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WO2017085889A1 - Ventilateur centrifuge, climatiseur et dispositif à cycle frigorifique - Google Patents

Ventilateur centrifuge, climatiseur et dispositif à cycle frigorifique Download PDF

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Publication number
WO2017085889A1
WO2017085889A1 PCT/JP2015/082791 JP2015082791W WO2017085889A1 WO 2017085889 A1 WO2017085889 A1 WO 2017085889A1 JP 2015082791 W JP2015082791 W JP 2015082791W WO 2017085889 A1 WO2017085889 A1 WO 2017085889A1
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WO
WIPO (PCT)
Prior art keywords
blade
region
centrifugal fan
inner peripheral
plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/082791
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English (en)
Japanese (ja)
Inventor
惇司 河野
池田　尚史
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2017551511A priority Critical patent/JP6430032B2/ja
Priority to PCT/JP2015/082791 priority patent/WO2017085889A1/fr
Publication of WO2017085889A1 publication Critical patent/WO2017085889A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • 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
    • 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

Definitions

  • the present invention relates to a centrifugal fan, an air conditioner including the centrifugal fan, and a refrigeration cycle apparatus.
  • Patent Document 1 JP-A-6-299994 discloses a multiblade centrifugal fan.
  • the centrifugal fan disclosed in Patent Document 1 has a configuration in which the entrance angles on the main plate side and the side plate side of the blades are different from each other.
  • Patent Document 1 in the axial direction from the side plate to the main plate, a portion of 30% to 40% of the total blade width is used as a boundary, and the inlet portion of the blade is divided from the boundary into the side plate side and the main plate side.
  • the blades are configured to have different entrance angles on the side plate side and the main plate side.
  • blade are reduced by such a structure.
  • the present invention has been made in order to solve the above-described problems, and an object of the present invention is to suppress the separation of air currents on the blade surface in the entire width direction of the blade, and to achieve high-efficiency and low-noise centrifugal.
  • an object of the present invention is to suppress the separation of air currents on the blade surface in the entire width direction of the blade, and to achieve high-efficiency and low-noise centrifugal.
  • the centrifugal fan according to the present invention includes a main plate having a main surface, a ring-shaped side plate facing the main surface, and a plurality of blades provided between the main plate and the side plate. On the inner peripheral side of the plurality of blades, the plurality of blades have a blade inlet angle.
  • Each of the plurality of wings has a first region, a second region, and a third region. The first region is connected to the main plate. The third region is connected to the side plate. The second region is located between the first region and the third region.
  • the blade inlet angle in the first region of at least one blade of the plurality of blades is greater than the blade inlet angle in the second region of the at least one blade.
  • the blade inlet angle in the third region of the at least one wing is smaller than the blade inlet angle in the second region of the at least one wing.
  • the angle of attack of the blade is made uniform in the blade width direction, separation from the front edge of the blade surface side on the counter-rotation direction side and the blade surface side on the rotation direction side is suppressed, and high efficiency is achieved. Low noise can be achieved.
  • FIG. 1 It is a perspective schematic diagram of the indoor unit of the air-conditioning apparatus according to Embodiment 1 of the present invention. It is a schematic diagram which shows the internal structure of the indoor unit of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a perspective schematic diagram of the centrifugal fan which concerns on Embodiment 1 of this invention. It is a partial expansion schematic diagram of the centrifugal fan according to Embodiment 1 of the present invention. It is the schematic diagram which looked at the blade
  • FIG. 1 is a schematic perspective view of an indoor unit of an air conditioner equipped with a centrifugal fan according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic diagram showing the internal configuration of the indoor unit of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the indoor unit of the air conditioner includes a case 1 installed behind the ceiling of a space to be air-conditioned.
  • the shape of case 1 can employ
  • the case 1 is formed in a rectangular parallelepiped shape.
  • Case 1 includes an upper surface portion 1a, a lower surface portion 1b, and a side surface portion 1c.
  • the air outlet 2 is provided on one surface of the side surface portion 1c of the case 1.
  • Arbitrary shapes can be employ
  • FIG. The shape of the blower outlet 2 is a rectangular shape, for example.
  • the suction inlet 8 is formed in the surface on the opposite side to the surface in which the blower outlet 2 was formed among the side surface parts 1c of the case 1.
  • FIG. Arbitrary shapes can be employ
  • the shape of the suction port 8 is, for example, a rectangular shape.
  • the suction port 8 may be provided with a filter for removing air.
  • a centrifugal fan 3 in which a bell mouth 5 is installed, a fan motor 4, a heat exchanger 6, and a spiral casing 7 are accommodated.
  • the fan motor 4 is supported by a motor support fixed to the upper surface portion 1a of the case 1, for example.
  • the fan motor 4 has a rotating shaft.
  • the rotating shaft is arranged so as to extend in parallel to the surface of the side surface portion 1c where the inlet 8 is formed and the surface where the outlet 2 is formed.
  • a centrifugal fan 3 which is a multiblade centrifugal fan is attached to the rotating shaft. At least one centrifugal fan 3 is attached to the rotating shaft. In the indoor unit shown in FIG. 2, two centrifugal fans 3 are attached to the rotating shaft.
  • the centrifugal fan 3 creates a flow of air that is sucked into the case 1 from the suction port 8 and blown out from the blowout port 2 to the target space.
  • the heat exchanger 6 is disposed in the air flow path.
  • the heat exchanger 6 adjusts the temperature of the air.
  • the spiral casing 7 is provided so as to surround the centrifugal fan 3.
  • the vortex casing 7 rectifies the air blown from the centrifugal fan 3.
  • a bell mouth 5 is disposed at the suction port of the spiral casing 7.
  • the bell mouth 5 is disposed at a position facing the suction port of the centrifugal fan 3.
  • the bell mouth 5 rectifies the airflow flowing into the centrifugal fan 3.
  • the space on the suction side of the bell mouth 5 and the space on the blow-out side of the spiral casing 7 are partitioned by a partition plate. Note that the configurations and modes of the bell mouth 5 and the heat exchanger 6 are not particularly limited, and well-known ones are used in the first embodiment.
  • FIG. 3 is a schematic perspective view of the centrifugal fan 3.
  • FIG. 4 is an enlarged schematic view of the blade of the centrifugal fan shown in FIG.
  • FIG. 5 is a schematic view of the blades of the centrifugal fan 3 as viewed from the axial direction.
  • the centrifugal fan 3 includes a main plate 3a, a side plate 3c, and a plurality of blades 3d.
  • the main plate 3a rotates around the rotation axis.
  • the side plate 3c is provided so as to face the main plate 3a and has a ring shape.
  • the plurality of blades 3d are provided between the main plate 3a and the side plate 3c. On the inner peripheral side of the plurality of blades 3d, the plurality of blades 3d have blade inlet angles ⁇ 1 to ⁇ 3.
  • Each of the plurality of blades 3d has a first region, a second region, and a third region.
  • the first region is connected to the main plate 3a.
  • the third region is connected to the side plate 3c.
  • the second region is located between the first region and the third region.
  • the blade inlet angle ⁇ 1 in the first region of at least one blade 3d of the plurality of blades 3d is larger than the blade inlet angle ⁇ 2 in the second region of the at least one blade 3d.
  • the blade inlet angle ⁇ 3 in the third region of the at least one blade 3d is smaller than the blade inlet angle ⁇ 2 in the second region of the at least one blade 3d.
  • a region on the main plate 3a side from the first position A of the blade 3d is defined as a first region.
  • a region from the first position A to the second position B of the blade 3d is defined as a second region.
  • a region on the side plate 3c side from the second position B of the blade 3d is defined as a third region.
  • the blade inlet angle ⁇ 1 on the inner peripheral side of the blade 3d in the first region is larger than the blade inlet angle ⁇ 2 in the second region of the blade 3d.
  • the blade inlet angle ⁇ 3 in the third region of the blade is smaller than the blade inlet angle ⁇ 2 in the second region.
  • the blade 3d includes an outer peripheral side edge 13b and an inner peripheral side edge 13a.
  • the width of the first region is the distance L1.
  • the width of the second region is the distance (L2-L1).
  • the width of the third region is the distance L3.
  • the main plate 3a has a disk shape.
  • the main plate 3a has a boss 3b at the center thereof.
  • the output shaft of the fan motor 4 (see FIG. 2) is connected to the center of the boss 3b.
  • the centrifugal fan 3 is rotated by the driving force of the fan motor 4.
  • the side plate 3c is disposed so as to face the main plate 3a.
  • the plurality of blades 3d are provided so as to surround the rotation axis X in an annular shape from the main plate 3a toward the side plate 3c.
  • the plurality of blades 3d have the same shape.
  • Each of the blades 3d has an inner peripheral side front edge 9a, an outer peripheral side rear edge 9b, a rotation direction side blade surface 9c, a counter rotation direction side blade surface 9d, and a side plate side end surface 9e.
  • the blade surface 9c on the rotation direction side is a pressure surface.
  • the blade surface 9d on the counter-rotation direction side is a suction surface.
  • the blade surface 9c on the rotation direction side is concave with respect to the air path between the blades.
  • the blade surface 9d on the side opposite to the rotation direction is convex with respect to the air path between the blades.
  • the blade 3d is a forward-facing blade in which the outer peripheral side rear edge 9b is positioned to move forward in the rotational direction from the inner peripheral side front edge 9a.
  • the blade inlet angles ⁇ 1, ⁇ 2, and ⁇ 3 at the inner circumferential front edge 9a of the blade 3d are the inner circumferential front edge 9a from the tangent line of the blade inscribed circle connecting the inner circumferential front edge 9a to the rotational direction side. Is defined by the angle formed by the tangent to the blade center line 9f.
  • the cross-sectional contour 9g on the inner peripheral side of the blade 3d in the first region is inclined toward the half rotation direction side as compared with the cross-sectional contour 9h on the inner peripheral side of the blade 3d in the second region.
  • the cross-sectional contour 9i on the inner peripheral side of the blade 3d in the third region is inclined to the rotational direction side as compared with the cross-sectional contour 9h on the inner peripheral side of the blade 3d in the second region.
  • FIG. 6 shows a change in the blade inlet angle in the blade width direction in the centrifugal fan 3 according to the present embodiment.
  • the horizontal axis in FIG. 6 indicates the position in the blade width direction, and the vertical axis indicates the blade inlet angle.
  • the blade inlet angle ⁇ 2 in the second region described above is constant.
  • the blade inlet angle ⁇ 1 gradually increases from the position A away from the main plate 3a by the first distance toward the main plate 3a. Specifically, the position of the end portion on the inner peripheral side of the blade center line 9f of the blade 3d gradually moves to the counter-rotation direction side toward the main plate 3a in the first region.
  • the blade inlet angle ⁇ 3 gradually decreases from the position B away from the main plate 3a by the second distance toward the side plate 3c. Specifically, the position of the end portion on the inner peripheral side of the blade center line 9f of the blade 3d gradually moves to the rotational direction side toward the side plate 3c in the third region.
  • the blade inlet angle ⁇ is maximized at the end portion on the main plate 3a side and is minimized at the end portion on the side plate 3c side. As shown in FIG. 6, the blade inlet angle ⁇ smoothly changes from the main plate 3a side to the side plate 3c side in the width direction of the blade 3d.
  • the angle of attack of the blade 3d is defined as the airflow inflow angle at the leading edge (inner peripheral side) of the blade 3d.
  • an angle formed by the direction of the airflow at the leading edge of the blade 3d from the tangent line of the circle around the rotation axis X to the rotation direction is defined as the angle of attack.
  • FIG. 7 is a graph showing the change in the angle of attack in the blade width direction when the blade inlet angle is constant in the width direction.
  • the horizontal axis of FIG. 7 shows the position in the width direction of a wing
  • the angle of attack also referred to as the inflow angle
  • the angle of attack decreases as the side plate 3c is approached. This is because the inflow speed between the blades is small on the side plate 3c side.
  • the first distance L1 (see FIG. 4) indicating the first position A is the blade width in the direction from the main plate 3a to the side plate 3c (in FIG. 4).
  • the distance L2 + the distance L3) is 20% or less.
  • the second distance L2 (see FIG. 4) indicating the second position B is, for example, 80% or more of the blade width in the direction from the main plate 3a to the side plate 3c.
  • the width (distance L1) of the first region is 20% or less of the blade width in the direction from the main plate 3a to the side plate 3c.
  • the width of the third region (distance L3 in FIG. 4) is 20% or less of the blade width in the direction from the main plate 3a to the side plate 3c.
  • the centrifugal fan 3 of the first embodiment the separation of the airflow from the main plate 3a to the side plate 3c can be suppressed. Therefore, high efficiency and low noise of the centrifugal fan 3 can be achieved by reducing the turbulence of the airflow.
  • the blade inlet angle ⁇ in the width direction of the blade 3d it is possible to suppress variations in the angle of attack in the width direction of the blade 3d. For this reason, about the whole width direction area
  • the first distance may be 20% or less of the blade width in the direction from the main plate 3a to the side plate 3c.
  • the first distance may be 15% or less of the blade width.
  • the second distance may be 80% or more of the blade width in the direction from the main plate 3a toward the side plate 3c.
  • the second distance may be 85% or more of the blade width.
  • the blade inlet angle ⁇ can be adjusted particularly in a region where the angle of attack varies in the main plate 3a side or the side plate 3c side of the blade 3d.
  • FIG. 8 is a schematic view of the blades of the centrifugal fan 3 according to the present embodiment as viewed from the axial direction.
  • the centrifugal fan 3 according to the second embodiment basically has the same configuration as the centrifugal fan 3 according to the first embodiment of the present invention, but the cross-sectional shape of the blade 3d is the centrifugal fan according to the first embodiment. 3 and different. That is, in the centrifugal fan 3 shown in FIG. 8, the blade thickness on the inner peripheral side of the blade 3d in the first region on the main plate 3a side is larger than the second region of the blade 3d. That is, the blade thickness increases in the counter-rotating direction. For this reason, the position of the edge part of the inner peripheral side of the blade center line 9f of the blade 3d in the first region is shifted from the second region to the counter-rotation direction side. More specifically, in the first region, the position of the end portion on the inner peripheral side of the blade center line 9f moves to the counter-rotation direction side as it approaches the main plate 3a.
  • the blade thickness on the inner peripheral side of the blade 3d in the third region on the side plate 3c side is smaller than the second region of the blade 3d. That is, the blade thickness is reduced in the rotational direction. For this reason, the position of the edge part of the inner peripheral side of the blade center line 9f of the blade 3d in the third region is shifted from the second region to the rotational direction side. More specifically, in the third region, as the side plate 3c is approached, the position of the end portion on the inner peripheral side of the blade center line 9f moves to the rotational direction side.
  • the blade thickness on the inner peripheral side of the blade 3d in the first region is thicker than the blade thickness on the inner peripheral side of the blade 3d in the second region.
  • the blade surface on the inner peripheral side of the blade 3d in the second region and on the counter-rotation direction side is opposed to the blade surface on the inner periphery side of the blade 3d in the first region and on the counter-rotation direction side. It protrudes.
  • the blade thickness on the inner peripheral side of the blade 3d in the third region is thinner than the blade thickness on the inner peripheral side of the blade 3d in the second region.
  • the blade surface on the inner peripheral side of the blade 3d in the second region and the blade surface on the counter-rotation direction side is recessed in the rotation direction on the inner periphery side of the blade 3d in the third region and on the counter-rotation direction side. It is out.
  • the same effect as the centrifugal fan 3 according to the first embodiment can be obtained.
  • the blade thickness on the inner peripheral side of the blade 3d gradually decreases in the width direction from the first region to the second region and the third region. For this reason, for example, when the wing 3d is molded using a mold, the mold can be separated from the wing 3d from the third region side, that is, the side plate 3c side.
  • the distance between the blades on the main plate 3a side is small and the ventilation resistance can be increased.
  • the distance between the blades is large on the side plate 3c side, and the ventilation resistance can be reduced. For this reason, the flow biased toward the main plate 3a can be made uniform in the blade width direction. As a result, friction loss and vortices caused by wind speed differences in the blade width direction can be suppressed. Therefore, high efficiency and low noise of the centrifugal fan 3 can be achieved.
  • FIG. 9 is a partially enlarged schematic view of the centrifugal fan 3 according to the present embodiment.
  • the centrifugal fan 3 according to the third embodiment basically has the same configuration as the centrifugal fan 3 according to the first embodiment of the present invention, but the shape of the blade 3d is the centrifugal fan 3 according to the first embodiment. Is different. That is, in Embodiment 3, the centrifugal fan 3 further includes a bell mouth 5 that is disposed on the side plate 3c side and includes an opening 5a that faces the wing 3d. The inner diameter of the opening 5a of the bell mouth 5 is larger than the inner diameter of the plurality of blades 3d arranged in an annular shape along the side plate 3c. On the inner peripheral side of the opening 5a of the bell mouth 5, the end 19a on the side plate 3c side of the wing 3d is inclined in the rotational direction.
  • the inner diameter of the plurality of blades 3d arranged in an annular shape means that the inner diameter side of the annular region occupied by the blades 3d when the plurality of blades 3d arranged in a ring shape are viewed from the axial direction. It means the diameter of the opening to be formed.
  • the inner diameter of the downstream end of the opening 5a of the bell mouth 5 (see FIG. 2) is larger than the inner diameter of the blade 3d of the centrifugal fan 3.
  • An inner peripheral front edge 9 a of the wing 3 d protrudes from the opening 5 a of the bell mouth 5.
  • the side plate side blade end (end portion 19a) of the blade 3d is inclined in the rotational direction.
  • the side plate side blade end (end portion 19b) of the blade 3d faces the counter-rotation direction side from the side plate side blade end on the inner peripheral side.
  • the end 19b of the blade 3d on the outer peripheral side of the opening 5a is also basically inclined in the rotational direction in the blade width direction.
  • the inclination of the end portion 19b in the rotation direction is smaller than the inclination in the rotation direction in the blade width direction with respect to the end portion 19a of the blade 3d on the inner peripheral side from the opening 5a.
  • Both the rotation direction side surface and the counter rotation direction side surface of the end portions 19a and 19b are curved.
  • the separation of the airflow flowing from the end portions 19a and 19b of the side plate side wings is further suppressed. it can.
  • FIG. 10 is a configuration diagram of an air-conditioning apparatus according to Embodiment 4 of the present invention.
  • an air conditioner as a refrigeration cycle apparatus having an indoor unit 200 including the centrifugal fan described above will be described.
  • the air conditioner shown in FIG. 10 includes an outdoor unit 100 and an indoor unit 200.
  • the outdoor unit 100 and the indoor unit 200 are connected by a refrigerant pipe to form a refrigerant circuit.
  • a refrigerant is circulated in the refrigerant circuit.
  • a pipe through which a gaseous refrigerant (gas refrigerant) flows is referred to as a gas pipe 300.
  • a pipe through which a liquid-containing refrigerant (a liquid refrigerant or a gas-liquid two-phase refrigerant may flow) flows is referred to as a liquid pipe 400.
  • the outdoor unit 100 includes a compressor 101, a four-way valve 102, an outdoor heat exchanger 103, an outdoor blower 104, and a throttle device (expansion valve) 105.
  • Compressor 101 compresses and discharges the sucked refrigerant.
  • the compressor 101 includes an inverter device or the like, and can arbitrarily change the capacity of the compressor 101 (the amount of refrigerant sent out per unit time) by arbitrarily changing the operation frequency.
  • the four-way valve 102 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from a control device (not shown).
  • the outdoor heat exchanger 103 exchanges heat between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation, and performs heat exchange between the low-pressure refrigerant flowing from the liquid pipe 400 and the air. In this case, the outdoor heat exchanger 103 evaporates and vaporizes the refrigerant. Further, during the cooling operation, the outdoor heat exchanger 103 functions as a condenser. In this case, the refrigerant compressed in the compressor 101 flows into the outdoor heat exchanger 103 from the four-way valve 102 side. In the outdoor heat exchanger 103, heat is exchanged between the refrigerant and air, and the refrigerant is condensed and liquefied.
  • the outdoor heat exchanger 103 is provided with an outdoor fan 104 having the centrifugal fan 3 described in the first to third embodiments in order to efficiently exchange heat between the refrigerant and the air.
  • the rotational speed of the centrifugal fan 3 as the blower fan may be finely changed by arbitrarily changing the operating frequency of the fan motor by the inverter device.
  • the expansion device 105 is provided to adjust the refrigerant pressure or the like by changing the opening degree.
  • the indoor unit 200 includes a load side heat exchanger 201 and a load side blower 202.
  • the load side heat exchanger 201 performs heat exchange between the refrigerant and air. For example, it functions as a condenser during heating operation.
  • the load-side heat exchanger 201 performs heat exchange between the refrigerant flowing in from the gas pipe 300 and the air, condensing the refrigerant and liquefying (or gas-liquid two-phase). As a result, the liquefied refrigerant flows out from the load side heat exchanger 201 to the liquid pipe 400 side.
  • the load-side heat exchanger 201 functions as an evaporator.
  • the load-side heat exchanger 201 performs heat exchange between the refrigerant and the air that have been brought into a low pressure state by the expansion device 105.
  • the refrigerant is vaporized by causing the refrigerant to take heat of the air and evaporate it.
  • the refrigerant evaporated from the load side heat exchanger 201 flows out to the gas pipe 300 side.
  • the indoor unit 200 is provided with a load-side blower 202 for adjusting the flow of air for heat exchange.
  • the operating speed of the load-side blower 202 is determined by, for example, user settings.
  • the centrifugal fan described in the first to third embodiments can be used for the load-side blower 202.
  • the air conditioner according to the fourth embodiment by using the blower described in the first to third embodiments for the outdoor unit 100 and further for the indoor unit 200, air volume reduction, noise suppression, and the like can be realized. Can do.
  • the present invention can be widely used not only for indoor units constituting a refrigeration cycle apparatus, for example, indoor units for air conditioners, but also for various devices and facilities in which a centrifugal fan is installed.
  • the present invention is particularly advantageously applied to a multiblade centrifugal fan.

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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)

Abstract

La présente invention concerne un ventilateur centrifuge qui fonctionne de façon silencieuse à haute efficacité. Le ventilateur centrifuge est pourvu d'un panneau principal, d'un panneau latéral et d'une pluralité de pales. Le panneau latéral, qui est disposé de façon à faire face au panneau principal, a la forme d'un anneau. La pluralité de pales est disposée entre le panneau principal et le panneau latéral. Du côté périphérique interne de la pluralité de pales, la pluralité de pales a un angle d'incidence de pale θ1-θ3. Chacune de la pluralité de pales a une première section, une deuxième section et une troisième section. La première section est reliée au panneau principal. La troisième section est reliée au panneau latéral. La deuxième section est placée entre la première section et la troisième section. L'angle θ1 d'incidence de pale dans la première section d'au moins l'une de la pluralité de pales est supérieur à l'angle θ2 d'incidence de pale dans la deuxième section de ladite pale. L'angle θ3 d'incidence de pale dans la troisième section de ladite pale est inférieur à l'angle θ2 d'incidence de pale dans la deuxième section de ladite pale.
PCT/JP2015/082791 2015-11-20 2015-11-20 Ventilateur centrifuge, climatiseur et dispositif à cycle frigorifique Ceased WO2017085889A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2017551511A JP6430032B2 (ja) 2015-11-20 2015-11-20 遠心ファン、空気調和装置および冷凍サイクル装置
PCT/JP2015/082791 WO2017085889A1 (fr) 2015-11-20 2015-11-20 Ventilateur centrifuge, climatiseur et dispositif à cycle frigorifique

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PCT/JP2015/082791 WO2017085889A1 (fr) 2015-11-20 2015-11-20 Ventilateur centrifuge, climatiseur et dispositif à cycle frigorifique

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US11421702B2 (en) 2019-08-21 2022-08-23 Pratt & Whitney Canada Corp. Impeller with chordwise vane thickness variation

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JP2007170331A (ja) * 2005-12-26 2007-07-05 Daikin Ind Ltd ターボファン及びこれを用いた空気調和機の室内ユニット
JP2010174671A (ja) * 2009-01-28 2010-08-12 Mitsubishi Electric Corp ターボファン及びターボファンを備えた空気調和装置
WO2015045907A1 (fr) * 2013-09-30 2015-04-02 ダイキン工業株式会社 Ventilateur centrifuge et climatiseur pourvu de celui-ci

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