EP2902639B1 - Ventilateur hélicoïdal et climatiseur équipé de celui-ci - Google Patents

Ventilateur hélicoïdal et climatiseur équipé de celui-ci Download PDF

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Publication number
EP2902639B1
EP2902639B1 EP13841827.2A EP13841827A EP2902639B1 EP 2902639 B1 EP2902639 B1 EP 2902639B1 EP 13841827 A EP13841827 A EP 13841827A EP 2902639 B1 EP2902639 B1 EP 2902639B1
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EP
European Patent Office
Prior art keywords
blade
pressure surface
propeller fan
radius
region
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.)
Active
Application number
EP13841827.2A
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German (de)
English (en)
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EP2902639A4 (fr
EP2902639A1 (fr
Inventor
Kiyonori YOKOSE
Shimei Tei
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP2902639A1 publication Critical patent/EP2902639A1/fr
Publication of EP2902639A4 publication Critical patent/EP2902639A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • 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
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • 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
    • F05D2250/71—Shape curved
    • F05D2250/712—Shape curved concave

Definitions

  • the present invention relates to a propeller fan and an air conditioner including the same.
  • propeller fans for use in an air conditioner and the like.
  • Rotation of the propeller fan generates airflow (leakage flow) in the vicinity of an outer peripheral portion of a blade, the airflow passing from a pressure surface side of the blade where pressure is high to a suction surface side of the blade where pressure is low.
  • the airflow causes vortex flows (wing tip vortexes) in the vicinity of the outer peripheral portion of the blade.
  • wing tip vortex is liable to cause noise.
  • a propeller fan of Patent Literature 1 an outer peripheral portion of a blade is provided with a bent portion for stabilizing a wing tip vortex, thereby attempting to reduce noise.
  • a propeller fan of Patent Literature 2 includes a hub and a plurality of blades, which are radially arranged on the outer circumference of the hub.
  • a plurality of bent surface-shaped recesses are formed on the positive pressure surface at a trailing edge of each blade.
  • the recesses extend in the rotation direction of the fan and are arranged in a radial direction.
  • Protrusions are each formed between adjacent pair of the recesses. The bent surfaces of the recesses and the protrusions reduces air flow caused by centrifugal force.
  • the present invention aims to provide a propeller fan capable of reducing noise.
  • a propeller fan of the present invention includes a hub and a plurality of blades.
  • the pressure surface of the inner region and the pressure surface of the outer region each have single concave curve surface, when seen in a plane that includes the
  • FIG. 1 is a sectional view showing a general structure of an outdoor unit 1 of an air conditioner according to an embodiment of the present invention.
  • the air conditioner includes the outdoor unit 1 shown in FIG. 1 and an unillustrated indoor unit.
  • the outdoor unit 1 includes an outdoor heat exchanger 3, a propeller fan 4, a motor 5 and an unillustrated compressor, which are placed in a casing 2.
  • the indoor unit includes unillustrated expansion mechanism and indoor heat exchanger, for example.
  • the compressor, the outdoor heat exchanger 3, the expansion mechanism, the indoor heat exchanger, and an unillustrated refrigerant pipe connecting these components constitute a refrigerant circuit of the air conditioner.
  • the outdoor heat exchanger 3 is provided at the back surface side of the casing 2, and a discharge port 7 is provided at the front surface side of the casing 2.
  • the invention is not limited to this configuration.
  • the discharge port 7 may be provided in a top portion of the casing 2.
  • the discharge port 7 is provided with a fan guard 7a in the form of a grill.
  • the propeller fan 4 is located inside the discharge port 7 of the casing 2.
  • the propeller fan 4 is connected to a shaft 5a of the motor 5, and is driven to rotate around a rotation axis A0 by the motor 5.
  • the rotation axis A0 of the propeller fan 4 lies in a forward-backward direction (horizontal direction).
  • the rotation axis A0 may lie in a direction oblique to the horizontal direction, for example.
  • the rotation axis A0 of the propeller fan 4 may lie in a top-bottom direction (vertical direction).
  • a bell mouth 6 surrounding the outer circumference of the propeller fan 4 is provided in the casing 2.
  • the bell mouth 6 is disposed between a region X (suction region X) that lies upstream of the propeller fan 4 in a direction of airflow and a region Y (discharge region Y) that lies downstream of the propeller fan 4 in the airflow direction.
  • the bell mouth 6 is in the form of a ring and extends around the propeller fan 4 for guiding air that has passed through the outdoor heat exchanger 3 to the discharge port 7.
  • the bell mouth 6 is slightly spaced from the propeller fan 4 so as not to be in contact with the propeller fan 4.
  • the propeller fan 4, the motor 5, and the bell mouth 6 constitute an axial flow blower 8. Rotation of the propeller fan 4 driven by the motor 5 of the axial flow blower 8 generates a pressure difference between the suction region X and the discharge region Y, which generates airflow passing from the suction region X to the discharge region Y.
  • FIG. 2 is a front view of a propeller fan 4 according to a first embodiment of the present invention.
  • the propeller fan 4 includes a hub 11 and a plurality of blades 12.
  • the propeller fan 4 includes three blades 12.
  • the invention is not limited to this configuration, and the propeller fan 4 may alternatively include two blades 12 or four or more blades 12.
  • the hub 11 and the plurality of blades 12 are integrally molded.
  • the invention is not limited to this configuration, and a plurality of components may be individually molded and then bonded together to form the propeller fan 4.
  • the hub 11 is generally in the form of a cylinder, a truncated cone or the like, but is not limited to these shapes.
  • the hub 11 has an outer circumferential surface 11a joining the plurality of blades 12.
  • the plurality of blades 12 are disposed at regular intervals along the outer circumferential surface 11a of the hub 11.
  • the hub 11 has a substantially uniform outer diameter.
  • the hub 11 may be in the form of a combination of a cylinder and a truncated cone, for example, or may have another shape.
  • the rotation axis A0 of the propeller fan 4 lies at the center of the hub 11.
  • Each of the blades 12 includes an inner peripheral portion 13 located at radially inner side (hub 11 side) and connected to the hub 11, a leading edge 14 located at front side in a rotational direction D, a trailing edge 15 located at rear side in the rotational direction D (reverse side in the rotational direction D), and an outer peripheral portion 16 located at radially outer side.
  • the blade 12 has a twisted shape in which the leading edge 14 is totally located at the side of the suction region X in comparison with the trailing edge 15. Further, the blade 12 has a pressure surface 21 located at the side of the discharge port 7 (the side of the discharge region Y), and a negative pressure surface 22 (see FIG. 6 ) located at the opposite side of the pressure surface 21 (the side of the suction region X).
  • the outer peripheral portion 16 includes a bent portion 17 at which an end of the blade 12 is bent on the suction surface 22 (toward the suction region X), and an outer peripheral edge 18 defining a radially outer edge of the blade 12.
  • the outer peripheral portion 16 has a width extending from the bent portion 17 to the outer peripheral edge 18. The bent portion 17 makes it possible to prevent vortexes from occurring in the vicinity of the outer peripheral portion 16 of the blade 12.
  • the bent portion 17 extends from the leading edge 14 (or the vicinity of the leading edge 14) to the trailing edge 15.
  • the width of the outer peripheral portion 16 (distance between the bent portion 17 and the outer peripheral edge 18) increases toward the trailing edge 15.
  • the invention is not limited to this configuration. Further, the bent portion 17 may be omitted, in which case, the outer peripheral portion 16 is defined by the outer peripheral edge 18.
  • outlet angles ⁇ at the trailing edge 15, which is a feature of the propeller fan 4 of the first embodiment, will be described.
  • the solid line indicates a relationship between radii and outlet angles ⁇ at the trailing edge 15 of the propeller fan 4 of the first embodiment shown in FIGS. 2 and 4A
  • the broken line indicates a relationship between radii and outlet angles ⁇ at a trailing edge 115 of a propeller fan 104 of a reference example shown in FIG. 4B .
  • the propeller fan 104 of the reference example will be briefly described.
  • the propeller fan 104 of the reference example includes a hub 111 and three blades 112.
  • Each of the blades 112 includes an inner peripheral portion 113, a leading edge 114, a trailing edge 115, and an outer peripheral portion 116 (a bent portion 117 and an outer peripheral edge 118). Further, the blade 112 has a pressure surface 121 and a negative pressure surface 122 (see FIG. 7C ).
  • a plurality of peak outlet angles ⁇ exist at the trailing edge 15 of the blade 12 of the propeller fan 4 of the first embodiment. Specifically, two peak outlet angles ⁇ exist at the trailing edge 15 of the blade 12. One of the peak outlet angle at the trailing edge 15 exists in the outer region 12 that is located radially outer than the representative square mean radius position. The other of the peak outlet angle at the trailing edge 15 exists in the inner region 12A that is located radially inner than the representative square mean radius position.
  • the blade 12 of the reference example shown in FIG. 4B has only one peak outlet angle ⁇ at the trailing edge 15.
  • the peak outlet angle ⁇ is disposed at the trailing edge 115 in an outer region of the blade 112 which is located radially outer than the representative square mean radius position Rr.
  • the blade 112 of the reference example has progressively greater outlet angles ⁇ from the inner peripheral portion 113 toward the outer peripheral portion 116 at the trailing edge 115, the peak outlet angle ⁇ being disposed in the outer region located radially outer than the representative square mean radius position (at a position close to the outer peripheral portion 116).
  • the representative square mean radius position Rr bisects a flow area of the propeller fan 4 (104) into a central side portion (hub side portion) and an outer peripheral side portion.
  • FIG. 5 is a diagram for explaining the representative square mean radius position Rr of the propeller fan 4 (104).
  • the representative square mean radius position Rr is calculated by the following formula (1) wherein "R” represents a representative radius of the blade 12 (112) and "r” represents a representative radius of the hub 11 (111).
  • representative square mean radius position Rr R 2 + r 2 / 2 0.5
  • the representative radius R of the blade is calculated as follows.
  • the representative radius R of the blade is equal to a half of the outer diameter.
  • the representative radius R of the blade is calculated as follows.
  • the representative radius r of the hub is, in the case where the outer diameter of the hub is uniform along the rotation axis, equal to a half of the outer diameter.
  • the representative radius r of the hub is calculated as follows.
  • radius lines A1 to A5 shown in FIG. 3 correspond to radius lines A1 to A5 shown in FIGS. 4A and 4B .
  • the radius line A1 is on the blade 12 (112) and a part of a circle having the radius A1 and centered on the rotation axis A0, in a front view of the propeller fan, as shown in FIGS. 4A and 4B .
  • the same description is applicable to the radius lines A2 to A5, and is therefore omitted.
  • the radius line A3 lies on the representative square mean radius position Rr.
  • the radius line A3 bears an outlet angle ⁇ 3 having a minimum value between the two peak outlet angles.
  • the radius lines A1 and A2 are located in the inner region 12A that is located at the side of the hub 11 than radius line A3.
  • the radius lines A4 and A5 are located in the outer region 12B that is located at the side of the outer peripheral portion 16 than radius line A3.
  • FIG. 6 is a circumferential sectional view of the blade 12 (for example, a sectional view taken along the radius line A3 shown in FIG. 4 ).
  • an outlet angle ⁇ at the trailing edge 15 is defined by an angle between a tangent line L3 contacting to the pressure surface 21 at the trailing edge 15 and a straight line L4 perpendicularly intersecting the rotation axis A0 of the propeller fan 4.
  • the peak outlet angle ⁇ in the inner region 12A in other words, the outlet angle ⁇ having a maximum value in the inner region 12A, is an outlet angle ⁇ 2 at the radius A2 (first peak position).
  • the peak outlet angle ⁇ in the outer region 12B in other words, the outlet angle having a maximum value in the outer region 12B, is an outlet angle ⁇ 4 at the radius A4 (second peak position).
  • the outlet angle ⁇ 3 at the radius A3 is smaller than the outlet angles ⁇ 2 and ⁇ 4.
  • the outlet angle ⁇ having a minimum value between the two peak outlet angles (between the radius A2 and the radius A4) is the outlet angle ⁇ 3 at the representative square mean radius position Rr (radius A3).
  • the outlet angles ⁇ progressively increase from the inner peripheral portion 13 to the radius A2 and progressively decrease from the radius A4 to the outer peripheral portion 16 (bent portion 17) at the trailing edge 15. Further, the outlet angles ⁇ progressively decrease from the radius A2 to the radius A3 and progressively increase from the radius A3 to the radius A4 at the trailing edge 15. In other words, the outlet angles ⁇ at the trailing edge 15 change in a substantially M-shaped curve as shown in FIG. 3 .
  • a specific example of differences between the outlet angles ⁇ 2 and ⁇ 4 at the peak radii and the outlet angle ⁇ 3 located therebetween and having a minimum value is provided as follows.
  • the difference between the outlet angle ⁇ 2 and the outlet angle ⁇ 3 may be set to fall within the range from 0.5 to 10 degrees or the range from 1 to 5 degrees, for example.
  • the difference between the outlet angle ⁇ 4 and the outlet angle ⁇ 3 may be set to fall within the range from 0.5 to 10 degrees or the range from 1 to 5 degrees, for example.
  • FIG. 3 shows an example in which the outlet angle ⁇ 2 at the radius A2 (first peak position) and the outlet angle ⁇ 4 at the radius A4 (second peak position) have the same value.
  • the outlet angles ⁇ 2 and ⁇ 4 may have different values. Specifically, the outlet angle ⁇ 2 may be greater or smaller than the outlet angle ⁇ 4.
  • FIGS. 7A and 7B are sectional views taken along the line VIIA-VIIA in FIG. 4A .
  • FIGS. 7A and 7B are sectional views obtained by cutting the propeller fan 4 of the first embodiment at a plane including the rotation axis A0.
  • FIG. 7C is a sectional view taken along the line VIIC-VIIC in FIG. 4B .
  • FIG. 7C is a sectional view obtained by cutting the propeller fan 104 of the reference example at a plane including the rotation axis A0.
  • a pressure surface 21A in the inner region 12A has a concave curve surface
  • a pressure surface 21B in the outer region 12B has an another concave curve surface.
  • the outer pressure surface 21B is located at the region between the representative square mean radius position Rr and the bent portion 17 of the outer peripheral portion 16.
  • the concave curve surface of the inner pressure surface 21A and the concave curve surface of the outer pressure surface 21B adjoin each other via the representative square mean radius position Rr.
  • the concave curve surface of the inner pressure surface 21A and the concave curve surface of the outer pressure surface 21B are adjacently disposed to each other in a radial direction.
  • a pressure surface 21C of the specific region that bears the representative square mean radius position Rr lying on the boundary between the adjoining two concave curve surfaces and the vicinity thereof is in the form of a convex curve surface.
  • the concave curve surface of the inner pressure surface 21A circumferentially extends from the leading edge 14 to the trailing edge 15 and, similarly, the concave curve surface of the outer pressure surface 21B circumferentially extends from the leading edge 14 to the trailing edge 15.
  • the inner pressure surface 21A may be entirely in the form of a concave curve surface, but is not limited to this shape.
  • the inner pressure surface 21A has a concave curve surface in a region close to the representative square mean radius position Rr, but has a flat or substantially flat surface in a region close to the inner peripheral portion 13.
  • the outer pressure surface 21B may be entirely in the form of a concave curve surface, but is not limited to this shape. In the present embodiment, the outer pressure surface 21B is substantially entirely in the form of a concave curve surface.
  • the negative pressure surface 22 extends along the pressure surface 21 in such a manner that the thickness of the blade 12 does not change much over the entire blade. Therefore, the negative pressure surface 22 has a convex curve surface on the opposite side of the concave curve surface of the pressure surface 21 .
  • the inner pressure surface 21A has a maximum radius of curvature greater than a maximum radius of curvature of the outer pressure surface 21B.
  • the inner region 12A includes a negative pressure surface 22A (inner negative pressure surface 22A) having a maximum radius of curvature greater than a maximum radius of curvature of a negative pressure surface 22B (outer negative pressure surface 22B) of the outer region 12B.
  • the inner pressure surface 21A is flatter than the outer pressure surface 21B.
  • the flat shape of the inner pressure surface 21A can also be described as follows.
  • an imaginary straight line L5 is drawn from an end T1 of the pressure surface 21, the end joining the inner peripheral portion 13 to an intersection T2 of the pressure surface 21 with the characteristic root mean square radius line Rr.
  • an imaginary straight line L6 is drawn from an end T3 of the pressure surface 21, the end joining the outer peripheral portion 16 (the bent portion 17 in the present embodiment) to the intersection T2 of the pressure surface 21 with the representative square mean radius position Rr.
  • a maximum value D1 in the varied distances between the imaginary straight line L5 and the pressure surface 21 (inner pressure surface 21A) is smaller than a maximum value D2 in the varied distances between the imaginary straight line L6 and the pressure surface 21 (outer pressure surface 21B),
  • the position that bears the maximum value D1 over the pressure surface 21 is disposed at a position closer to the intersection T2 than the end T1.
  • the position that bears the maximum value D1 over the pressure surface 21 is disposed on the inner pressure surface 21A at a position closer to the representative square mean radius position Rr than the inner peripheral portion 13.
  • a portion that lies in the inner region 12A and is closer to the inner peripheral portion 13 is flatter (more planar) than a portion that lies in the inner region 12A and is closer to the outer peripheral portion 16 (representative square mean radius position Rr).
  • the pressure surface 121 of the blade 112 has a single large convex surface extending from the inner peripheral portion 113 to the bend 117 of the outer peripheral portion 116.
  • the suction surface 122 on the opposite side of the pressure surface 121 has a shape corresponding to the pressure surface 121.
  • the suction surface 122 has a single large convex surface extending from the inner peripheral portion 113 to the bend 117 of the outer peripheral portion 116.
  • the blade 112 of the reference example extends radially, and is curved more greatly in the direction of the rotation axis A0 than the blade 12 of the first embodiment, thereby having a solid shape.
  • an imaginary straight line L11 is drawn from an end T11 of the pressure surface 121, the end joining the inner peripheral portion 113 to an end T12 of the pressure surface 121, the end joining the outer peripheral portion 116 (the bent portion 117 in this reference example).
  • a maximum value D11 in the varied distances between the imaginary straight line L11 and the pressure surface 121 is considerably greater than the maximum values D1 and D2 in the first embodiment.
  • each of the blades 112 has a large sectional area and, therefore, the entire propeller fan has large volume and weight compared to the first embodiment. Accordingly, the propeller fan of the reference example has problems in terms of resource saving, cost reduction, and the like.
  • the blade 112 of the reference example has a solid shape as described, it is liable to elastically deform due to a stress generated by rotation of the propeller fan.
  • the blade 112 of the reference example has a solid shape and includes many causing points of elastic deformation, and is therefore liable to elastically deform in a deformation mode in which the blade 112 is liable to elastically deform into a planar shape (deformation mode in which the blade 112 is liable to expand radially outward) during rotation.
  • the blade 112 of the reference example requires reinforcement for preventing the elastic deformation, which results in a problem of an increased weight.
  • the propeller fan 4 of the first embodiment shown in FIGS. 7A and 7B includes, not a single large concave curve surface as in the reference example, but the combination of two concave curve surfaces as described above.
  • each of the two concave curve surfaces has a peak depth (the maximum values D1 and D2).
  • the depths D1 and D2 (maximum values D1 and D2) of the two concave curve surfaces of the first embodiment are smaller than the depth (maximum value D11) of the concave curve surface of the reference example.
  • the radial length of each of the concave curve surfaces of the first embodiment is smaller than the radial length of the concave curve surface of the reference example.
  • the blade 12 of the first embodiment having the above-described features is flatter (more planar) than the blade 112 of the reference example.
  • the blade 12 of the first embodiment having such shape is allowed to have, in the case of having a thickness distribution from the inner peripheral portion 13 to the outer peripheral portion 16 similar to that of the blade 112 of the reference example, a smaller sectional area than the blade 112 of the reference example. This allows each of the blades 12 to have a small weight and, therefore, allows the entire propeller fan 4 to have a small volume and weight compared to the reference example.
  • the blade 12 of the first embodiment is flatter than the blade 112 of the reference example, it is unlikely to elastically deform due to a stress generated by rotation of the propeller fan 4. In other words, since the blade 12 of the first embodiment usually has a planar shape, the amount of an elastic deformation is small.
  • the momentum of the air flowing along the pressure surface 21 locally changes greatly in the outer pressure surface 21B as shown by arrows in the figure.
  • the momentum of the air flowing along the pressure surface 121 changes over the entire pressure surface 121 as shown by arrows in the figure.
  • the recessed portion 19 is provided on the trailing edge 15 of the blade 12 of the first embodiment, the recessed portion being oriented toward the leading edge 14.
  • the recessed portion 19 is provided in a region bearing the representative square mean radius position Rr.
  • the recessed portion 19 is not an essential constituent and may be omitted.
  • the recessed portion 19 has a substantially V-shape or a substantially U-shape in a front view, for example, but is not limited to these shapes.
  • the provision of the recessed portion 19 at the representative square mean radius position Rr on the trailing edge 15 where the pressure is liable to increase on the pressure surface 21 makes it possible to reduce a pressure rise at the representative square mean radius position Rr on the trailing edge 15. This allows the air flowing along the pressure surface 21 from the leading edge 14 toward the trailing edge 15 to move toward the hub 11 and to the outer peripheral portion 16 in such a manner as to avoid the representative square mean radius position Rr in the vicinity of the trailing edge 15. Therefore, the effect of guiding airflow in a circumferential direction can be enhanced.
  • the effect of guiding airflow in the circumferential direction can be further enhanced by the combination of this effect of guiding airflow in the circumferential direction provided by the recessed portion 19, and the guiding effect provided by disposing the respective peak outlet angles ⁇ in the hub 11-side region and the outer peripheral portion 16 side-region, the regions being on opposite sides of the representative square mean radius position Rr.
  • a bottom 19a of the recessed portion 19 (leading part of the recessed portion 19 in the rotational direction D) lies at the representative square mean radius position Rr.
  • the invention is not limited to this configuration. In the case where the bottom 19a of the recessed portion 19 lies at the representative square mean radius position Rr, the above-described guiding effect can be further enhanced.
  • FIG. 8A is a perspective view showing airflow in the propeller fan according to the first embodiment, and FIG. 8B being a schematic view illustrating the airflow.
  • FIG. 9A is a perspective view showing airflow in the propeller fan of the reference example, and FIG. 9B being a schematic view illustrating the airflow.
  • the effect of guiding airflow in the circumferential direction is high especially in the inner region 12A. This restrains air from flowing to the outer peripheral portion 16.
  • blowing loudness is considerably lower in the first embodiment than in the reference example, as shown in FIG. 10A .
  • the first embodiment makes it possible to, while reducing blowing loudness, obtain an equal air quantity by a substantially equal fan motor input to those of the reference example as shown in FIG. 10B .
  • reduction in weight is achieved without sacrificing blowing performance.
  • FIG. 11A is a front view showing a part of a propeller fan 4 according to a second embodiment which is not part of the invention, and FIG. 11B being a sectional view taken along the line XIB-XIB in FIG. 11A .
  • the propeller fan 4 of the second embodiment differs from the first embodiment in that each of blades 12 has a solid shape similarly to the blade 112 of the reference example.
  • the blade 12 of the second embodiment includes, as shown in FIG. 11B , a pressure surface 21 including a single large concave curve surface extending from an inner peripheral portion 13 to a bent portion 17 of an outer peripheral portion 16.
  • the second embodiment differs from the reference example in that the blade 12 has outlet angles ⁇ having the same features as those of the first embodiment shown in, for example, FIG. 3 .
  • the blade 12 has a shape in which a peak outlet angle ⁇ at the trailing edge 15 thereof exists in the outer region 12B of the blade 12 that is located radially outer than the representative square mean radius position Rr, and an another peak outlet angle ⁇ at the trailing edge 15 thereof exists in an inner region 12A of the blade 12 that is located radially inner than the representative square mean radius position Rr.
  • the representative square mean radius position Rr serves as a reference at which the flow area of the propeller fan 4 is bisected into the radially inner region and the radially outer region, and each of the outer region 12B occupying one half of the flow area and the inner region 12A occupying the remaining half of the flow area is provided with the function of guiding air in the circumferential direction, thereby making it possible to effectively achieve the noise reduction.
  • the shape of the blade in which a peak outlet angle ⁇ at the trailing edge 15 exists in the outer region 12B is adopted, to thereby obtain a large amount of work of the fan at the trailing edge 15 of the outer region 12B.
  • This can enhance the effect of guiding air flowing along the pressure surface 21 of the outer region 12B in the circumferential direction.
  • the shape of the blade in which an another peak outlet angle ⁇ at the trailing edge 15 exists in the inner region 12A is adopted, to thereby obtain a large amount of work of the fan also at the trailing edge 15 of in the inner region 12A. This can also enhance the effect of guiding air flowing along the pressure surface 21 of the inner region 12A in the circumferential direction.
  • the inner region 12A includes the pressure surface 21 having a maximum radius of curvature greater than a maximum radius of curvature of the pressure surface 21 of the outer region 12B.
  • the inner region 12A has a smaller maximum value of curvature radius and is therefore flatter than the outer region 12B. Therefore, the blade 12 is allowed to have a small cross-sectional area especially in the inner region 12A. This allows the blade 12 to be light in weight and small in volume.
  • the pressure surface 21 of the inner region 12A and the pressure surface 21 of the outer region 12B include a concave curve surface.
  • the pressure surface 21 of the inner region 12A and the pressure surface 21 of the outer region 12B each include a concave curve surface, it is possible to enhance, in each of the regions, the effect of guiding air flowing along the pressure surface 21 in the circumferential direction.
  • the pressure surface 21 of the outer region 12B has a maximum radius of curvature smaller than a maximum radius of curvature of the pressure surface 21 of the inner region 12A, and the respective pressure surfaces of the regions 12A and 12B each have a concave curve surface. Because changes in the pressure over the pressure surface 21 and the negative pressure surface 22 is great in the outer region 12B close to the outer peripheral portion 16, the radius of curvature in the outer region 12B is set to a small value, to thereby make it possible to enhance the effect of guiding air flowing along the pressure surface 21 of the outer region 12B in the circumferential direction. Consequently, the entire pressure surface 21 is further unlikely to cause the leakage flow.
  • the inner region 12A and the outer region 12 B each have single concave curve surface and single peak outlet angle.
  • Such relatively simple structure allows the blade 12 to be light in weight and small in volume while achieving the noise reduction.
  • the trailing edge 15 of the blade 12 includes the recessed portion 19 in the region bearing the representative square mean radius position Rr, the recessed portion being oriented toward the leading edge 14.
  • the recessed portion 19 is provided in the region of the trailing edge 15 bearing the representative square mean radius position Rr where the pressure rise is otherwise liable to be greatest. Therefore, the pressure rise can be reduced in the vicinity of the recessed portion 19. This allows the air flowing from the leading edge 14 toward the trailing edge 15 to move toward the hub 11 and to the outer peripheral portion 16 in such a manner as to avoid the representative square mean radius position Rr in the vicinity of the trailing edge 15. This can enhance the effect of guiding airflow in the circumferential direction.
  • the position P1 where the leading edge 14 and the outer peripheral portion 16 join each other is located further forward in the rotational direction D than the position P2 where the leading edge 14 and the inner peripheral portion 13 join each other.
  • the position P3 where the trailing edge 15 and the outer peripheral portion 16 join each other is located further rearward in the rotational direction D than the position P4 where the trailing edge 15 and the inner peripheral portion 13 join each other.
  • the position P13 where the trailing edge 115 and the outer peripheral portion 116 join each other is located further forward in the rotational direction D than the position P14 where the trailing edge 115 and the inner peripheral portion 113 join each other.
  • the blade 12 is made to be compact especially in the inner region 12A and is thereby light in weight, compared to the reference example shown in FIG. 4B .
  • the above-described embodiment illustrates the case where the propeller fan is used in the outdoor unit 1 of the air conditioner.
  • the propeller fan may be used, for example, as a fan for an indoor unit of an air conditioner or as a ventilation fan.
  • the first embodiment illustrates the case where the pressure surface 21A of the inner region 12A and the pressure surface 21B of the outer region 12B each have a concave curve surface.
  • a propeller fan of the present invention includes a blade, and the blade has a shape in which a peak outlet angle at a trailing edge thereof exists in an outer region of the blade that is located radially outer than the representative square mean radius position, and an another peak outlet angle at a trailing edge thereof exists in an inner region of the blade that is located radially inner than the representative square mean radius position.
  • the representative square mean radius position serves as a reference at which a flow area of the propeller fan is bisected into the radially inner region and the radially outer region, and each of the outer region occupying one half of the flow area and the inner region occupying the remaining half of the flow area is provided with a function of guiding air in a circumferential direction, thereby making it possible to effectively achieve noise reduction, specifically as follows.
  • air flowing along the pressure surface is liable to flow to the outer peripheral portion (wing tip) due to a pressure gradient, a centrifugal force and the like during rotation of the propeller fan.
  • the shape of the blade in which a peak outlet angle ⁇ at the trailing edge exists in the outer region is adopted, to thereby obtain a large amount of work of the fan at the trailing edge of the outer region.
  • This can enhance the effect of guiding air flowing along the pressure surface of the outer region in the circumferential direction.
  • the shape of the blade in which an another peak outlet angle ⁇ at the trailing edge exists in the inner region is adopted, to thereby obtain a large amount of work of the fan also at the trailing edge of the inner region. This can also enhance the effect of guiding air flowing along the pressure surface of the inner region in the circumferential direction.
  • the blade will also need to have a small blade height in the inner peripheral portion thereof that joins the outer circumferential surface of the hub (at a joint where the blade joins the hub).
  • the blade height refers to the difference in height (difference in height along the rotation axis) between one end (the leading edge end) and the other end (the trailing edge end) of a camber line on the joint. If the blade has a small height, the amount of work (head rise) of the blade is small in the vicinity of the joint, so that the air flowing onto the pressure surface from the leading edge is liable to move radially outward to the wing tip where the amount of work is large (the wing tip where the head rise is great).
  • the hub is made to have a small height in the conventional propeller fan, it will be difficult to allow air to flow dominantly in the circumferential direction.
  • head rise work of the blade in the vicinity of the joint
  • this will increase the weight of the blade, which makes it difficult to provide a propeller fan that is light in weight.
  • the blade having the shape in which a peak outlet angle at the trailing edge exists in the outer region and an another peak outlet angle at the trailing edge exists in the inner region is adopted, which allows air to flow dominantly in the circumferential direction, as described above. Therefore, the propeller fan of the present invention is allowed to include the hub having a smaller height than the conventional fan and is thereby light in weight, while allowing air to flow dominantly in the circumferential direction.
  • the peak outlet angle in the outer region and the peak outlet angle in the inner region may have the same or different values.
  • the peak outlet angle in the outer region may have a greater or smaller value than the peak outlet angle in the inner region.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (4)

  1. Ventilateur hélicoïdal (4) comprenant un moyeu (11) et une pluralité de pales (12), dans lequel chacune des pales (12) présente une forme dans laquelle un angle de sortie de crête sur un bord de fuite (15) de celle-ci existe dans une région extérieure (12B) de la pale (12) qui est située radialement vers l'extérieur d'une position de rayon médian carré représentatif (Rr), et un autre angle de sortie de crête sur un bord de fuite (15) de celle-ci existe dans une région intérieure (12A) de la pale (12) qui est située radialement vers l'intérieur de la position de rayon médian carré représentatif (Rr),
    dans lequel la position de rayon médian carré représentatif est déterminée par l'utilisation de la formule Rr = R 2 + r 2 / 2 0,5 ,
    Figure imgb0004
     dans lequel
    R = un rayon représentatif de la périphérie extérieure de la pale (12) et
    r = un rayon représentatif de la périphérie extérieure du moyeu, et
    l'angle de sortie est défini dans une vue résultant d'une section de la pale par une surface de rayon constant comme un angle entre une ligne tangente L3 touchant à une surface de pression (21) sur le bord de fuite (15) et la direction circonférentielle,
    le ventilateur hélicoïdal étant caractérisé en ce que la surface de pression de la région intérieure (12A) et la surface de pression de la région extérieure (12B) présentent chacune une seule surface de courbe concave, lorsqu'il est vu dans un plan qui inclut l'axe de rotation A0 et croise la pale (12), et un seul angle de sortie de crête.
  2. Ventilateur hélicoïdal (4) selon la revendication 1, dans lequel
    la région intérieure (12A) inclut la surface de pression (21) présentant un rayon de courbure maximum supérieur à un rayon de courbure maximum d'une surface de pression (21) de la région extérieure (12B), dans lequel le rayon de courbure est vu dans un plan qui inclut l'axe de rotation A0 et croise la pale (12).
  3. Ventilateur hélicoïdal (4) selon la revendication 1 ou 2, dans lequel
    le bord de fuite (15) de la pale (12) présente une portion évidée (19) évidée vers un bord d'attaque (14) de la pale (12) dans une région incluant la position de rayon médian carré représentatif (Rr).
  4. Climatiseur comprenant un ventilateur hélicoïdal (4) selon l'une quelconque des revendications 1 à 3.
EP13841827.2A 2012-09-28 2013-09-27 Ventilateur hélicoïdal et climatiseur équipé de celui-ci Active EP2902639B1 (fr)

Applications Claiming Priority (2)

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JP2012217270 2012-09-28
PCT/JP2013/005794 WO2014050146A1 (fr) 2012-09-28 2013-09-27 Ventilateur hélicoïdal et climatiseur équipé de celui-ci

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EP2902639A1 EP2902639A1 (fr) 2015-08-05
EP2902639A4 EP2902639A4 (fr) 2016-05-25
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AU (1) AU2013321833B2 (fr)
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KR102479815B1 (ko) * 2015-11-30 2022-12-23 삼성전자주식회사 송풍팬 및 이를 구비하는 공기 조화기
WO2018020708A1 (fr) * 2016-07-27 2018-02-01 シャープ株式会社 Ventilateur hélicoïdal et dispositif d'alimentation en fluide
AU2017206193B2 (en) * 2016-09-02 2023-07-27 Fujitsu General Limited Axial fan and outdoor unit
CN107355425B (zh) * 2017-07-26 2023-04-25 奥克斯空调股份有限公司 高噪声消除度轴流风叶
JP6739656B2 (ja) * 2017-08-14 2020-08-12 三菱電機株式会社 羽根車、送風機、及び空気調和装置
CN108087333A (zh) * 2017-12-08 2018-05-29 广东美的制冷设备有限公司 轴流风轮及空调器
CN108087302A (zh) * 2017-12-08 2018-05-29 广东美的制冷设备有限公司 轴流风轮及空调器
CN207795681U (zh) * 2018-01-13 2018-08-31 广东美的环境电器制造有限公司 轴流扇叶、轴流风机扇叶组件、轴流风机风道组件
US11408435B2 (en) * 2018-06-22 2022-08-09 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Rotor and centrifugal compressor including the same
EP3882470A4 (fr) * 2018-11-22 2022-02-23 GD Midea Air-Conditioning Equipment Co., Ltd. Draisienne à flux axial et climatiseur la comprenant
JP2020112034A (ja) * 2019-01-08 2020-07-27 パナソニックＩｐマネジメント株式会社 軸流ファン
CN113825915B (zh) * 2019-05-21 2023-08-29 三菱电机株式会社 轴流风扇、送风装置及制冷循环装置
JP7289235B2 (ja) * 2019-07-18 2023-06-09 株式会社コロナ エアコン装置の室外機用プロペラファン
EP4209682A4 (fr) * 2020-09-02 2023-10-18 Mitsubishi Electric Corporation Ventilateur à écoulement axial et unité intérieure pour climatiseur
JPWO2022091225A1 (fr) * 2020-10-27 2022-05-05
KR102401163B1 (ko) 2020-12-03 2022-05-24 엘지전자 주식회사 공기 조화기의 실외기에 구비되는 축류팬
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BR112015006704B1 (pt) 2022-05-10
US20150240645A1 (en) 2015-08-27
EP2902639A4 (fr) 2016-05-25
AU2013321833B2 (en) 2015-11-26
WO2014050146A1 (fr) 2014-04-03
BR112015006704A2 (pt) 2017-07-04
EP2902639A1 (fr) 2015-08-05
CN104641121B (zh) 2016-08-31
AU2013321833A1 (en) 2015-04-02
JP5549772B2 (ja) 2014-07-16
CN104641121A (zh) 2015-05-20

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