warped position to a blade length in Reference Document 1.
  • By forming the blade to have a configuration as described above, it is specified that a noise of the sirocco fan is not increased even when a rotation speed is increased with an air-blowing amount being preserved.
  • [Patent Document 1] Japanese Unexamined Patent Application Publication No. 2001-323895 (Claim 1, Fig. 1 through Fig. 3)
  • EP 1 632 725 A1 discloses an air conditioner.
  • There were problems such that, since an air-blowing amount of the sirocco fan at a predetermined noise value is small, and a capability of a heat exchanger is lowered in the air-conditioning apparatus on which the conventional sirocco fan is mounted, a load of a compressor is increased, and a COP (performance coefficient) being lowered. In addition, if the air-blowing amount of the sirocco fan is increased in order to suppress the lowering of the COP, the noise value is increased to give an uncomfortable feeling to users.
  • In light of the above-described problems, an object of the present invention is to provide a sirocco fan capable of obtaining a large air-blowing amount at a time of a predetermined noise occurrence, in other words, capable of reducing a noise value and a number of revolutions when obtaining a predetermined air-blowing amount, and an air-conditioning apparatus provided with the same.
  • According to the present invention there is provided a sirocco fan as defined in the independent claim.
  • According to the present invention, regarding a blade shape of a sirocco fan, when a fan diameter is defined as D, a maximum camber height is defined as H, a blade chord length is defined as L, a radius of a front edge of an inner circumferential side of the blade is defined as R, a blade inlet angle is defined as β1, and a blade exit angle is defined as β2, by making 0.18 ≤ H/L ≤ 0.26, R/L ≤ 0.11, 100° ≤ β1 ≤ 130°, and 26° ≤ β2 ≤ 32°, an air-blowing amount at the time of a predetermined noise occurrence can be increased and in the case of an air-conditioning apparatus, the COP can be improved.
  • The present invention will be described by way of example with reference to the accompanying drawings as follows.
    • [Fig. 1] Fig. 1 is a schematic plan view (a) and side elevation (b) illustrating an inner construction of an indoor unit of an air-conditioning apparatus provided with a sirocco fan in a first embodiment of the present invention.
    • [Fig. 2] Fig. 2 is an explanatory view of parameters indicating a blade shape of the sirocco fan in the first embodiment.
    • [Fig. 3] Fig. 3 is a view illustrating a blade shape of the sirocco fan in the first embodiment.
    • [Fig. 4] Fig. 4 is a comparative view of the blade shape of the sirocco fan in the first embodiment and that of a conventional blade shape.
    • [Fig. 5] Fig. 5 is a view illustrating the blade shapes of the sirocco fans in the first and second embodiments.
    • [Fig. 6] Fig. 6 is a view illustrating a relative velocity distribution of the sirocco fan in the first embodiment.
    • [Fig. 7] Fig. 7 is a view illustrating a relative velocity distribution of the sirocco fan in the second embodiment.
    Reference Numerals
  • 1 sirocco fan, 2 fan motor, 3 heat exchanger, 4 suction inlet, 5 blowing-out exit, 6 scroll, 7 rotation shaft, 8 blade, 9 warped line, 9a inner circumferential end, 9b outer circumferential end, 10 indoor unit, 11 straight line (blade chord length L), 12 perpendicular line, 13 inner circumferential tangent, 14 warped line tangent, 15 outer circumferential tangent, 16 warped line tangent, 100 conventional sirocco fan, D fan-diameter, H maximum camber height, L blade chord length, R radius of a front edge, α incidence angle, β1 blade inlet angle, β2 blade exit angle.
  • Hereinbelow, embodiments of the present invention will be explained with reference to the drawings.
    • First Embodiment
  • Fig. 1 is a schematic plan view (a) and a schematic side elevation (b) illustrating an inner constitution of an indoor unit of an air-conditioning apparatus provided with a sirocco fan of a first embodiment of the present invention.
  • In Fig. 1, the indoor unit 10 constitutes an indoor air-conditioning apparatus, and is provided with a pair of sirocco fans 1, a fan motor 2 that simultaneously rotationally drives these sirocco fans 1, and a heat exchanger 3 that performs heat-exchanging operation with air that is blown out from the sirocco fans 1. The sirocco fan 1 is provided with a whorl-shaped scroll 6, and a large number of blades that are rotatably disposed in the scroll 6 and arranged in a cylindrical manner. In the drawing, a reference numeral 4 denotes a suction inlet of the air, a reference numeral 5 denotes a blowing outlet for cold air or warm air, and a reference numeral 7 denotes a rotation shaft of the fan motor 2.
  • The aforementioned indoor unit 10 is provided with a refrigerating circuit for a refrigerant, which is constituted by a compressor, a condenser, an expansion valve, and an evaporator, all of which being not shown, and is configured so as to perform cooling heating operations in a room, or the like. Further, an example of specifications of the present first embodiment is as follows: the sirocco fan 1 is configured to have a fan-diameter D of 160 mm, a width of 190 mm, the number of the blades of 40, and the heat exchanger 3 is provided with a heat transmission pipe of 12 steps, and an array pitch thereof is 12.7 mm and a step pitch thereof is 20.4 mm, a length in an axial direction of the heat transmission pipe is 700 mm, and a draft resistance ΔP1 is 23.1 V1.3 [Pa] (V: velocity[m/s]). Furthermore, the indoor unit 10 is configured to have a depth of 680 mm, a height of 210 mm, and a width of 960 mm.
  • The air in the room is sucked in from the suction inlet 4 of the indoor unit 10, and is further sucked in from a suction inlet of the scroll 6 in an axial direction. The air to which a dynamic pressure and a static pressure is applied by a cylindrical blade array that is rotating in the scroll 6 by means of the fan motor 2 is blown out from a blowing outlet that opens to an air trunk in the indoor unit 10 to be heat-exchanged with the heat exchanger 3 installed in the air trunk, then blown out from the blowing outlet 5 into the room while being turned into cool or warm air.
  • Fig. 2 is an explanatory view of parameters indicating a blade shape of the sirocco fan. Fig. 3 is a view illustrating a blade shape of the sirocco fan in the first embodiment. Fig. 4 is a comparative view illustrating a conventional blade shape by superimposing Fig. 3.
  • An air-blowing amount of the sirocco fan 1 at a predetermined noise value is decided by relations of parameters D, L, H, β1, β1, and R of the sirocco fan 1, where a fan-diameter is defined as D, a blade chord length is defined as L, a maximum camber height is defined as H, a radius of a front edge of an inner circumferential side of the blade is defined as R, a blade inlet angle is defined as β1, and a blade exit angle is defined as β2, respectively. Incidentally, regarding a fan-diameter D and the radius R of the front edge of an inner circumferential side of the blade , illustrations are omitted.
  • Here, definitions of each aforementioned parameters are as follows. The fan-diameter D is a diameter of an outer circumferential circle of the blade 8 of the sirocco fan 1. The blade chord length L is a length of a straight line 11 that connects an inner circumferential end 9a and an outer circumferential end 9b of a warped line 9 of the blade 8. The maximum camber height H is a maximum length of a perpendicular line 12 for the warped line 9 of the blade 8 from the straight line 11. The blade inlet angle β1 is an angle formed by an inner circumferential tangent 13 and a warped line tangent 14 at the inner circumferential end 9a of the warped line 9 of the blade 8. The blade exit angle β2 is an angle formed by an outer circumferential tangent 15 and a warped line tangent 16 at the outer circumferential end 9b of the warped line 9 of the blade 8. An incidence angle α is an angle formed by the camber line tangent 14 and an inflow direction of airflow at the inner circumferential end 9a of the warped line 9 of the blade 8. The radius R of the front edge at the inner circumferential side of the blade is a radius of a circular arc portion formed at the front edge of the blade 8.
  • On the other hand, when denoting a conventional sirocco fan as a reference numeral 100 denotes, the sirocco fan 100 has a shortcoming such that the air-blowing amount is small at a time of a predetermined noise occurrence compared with that of the sirocco fan 1. This is because the air-blowing amount becomes small at the time of a predetermined noise occurrence because H/L is small, R/L is large, angles of β1 and P2 are inappropriate, and so forth. As a result, in a case where the sirocco fan 100 is mounted on the indoor unit 10, performance of the heat exchanger 3 is reduced, loads of the compressor being increased, and the COP being lowered.
  • Accordingly, since the air-blowing amount at the time of the predetermined noise occurrence is reduced and performance of the heat exchanger 3 is lowered in a case of the indoor unit on which the sirocco fan 100 is mounted, a temperature difference between a refrigerant temperature and room temperature has to be made large by lowering the refrigerant temperature more than necessary in a cooling operation and raising more than necessary in a heating operation so as to obtain a predetermined air-conditioning capability at the time of the predetermined noise occurrence. Therefore, there is a problem that the load of the compressor is increased and the COP is lowered.
  • In Table 1, values of H/L, R/L, β1, and β2 of a first exemplary sirocco fan useful for an understanding of the present invention and that of the conventional sirocco fan 100 are shown. Incidentally, a L/D value is set to be 0.17.
    • [Table 1]
  • Table 1 Shape Parameter of Blade
    First Exemplary Sirocco Fan Sirocco Fan 100
    H/L 0.22 0.28
    R/L 0.16 0.16
    β 1 100° 100°
    β2 43° 43°
  • In Table 2, a noise value and a number of revolutions are shown at a blown-out airflow amount of 16 m3/min in a case where the first exemplary sirocco fan and the sirocco fan 100 are mounted on the indoor unit 10. All the conditions other than the sirocco fan are the same.
    • [Table 2]
  • Table 2 Noise Value and Number of Revolutions at 16 m3/min
    First Exemplary Sirocco Fan Sirocco Fan 100
    Noise Value (dB) 46.5 47.2
    Number of Revolutions (rpm) 1101 1127
  • As shown in Tables 1 and 2, by setting H/L = 0.22, the noise value and the number of revolutions can be reduced.
  • In Table 3, values of H/L, R/L, β1, and β2 of a second exemplary sirocco fan useful for an understanding of the present invention and that of the conventional sirocco fan 100 are shown.
    • [Table 3]
  • Table 3 Shape Parameters of Blade
    Second Exemplary Sirocco Fan Sirocco Fan 100
    H/L 0.28 0.28
    R/L 0.11 0.16
    β1 125° 125°
    β2 47° 47°
  • In Table 4, the noise value and the number of revolutions are shown at a blown-out airflow amount of 16 m3/min in a case where the second exemplary sirocco fan and the sirocco fan 100 are mounted on the indoor unit 10. All the conditions other than the sirocco fan are the same.
    • [Table 4]
  • Table 4 Noise Value and Number of Revolutions at 16 m3/min
    Second Exemplary Sirocco Fan Sirocco Fan 100
    Noise Value (dB) 46.1 47.2
    Number of Revolutions (rpm) 1088 1127
  • As shown in Tables 3 and 4, by setting R/L = 0.11, the noise value and the number of revolutions can be reduced.
  • In Table 5, values of H/L, R/L, β1, and β2 of a third exemplary sirocco fan useful for an understanding of the present invention and that of the conventional sirocco fan 100 are shown.
    • [Table 5]
  • Table 5 Shape Parameters of Blade
    Third Exemplary Sirocco Fan Sirocco Fan 100
    H/L 0.28 0.28
    R/L 0.16 0.16
    β1 110° 125°
    β2 47° 47°
  • In Table 6, the noise value and the number of revolutions are shown at a blown-out airflow amount of 16 m3/min in a case where the third exemplary sirocco fan and the sirocco fan 100 are mounted on the indoor unit 10. All the conditions other than the sirocco fan are the same.
    • [Table 6]
  • Table 6 Noise Value and Number of Revolutions at 16 m3/min
    Third Exemplary Sirocco Fan Sirocco Fan 100
    Noise Value (dB) 46.3 47.2
    Number of Revolutions (rpm) 1115 1127
  • As shown in Tables 5 and 6, by setting β1 = 110°, the noise value and the number of revolutions can be reduced.
  • In Table 7, the values of H/L, R/L, β1, and β2 of a fourth exemplary sirocco fan useful for an understanding of the present invention and that of the conventional sirocco fan 100 are shown.
    • [Table 7]
  • Table 7 Shape Parameters of Blade
    Fourth Exemplary Sirocco Fan Sirocco Fan 100
    H/L 0.28 0.28
    R/L 0.16 0.16
    β1 125° 125°
    β2 29° 47°
  • In Table 8, the noise value and the number of revolutions are shown at a blown-out airflow amount of 16 m3/min in a case where the fourth exemplary sirocco fan and the sirocco fan 100 are mounted on the indoor unit 10. All the conditions other than the sirocco fan are the same.
    • [Table 8]
  • Table 8 Noise Value and Number of Revolutions at 16 m3/min
    Fourth Exemplary Sirocco Fan Sirocco Fan 100
    Noise Value (dB) 46.4 47.2
    Number of Revolutions (rpm) 1113 1127
  • As shown in Tables 7 and 8, by setting β2 = 29°, the noise value and the number of revolutions can be reduced.
  • In Table 9, the noise value and the number of revolutions is shown at a blown-out airflow amount of 16 m3/min in a case where the sirocco fan 1 according to an embodiment of the present invention is mounted on the indoor unit 10 and H/L = 0.22, R/L = 0.11, β1 = 110°, and β2 = 29°, respectively.
    • [Table 9]
  • Table 9 Noise Value and Number of Revolutions at 16 m3/min
    Sirocco Fan
    1
    Noise Value (dB) 45.3
    Number of Revolutions (rpm) 1088
  • As shown in Table 9, when optimal H/L, R/L, β1, and β2 are combined, both the noise value and the number of revolutions become minimum.
  • Next, descriptions will be given to why the noise value and the number of revolutions are reduced by setting H/L = 0.22, R/L = 0.11, β1 = 110°, and β2 = 29°.
  • In a case where the H/L is greater than 0.26, the warp of the blade increases and the airflow is peeled off from a blade surface at a negative pressure surface side, so that a stall occurs to cause an increase in the noise value and the number of revolutions. On the other hand, in a case where the H/L is smaller than 0.18, the warp of the blade is reduced and a lifting power of the blade is lowered to cause an increase in the noise value and the number of revolutions.
  • In a case where the R/L is greater than 0.11, a stagnation pressure increases and a dynamic pressure is lowered at the front edge of the blade, so that the airflow amount is reduced to cause an increase in the noise value and the number of revolutions.
  • If the β1 is greater than 130°, an area of an inflow portion between the blades is reduced to cause an increase in the noise value and the number of revolutions. On the other hand, if the β2 is smaller than 100°, the incidence angle α of the blade is increased to bring about the stall to cause an increase in the noise value and the number of revolutions.
  • If the β2 is greater than 32°, the warp of the blade is reduced and the lifting power is reduced to cause an increase in the noise value and the number of revolutions. On the other hand, if the β2 is smaller than 26°, an area of an outflow portion between the blades is reduced to cause an increase in the velocity of the airflow at the outflow portion between the blades. Since the airflow between the blades of the sirocco fan is in a stall state to some extent, when the velocity at the outflow portion between the blades is increased, a re-adhesion of the flow that has stalled in the vicinity of the front edge occurs in the vicinity of the rear edge. When the re-adhesion occurs, a fluctuation in the static pressure on a blade surface is increased to cause an increase in the noise.
    • Second Embodiment
  • In the sirocco fan 1 of H/L = 0.22, R/L = 0.11, β1 = 110°, and β2 = 29° shown in the first embodiment, a sirocco fan 1X is defined in such a way that the negative pressure surface side of the front edge is almost linearly cut off as illustrated in Fig. 5. The front edge of the sirocco fan 1 has a shape composed of a semicircular arc.
  • In Table 10, the noise value and the number of revolutions are shown at a blown-out airflow amount of 16 m3/min in a case where the sirocco fans 1 and 1X are mounted on the indoor unit 10. All the conditions other than the sirocco fan are the same.
    • [Table 10]
  • Table 10 Noise Value and Number of Revolutions at 16 m3/min
    Sirocco Fan
    1X Sirocco Fan 1
    Noise Value (dB) 45.3 45.8
    Number of Revolutions (rpm) 1088 1103
  • As shown in Table 10, if the negative pressure surface side of the front edge formed of the semicircular arc of the sirocco fan is cut off, the noise value and the number of revolutions can be reduced.
  • Next, descriptions will be given to the reason. In Figs. 6 and 7, a relative velocity distribution of the airflow inside of the fan in the vicinity of a main plate at 1100 rpm is shown. In Table 11, the static pressure of the fan under a single operation is shown (1100 rpm, and the air-blowing amount 8 m3/min).
  • When comparing the relative velocity distribution inside of the fan of the sirocco fan 1 shown in Fig. 6, and that of the sirocco fan 1X in which the negative pressure surface side of the front edge is cut off, shown in Fig. 7, the velocity distribution in the vicinity of the front edge at the negative pressure surface side of the sirocco fan 1X is greater. This is because, primarily, the velocity of the blowing air on the negative pressure surface side of the front edge where the a wind easily blows is increased by cutting off the negative pressure surface side, and the number of revolutions and the noise value are reduced as shown in Table 10. Further, from the static pressure shown in Table 11, the highest static pressure can be obtained at the same number of revolutions and air-blowing amount by the sirocco fan 1X in which the negative pressure surface side of the front edge is cut off, and an effect appears that the wind is easier to blow by cutting off the negative pressure surface side of the front edge.
    • [Table 11]
  • Table 11 Static Pressure at 1100 rpm, 8 m3/min
    Sirocco Fan
    1X Sirocco Fan 1
    Static Pressure (Pa) 61.3 60.2

Claims (3)

  1. A sirocco fan including: a scroll (6) and a number of blades (8) being rotatably disposed in the scroll (6) and arranged in a cylindrical manner,
    characterised in that a fan diameter is defined as D, a maximum camber height is defined as H, a blade chord length is defined as L, a radius of a front edge at an inner circumferential side of the blade (8) is defined as R, a blade inlet angle is defined as β1, and a blade exit angle is defined as β2, then 0.18 ≤ H/L ≤ 0.26, R/L ≤ 0.11, 100° ≤ β1 ≤ 130°, and 26° ≤ β2 ≤ 32° are satisfied.
  2. The sirocco fan of Claim 1, wherein the front edge at the inner circumferential side of the blade (8) has a shape in which a negative pressure surface side of the blade (8) is linearly cut off from a semicircular arc shape.
  3. An air-conditioning apparatus comprising the sirocco fan of any one of Claims 1 through 2.
EP08722746.8A 2007-03-27 2008-03-25 Sirocco fan and air conditioner Active EP2131041B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007081120 2007-03-27
PCT/JP2008/055483 WO2008123212A1 (en) 2007-03-27 2008-03-25 Sirocco fan and air conditioner

Publications (3)

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EP2131041A1 EP2131041A1 (en) 2009-12-09
EP2131041A4 EP2131041A4 (en) 2013-11-13
EP2131041B1 true EP2131041B1 (en) 2018-08-22

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JP (1) JP5235867B2 (en)
KR (1) KR101122802B1 (en)
CN (1) CN101595309B (en)
AU (1) AU2008236113B2 (en)
ES (1) ES2689721T3 (en)
HK (1) HK1135161A1 (en)
TW (1) TW200916662A (en)
WO (1) WO2008123212A1 (en)

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KR20090086640A (en) 2009-08-13
CN101595309B (en) 2011-07-13
AU2008236113A1 (en) 2008-10-16
HK1135161A1 (en) 2010-05-28
TWI352779B (en) 2011-11-21
CN101595309A (en) 2009-12-02
KR101122802B1 (en) 2012-03-22
JP5235867B2 (en) 2013-07-10
WO2008123212A1 (en) 2008-10-16
EP2131041A1 (en) 2009-12-09
ES2689721T3 (en) 2018-11-15
TW200916662A (en) 2009-04-16
EP2131041A4 (en) 2013-11-13
AU2008236113B2 (en) 2010-11-18
JPWO2008123212A1 (en) 2010-07-15

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