WO2014080899A1 - 空気調和機 - Google Patents
空気調和機 Download PDFInfo
- Publication number
- WO2014080899A1 WO2014080899A1 PCT/JP2013/081150 JP2013081150W WO2014080899A1 WO 2014080899 A1 WO2014080899 A1 WO 2014080899A1 JP 2013081150 W JP2013081150 W JP 2013081150W WO 2014080899 A1 WO2014080899 A1 WO 2014080899A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- blade
- rib
- impeller
- region
- once
- Prior art date
Links
Images
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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
- F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
- F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
-
- 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
- F04D29/66—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
- F04D29/663—Sound attenuation
- F04D29/665—Sound attenuation by means of resonance chambers or interference
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0025—Cross-flow or tangential fans
-
- 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
- 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
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
Definitions
- the present invention relates to an air conditioner equipped with a once-through fan used as a blowing means.
- Patent Document 1 discloses a blade having at least two support plates arranged at intervals in the rotation axis direction and a plurality of blades arranged at intervals in the circumferential direction of the support plate between the two support plates.
- a once-through fan with a car is disclosed.
- the outer diameters of the plurality of blades in the blade cross section orthogonal to the rotation axis in the impeller are substantially the same.
- the blade ring central portion is the second region, the first region and the first region.
- the blade exit angle at the blade outer peripheral side end of each region has a configuration in which the second region ⁇ first region ⁇ third region increases in this order.
- Patent Document 2 discloses a cross-flow fan provided with a plurality of ribs extending from the leading edge of the blade along the suction surface of the blade.
- Patent Document 3 discloses a cross current in which each blade is formed in a convex shape with a thin metal plate, and a plurality of rectangular cut and raised pieces that rise in the convex direction are provided on the convex surface. A fan is disclosed. These cut and raised pieces are arranged in parallel at a required pitch in the direction of the blade axis.
- JP 2006-329100 A page 3, [0017], FIG. 1
- JP 10-77789 A page 4, [0037], FIG. 6
- the present invention has been made in view of the above, and an object thereof is to provide a cross-flow fan and an air conditioner capable of reducing noise and improving air blowing efficiency.
- the cross-flow fan of the present invention is a cross-flow fan including an impeller and a shaft that rotatably supports the impeller, the impeller corresponding to a plurality of support plates.
- a plurality of blades arranged at intervals in a circumferential direction between the pair of support plates, and the blade has a plurality of regions having different blade cross sections perpendicular to the impeller rotation axis,
- the plurality of regions are arranged in the wing in the direction of the impeller rotation axis, and the wing further includes a connecting portion that connects the plurality of regions, and the wing includes at least one rib.
- the air conditioner of the present invention is disposed between a stabilizer that divides the suction side air passage and the blowout side air passage in the main body, and the suction side air passage and the blowout side air passage.
- FIG. 4 is a cross-sectional view taken along line AA in FIG.
- FIG. 4 is a cross-sectional view taken along line CC of FIG. FIG.
- FIG. 4 is a cross-sectional view taken along line CC of FIG.
- FIG. 4 is a cross-sectional view taken along line CC of FIG.
- FIG. 5 is a cross-sectional view of the cross-flow fan blades taken along line BB in FIG. 3.
- arrow Va of FIG. 6, Comprising: It is a schematic diagram in case the rib is provided on the blade ring vicinity part of the connection part vicinity. It is the figure seen from arrow Va of FIG. 6, Comprising: It is a schematic diagram in case the rib is provided on the connection part. It is the figure seen from arrow Va of FIG. 6, Comprising: It is a schematic diagram in case the rib is provided on the inter-blade part near a connection part.
- FIG. 6 is a perspective view corresponding to FIG. 4 when the rib is provided on the vicinity of the blade ring in the vicinity of one connecting portion in the impeller rotational axis direction.
- FIG. 6 is a perspective view corresponding to FIG. 5 when the rib is provided on the vicinity of the blade ring in the vicinity of the one connecting portion in the impeller rotating shaft direction.
- FIG. 5 is a perspective view corresponding to FIG.
- FIG. 1 is an installation schematic diagram when viewed from a room of an air conditioner equipped with a cross-flow fan according to Embodiment 1 of the present invention
- FIG. 2 is a longitudinal sectional view of the air conditioner of FIG. 1
- FIG. 1 is a front partial sectional view of an impeller of a once-through fan mounted on the air conditioner of FIG. 1
- FIG. 4 is a perspective schematic view of a state in which one blade of the impeller of the once-through fan of FIG.
- FIG. 5 is a schematic perspective view of a state where one blade of the impeller of the cross-flow fan of FIG. 3 is provided. It is the perspective view seen from the blade negative pressure surface 13b side when it is located in the suction side wind path (impeller suction area) E1.
- the air conditioner (indoor unit) 100 includes a main body 1 and a front panel 1 b provided on the front surface of the main body 1, so that an outline of the air conditioner 100 is configured.
- the air conditioner 100 is installed in the wall 11a of the room 11 which is an air-conditioning target space. That is, FIG. 1 illustrates an example in which the air conditioner 100 is a wall-hanging type, but the present invention is not limited to such an embodiment, and may be, for example, a ceiling-embedded type.
- the air conditioner 100 is not limited to being installed in the room 11, and may be installed in a room of a building or a warehouse, for example.
- a suction grill 2 for sucking room air into the air conditioner 100 is formed in the upper part 1 a constituting the upper part of the main body 1.
- An air outlet 3 for supplying the air to the room is formed, and a guide wall 10 for guiding air discharged from a cross-flow fan 8 described later to the air outlet 3 is formed.
- the main body 1 generates conditioned air by transmitting to the air a filter (ventilation resistor) 5 that removes dust and the like in the air sucked from the suction grill 2 and the heat or cold of the refrigerant.
- a filter (ventilation resistor) 5 that removes dust and the like in the air sucked from the suction grill 2 and the heat or cold of the refrigerant.
- the stabilizer 9 that partitions the suction side air passage E1 and the blowout side air passage E2, and the suction side air passage E1 and the blowout side air passage E2
- a cross-flow fan 8 that sucks in air and blows out air from the air outlet 3
- a vertical wind vane 4 a and a left-right wind vane 4 b that adjust the direction of the air blown from the cross-flow fan 8 are provided.
- the suction grill 2 is an opening for forcibly taking room air into the air conditioner 100 by the cross-flow fan 8.
- the suction grill 2 has an opening formed on the upper surface of the main body 1.
- the blower outlet 3 is an opening through which the air passes when the air sucked from the suction grill 2 and passed through the heat exchanger 7 is supplied into the room.
- the blower outlet 3 is formed as an opening in the front panel 1b.
- the guide wall 10 constitutes the blowing side air passage E2 in cooperation with the lower surface side of the stabilizer 9.
- the guide wall 10 forms a spiral surface from the cross-flow fan 8 to the outlet 3.
- the filter 5 is formed in a mesh shape, for example, and removes dust in the air sucked from the suction grill 2.
- the filter 5 is provided on the downstream side of the suction grille 2 and on the upstream side of the heat exchanger 7 in the air path from the suction grille 2 to the air outlet 3 (center portion inside the main body 1).
- the heat exchanger 7 (indoor heat exchanger) functions as an evaporator during cooling operation to cool air, and functions as a condenser (heat radiator) during heating operation to heat the air. is there.
- the heat exchanger 7 is provided on the downstream side of the filter 5 and on the upstream side of the cross-flow fan 8 in the air path from the suction grill 2 to the blower outlet 3 (center portion inside the main body 1).
- the shape of the heat exchanger 7 is a shape that surrounds the front surface and the upper surface of the cross-flow fan 8, but is merely an example and is not particularly limited.
- the heat exchanger 7 is connected to an outdoor unit that may be a well-known embodiment having a compressor, an outdoor heat exchanger, a throttling device, and the like and constitutes a refrigeration cycle. Further, as the heat exchanger 7, for example, a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a large number of fins is used.
- the stabilizer 9 divides the suction side air passage E1 and the blowout side air passage E2, and is provided on the lower side of the heat exchanger 7 as shown in FIG. Located on the upper surface side of the stabilizer 9, the blowing side air passage E ⁇ b> 2 is located on the lower surface side of the stabilizer 9.
- the stabilizer 9 has a drain pan 6 that temporarily stores the condensed water adhering to the heat exchanger 7.
- the cross-flow fan 8 is for sucking room air from the suction grill 2 and blowing air-conditioned air from the outlet 3.
- the cross-flow fan 8 is provided on the downstream side of the heat exchanger 7 and on the upstream side of the air outlet 3 in the air path from the suction grill 2 to the air outlet 3 (the central portion inside the main body 1).
- the cross-flow fan 8 includes an impeller 8a made of a thermoplastic resin such as AS resin (Styrene-AcryloNitrile copolymer) containing glass fiber, and a motor 12 for rotating the impeller 8a.
- the motor shaft 12a for transmitting the rotation of the motor 12 to the impeller 8a, and the impeller 8a itself rotates to suck indoor air from the suction grill 2 and send conditioned air to the blowout port 3.
- symbol V1 in FIG. 3 shows the conventional wind speed distribution
- symbol V2 shows the wind speed distribution of this Embodiment.
- the impeller 8a is configured by connecting a plurality of impeller units 8d, and each impeller unit 8d has a plurality of blades 8c and at least one ring fixed to the end side of the plurality of blades 8c. (Support plate) 8b. That is, in the impeller single unit 8d, each of the plurality of blades 8c extends from the outer peripheral side surface of the disk-shaped ring 8b so as to be substantially orthogonal to the side surface, and the plurality of blades 8c are formed on the ring 8b.
- the impellers 8a are aligned at a predetermined interval in the circumferential direction, and a plurality of such impellers 8d are welded and connected to be integrated.
- the impeller includes an aspect including only one impeller.
- the impeller 8a has a fan boss 8e protruding toward the inside (center) side of the impeller 8a.
- the fan boss 8e is fixed to the motor shaft 12a with a screw or the like.
- one side of the impeller 8a is supported by the motor shaft 12a via the fan boss 8e, and the other side of the impeller 8a is supported by the fan shaft 8f.
- the impeller 8a rotates in the rotation direction RO around the impeller rotation center O of the impeller 8a in a state where both ends are supported, sucks room air from the suction grille 2, and conditioned air into the outlet 3 Can be sent in.
- the impeller 8a will be described in detail later.
- the up-and-down airflow direction vane 4a adjusts the vertical direction of the air blown from the cross-flow fan 8, and the left-right wind direction vane 4b adjusts the left-right direction of the air blown from the cross-flow fan 8. is there.
- the up / down wind direction vane 4a is provided on the downstream side of the left / right wind direction vane 4b. Note that the vertical direction in the description corresponds to the vertical direction in FIG. 2, and the horizontal direction in the description corresponds to the front and back direction of the paper surface in FIG.
- FIG. 6 is a cross-sectional view taken along line AA in FIG. 7, 8, and 9 show the vicinity of the blade ring that has a predetermined length WL ⁇ b> 1 from the surface of each ring 8 b to the inside of the impeller unit 8 d with respect to the distance WL between the two support plates (rings) 8 b in FIG. 3.
- FIG. 10 is a diagram in which the cross section taken along line AA and the cross section taken along line CC are superimposed on the cross section taken along line BB in FIG.
- a section taken along the line AA (hereinafter also referred to as an AA section) is perpendicular to the rotation axis of the blade ring vicinity 8ca having a predetermined length WL1 from the surface of each ring 8b in FIG.
- a cross section taken along the line BB (hereinafter also referred to as a BB cross section) is a cross section perpendicular to the rotation axis of the blade ring center portion 8cb having a predetermined length WL2 at the longitudinal center between the two rings 8b.
- a section taken along the line CC (hereinafter also referred to as a CC section) is perpendicular to the rotation axis of the inter-blade portion 8cc at a predetermined length WL3 between the blade ring vicinity portion 8ca and the blade ring central portion 8cb. It is a cross section.
- the outer peripheral end (outer end) 15a and the inner peripheral end (inner end) 15b of the blade 8c are each formed in an arc shape.
- the blade 8c is formed so that the outer peripheral end 15a side is inclined forward in the impeller rotation direction RO with respect to the inner peripheral end 15b side. That is, when the blade 8c is viewed in a longitudinal section, the blade pressure surface 13a and the blade negative pressure surface 13b of the blade 8c are moved from the impeller rotation center O of the impeller 8a toward the outside of the blade 8c, and the impeller rotation direction RO Is curved.
- the center of the circle corresponding to the arc shape formed on the outer peripheral end 15a is P1 (also referred to as arc center P1), and the center of the circle corresponding to the arc shape formed on the inner peripheral end 15b is P2 (arc Also referred to as center P2.
- P1 also referred to as arc center P1
- P2 arc Also referred to as center P2.
- a line segment connecting the arc centers P1 and P2 is a chord line (chord) L, as shown in FIG. 8, the length of the chord line L is Lo (in FIG. 8, the chord length of the third region). (Hereinafter also referred to as chord length Lo).
- the blade 8c has a blade pressure surface 13a that is a surface on the rotational direction RO side of the impeller 8a and a blade negative pressure surface 13b that is a surface on the opposite side of the rotational direction RO of the impeller 8a.
- the vicinity of the center of the line L has a concave shape curved in a direction from the blade pressure surface 13a toward the blade suction surface 13b.
- the radius of the circle corresponding to the arc shape on the blade pressure surface 13a side is different between the outer peripheral side of the impeller 8a and the inner peripheral side of the impeller 8a. That is, as shown in FIG. 7, the surface on the blade pressure surface 13a side of the blade 8c has an outer peripheral curved surface Bp1 whose radius (arc radius) corresponding to the arc shape on the outer peripheral side of the impeller 8a is Rp1, and the impeller A radius (arc radius) corresponding to the arc shape on the inner peripheral side of 8a has an inner peripheral curved surface Bp2 whose radius is Rp2, and is a multiple arc curved surface. Further, the blade pressure surface 13a side surface of the blade 8c has a flat surface Qp that is connected to the inner peripheral end of the inner peripheral curved surface Bp2 and has a planar shape.
- the surface on the blade pressure surface 13a side of the blade 8c is configured by continuously connecting the outer peripheral curved surface Bp1, the inner peripheral curved surface Bp2, and the plane Qp. Note that when the blade 8c is viewed in a longitudinal section, the straight line forming the plane Qp is a tangent line at a point where the straight line is connected to the arc forming the inner peripheral curved surface Bp2.
- the surface on the blade suction surface 13b side of the blade 8c is a surface corresponding to the surface on the blade pressure surface 13a side.
- the surface of the blade 8c on the blade suction surface 13b side includes an outer peripheral curved surface Bs1 whose radius (arc radius) corresponding to the arc shape on the outer peripheral side of the impeller 8a is Rs1, and the inner periphery of the impeller 8a.
- an inner circumferential curved surface Bs2 whose radius (arc radius) corresponds to the arc shape on the side is Rs2.
- the surface of the blade 8c on the blade suction surface 13b side has a flat surface Qs that is connected to the inner peripheral end of the end portions of the inner peripheral curved surface Bs2 and has a planar shape.
- the surface on the blade suction surface 13b side of the blade 8c is configured by continuously connecting the outer circumferential surface curved surface Bs1, the inner circumferential surface curved surface Bs2, and the plane Qs. Note that when the blade 8c is viewed in a longitudinal section, the straight line that forms the plane Qs is a tangent line at the point that it is connected to the arc that forms the inner peripheral curved surface Bs2.
- the blade thickness When the diameter of a circle inscribed in the blade surface when the blade 8c is viewed in a longitudinal section is a blade thickness (thickness) t, as shown in FIG. 7, the blade thickness (thickness) t1 of the outer peripheral end 15a is shown in FIG. Is thinner than the blade thickness (wall thickness) t2 of the inner peripheral end 15b.
- the blade thickness t1 corresponds to the radius R1 ⁇ 2 of the circle that forms the arc of the outer peripheral side end portion 15a
- the blade thickness t2 corresponds to the radius R2 ⁇ 2 of the circle that forms the arc of the inner peripheral side end portion 15b.
- the blade thickness is smaller at the outer peripheral end 15a than at the inner peripheral end 15b. It is formed so as to gradually increase from the portion 15a toward the center, become maximum at a predetermined position near the center, gradually become thinner toward the inside, and have the same thickness at the straight portion Q.
- the blade thickness t of the blade 8c is determined by the outer peripheral curved surface Bp1 and the inner peripheral curved surface formed by the blade pressure surface 13a and the blade negative pressure surface 13b, excluding the outer peripheral end 15a and the inner peripheral end 15b.
- the outer peripheral curved surface Bs1, and the inner peripheral curved surface Bs2 it gradually increases from the outer peripheral end 15a toward the center of the blade 8c, and reaches the maximum thickness t3 at a predetermined position near the center of the chord line L. Then, the thickness gradually decreases toward the inner peripheral end 15b.
- the blade thickness t is an inner peripheral side end thickness t2 that is a substantially constant value in the range of the straight portion Q, that is, the range between the plane Qp and the plane Qs.
- a portion of the blade 8c having the planes Qp and Qs of the inner peripheral end 15b as the surface is referred to as a straight portion Q. That is, the blade negative pressure surface 13b of the blade 8c is formed by multiple arcs and straight portions Q from the outer peripheral side to the inner peripheral side of the impeller.
- the radius R1 of -P1 is the same effective radial dimension in the direction of the impeller rotational axis in the blade ring vicinity portion 8ca, the blade ring central portion 8cb, and the inter-blade portion 8cc, and the impeller effective outer diameter that is the diameter of the circumscribed circle of all the blades The radius is the same in the longitudinal direction.
- a wall thickness center line between the rotation direction RO side surface (pressure surface) 13a and the reverse rotation side surface (negative pressure surface) 13b of the blade 8c is defined as a sled line Sb, and the blade line 8b from the position of a predetermined radius R03 from the impeller rotation center O.
- the outer peripheral side portion is defined as an outer peripheral side sled line S1a, and the portion of the sled line Sb that is located on the inner peripheral side from the position of the predetermined radius R03 from the impeller rotation center O is defined as an inner peripheral side sled line S2a.
- the position of the predetermined radius R03 (not shown) is a position where the exit angle of the blade changes.
- the blade exit angle ⁇ b is assumed, the first region (the blade ring vicinity 8ca), the second region (the blade ring center 8cb), and the third region (the blade ring vicinity 8ca and the blade ring center 8cb) In part 8cc), the blade exit angle is different.
- the outer peripheral side of the blade ring central portion 8cb is most advanced in the impeller rotation direction RO than the other regions, and the outer peripheral side of the inter-blade portion 8cc is conversely most retracted, and the connecting portion 8ce is a blade cross section in the adjacent region. It is formed with an inclined surface whose shape gradually changes.
- the wing 8c includes a ring 8b on one side, a wing ring vicinity portion 8ca, a connecting portion 8ce, an interwing portion 8cc, a connecting portion 8ce, a wing ring central portion 8cb, a connecting portion 8ce, an interwing portion 8cc, a connecting portion 8ce,
- the blade ring vicinity portion 8ca and the other ring 8b are formed in the order of five regions and four connection portions 8ce.
- the blade ring vicinity portion 8ca, the blade ring center portion 8cb, the inter-blade portion 8cc, and the connection portion 8ce are respectively predetermined. Between the widths of the lengths WL1, WL2, WL3, and WL4, they are formed in the same shape in the longitudinal direction.
- the blade exit angles of the respective regions are defined as the first region (blade ring vicinity 8ca) blade exit angle ⁇ b1, the second region (blade ring central portion 8cb) blade exit angle ⁇ b2, the third region (near the blade ring).
- the blade portion 8 cc between the blade portion 8 ca and the blade ring central portion 8 cb) is formed such that ⁇ b 2 ⁇ b 1 ⁇ b 3 when the blade outlet angle ⁇ b 3 is assumed. Therefore, as shown in FIGS. 4 and 5, the blade outer peripheral end 15 a is the blade cross-sectional shape which is the most backward in the rotation direction in the third region and is retreated, and the blade cross-sectional shape which is most advanced in the rotation direction in the second region.
- the blade cross section orthogonal to the impeller rotation axis has a plurality of regions that are different in regions adjacent to each other in the impeller rotation axis direction of the blade.
- 10 indicates the blade advance angle. Specifically, ⁇ 1 indicates the blade advance angle in the first region, ⁇ 2 indicates the blade advance angle in the second region, and ⁇ 3 indicates the blade advance angle in the third region. Indicates a corner.
- symbol P13 in FIG. 10 shows the circular arc center of the blade
- the connection between the blade ring vicinity portion 8ca, which is the portion near the ring 8b in the impeller rotational axis direction of the blade pressure surface 13a and the blade negative pressure surface 13b, and the adjacent blade portion 8cc is connected.
- Ribs 14 and 16 are formed on the blade ring vicinity portion 8ca in the vicinity of the portion 8ce so as to stand at a predetermined height toward the adjacent seven blades so as to be substantially orthogonal to the impeller rotation axis.
- the ribs 14 and 16 are formed in the connecting portion 8ce or, in each of a pair of regions on both sides of the connecting portion 8ce adjacent to the connecting portion 8ce, rotation of the adjacent region from the connecting portion 8ce.
- the ribs 14 and 16 are arranged so that the thickness center line CL of the ribs 14 and 16 enters a rib installation region that is a range indicated by the length WLa in the rotation axis direction. ,It is formed.
- the length WLa of the rib installation region is 0.2 ⁇ WL1 which is 20% of the length WL4 of the connecting portion 8ce itself and the length WL1 of the blade ring vicinity portion 8ca adjacent to the connecting portion 8ce, and the connecting portion 8ce and 0.2 ⁇ WL3 which is 20% of the length WL3 of the adjacent blade portion 8cc.
- the range indicated by 0.2 ⁇ WL1 here is not a mere length at an arbitrary position on the blade ring vicinity portion 8ca, but one end of the range indicated by 0.2 ⁇ WL1 is the blade ring vicinity portion 8ca. And the other end of the range indicated by 0.2 ⁇ WL1 is 0.2 ⁇ WL1 away from the boundary between the blade ring vicinity portion 8ca and the connection portion 8ce on the blade ring vicinity portion 8ca. In the position. Similarly, one end of the range indicated by 0.2 ⁇ WL3 is at the boundary between the blade portion 8cc and the connecting portion 8ce, and the other end of the range indicated by 0.2 ⁇ WL3 is between the blades on the blade portion 8cc.
- FIG. 11 shows a range where both the front and back ribs are indicated by 0.2 ⁇ WL1.
- 12 is an example when both the front and back ribs are in the range indicated by WL4, and
- FIG. 13 is a range where both the front and back ribs are indicated by 0.2 ⁇ WL3.
- FIG. 14 shows an example in which one of the front and back ribs is in a range indicated by 0.2 ⁇ WL1, and the other of the front and back ribs is in a range indicated by 0.2 ⁇ WL3.
- the rib 14 is a region between the outer diameter Rt1 of the blade outer peripheral end 15a and the inner diameter Rt2 of the blade inner peripheral end 15b (the outer side of the virtual circle of the inner diameter Rt2 of the blade).
- the outer peripheral end 14a of the rib 14 on the blade suction surface 13b side is the same as the outer diameter Rt1 of the outer peripheral end 15a.
- the rib inner peripheral end 14b of the rib 14 is formed in a shape inclined toward the inner side of the chord (the side closer to the chord) than the straight line perpendicular to the chord L at the inner peripheral end 15b. ing.
- the tips of the rib outer peripheral side end portion 14a and the rib inner peripheral side end portion 14b in the standing direction are both formed in an arc shape.
- the rib upper end portion 14c is formed by a curved surface obtained by moving the curved surface of the blade suction surface 13b by a predetermined distance in a direction orthogonal to the chord L.
- the leading end of the rib upper end portion 14c in the standing direction has an arc shape.
- the thick chord which is not less than the thickness t1 of the blade outer peripheral end portion 15a which is the minimum thickness of the blade and which is the maximum thickness of the blade.
- the thickness gradually decreases from the blade suction surface 13b to form a tapered shape. That is, the side surfaces 14e on both sides of the rib 14 are inclined so that the interval is narrowed from the root 14d toward the tip in the standing direction.
- the rib 16 on the blade pressure surface 13a side is formed in a region between the outer diameter Rt1 of the blade outer peripheral end portion 15a and the inner diameter Rt2 of the blade inner peripheral end portion 15b.
- the rib 16 on the pressure surface 13a side has a rib outer peripheral end portion 16a formed in the same plane as the outer diameter Rt1 of the blade outer peripheral end portion 15a, and the rib inner peripheral end portion 16b has a blade shape rather than a straight line perpendicular to the chord L. It is formed in a shape inclined toward the inside of the string.
- the tips of the rib outer peripheral end portion 16a and the rib inner peripheral end portion 16b in the standing direction are both formed in an arc shape.
- the rib upper end portion 16c is formed by a curved surface obtained by moving the curved surface of the blade suction surface 13b in a direction orthogonal to the chord L by a predetermined distance.
- the tip of the rib upper end portion 16c in the standing direction has an arc shape.
- the blade chord center which is not less than the wall thickness t1 of the blade outer peripheral side end portion 15a which is the minimum wall thickness of the blade and which is the maximum blade thickness.
- the wall thickness gradually decreases from the blade pressure surface 13a to form a tapered shape. That is, the side surfaces 16e on both sides of the rib 16 are inclined so that the interval becomes narrower from the root 16d toward the tip in the standing direction.
- the ribs of adjacent blades do not collide as shown in FIGS. It is formed so that the height of the blade pressure surface side rib 16 ⁇ the height of the blade suction surface side rib 14 is less than half of the blade pitch.
- the impeller 8a includes a plurality of blades 8c having ribs standing on the blade surface of the present invention, and a ring 8b having a plurality of grooves 8ba into which the blades 8c are respectively inserted.
- the blade 8c is inserted into the groove 8ba on one surface of the ring 8b so that the blade pressure surface 13a and the blade suction surface 13b of the blade 8c are finally aligned. Let them fix.
- the impeller single body 8d is formed by performing this operation once or a plurality of times. Thereafter, the blade 8c fixed to the impeller single unit 8d is inserted into the groove 8ba on the other surface of the ring 8b, and is welded and fixed. By performing this operation a plurality of times, a plurality of impellers 8d are connected to form an impeller 8a.
- a portion of the blade 8c having the planes Qp and Qs of the inner peripheral end 15b as a surface is referred to as a straight portion Q.
- the blade suction surface 13b of the blade 8c is formed of multiple arcs and straight portions Q from the outer peripheral side to the inner peripheral side of the impeller.
- the blade thickness t does not increase rapidly toward the outer periphery of the impeller as compared with the curved surface, so that the frictional resistance can be suppressed.
- the blade pressure surface 13a of the blade 8c is also formed of multiple arcs and straight portions (planes) from the outer peripheral side to the inner peripheral side of the impeller.
- the downstream plane Qp is tangent to the inner circumferential curved surface Bs2.
- the blade 8c since the blade 8c has the downstream plane Qp, it has a shape bent by a predetermined angle with respect to the rotation direction RO. For this reason, compared with the case where there is no straight surface (plane Qp), even if the blade wall thickness t2 of the inner peripheral side end portion 15b is thick, the flow can be directed to the blade suction surface 13b. The wake vortex when flowing into the impeller from the side end 15b can be suppressed.
- the blade 8c has a thick inner end 15b and is difficult to separate in various inflow directions in the blowout air passage E2.
- the blade 8c has the maximum thickness near the center of the chord, which is the downstream side of the plane Qs. For this reason, if the flow is about to peel off after passing through the plane Qs, the blade thickness t gradually increases toward the vicinity of the center of the chord on the inner circumferential curved surface Bs2, so that the flow follows and the separation can be suppressed.
- the blade 8c has the inner peripheral curved surface Bs1 having a different arc radius on the downstream side of the inner peripheral curved surface Bs2, the separation of the flow is suppressed, and the effective blowing side air passage from the impeller is expanded. It is possible to reduce and equalize the blown wind speed, and to reduce the load torque applied to the blade surface. As a result, since flow separation on the blade surface can be suppressed on the impeller suction side and the blowout side, noise can be reduced, and power consumption of the fan motor can be reduced. That is, the air conditioner 100 equipped with the quiet and energy-saving once-through fan 8 can be obtained.
- the blade 8c may be formed so as to satisfy the following magnitude relationship with respect to the arc radii Rp1, Rp2, Rs1, and Rs2. That is, the blade 8c is preferably formed so that Rs1> Rp1> Rs2> Rp2. In this case, in the blowing side air passage E2, the blade 8c has the following effects.
- the blade suction surface 13b is a flat arc having a small radius of curvature, with the arc radius Rs1 of the outer peripheral curved surface Bs1 being larger than the arc radius Rs2 of the inner peripheral curved surface Bs2. For this reason, in the blowing-side air passage E2, the flow follows the vicinity of the outer peripheral side end portion 15a of the outer peripheral side curved surface Bs1, and the wake vortex can be reduced.
- the blade pressure surface 13a is a flat arc having a smaller radius of curvature than the arc radius Rp2 of the outer peripheral curved surface Bp1 and the arc radius Rp2 of the inner peripheral curved surface Bp2, the flow is on the blade pressure surface 13a side. Friction loss can be reduced because it flows smoothly without concentrating on.
- the blade 8c has the following effects.
- a chord line L that is in contact with the blade suction surface 13b is defined by setting a contact point between the parallel line Wp of the blade chord line L contacting the blade pressure surface 13a and the blade pressure surface 13a as a maximum warpage position Mp.
- a contact point between the parallel line Ws and the blade suction surface 13b is defined as a maximum warpage position Ms.
- the intersection with the perpendicular of the chord line L passing through the maximum warp position Mp is defined as the maximum warp chord point Pp
- the intersection with the perpendicular of the chord line L passing through the maximum warp position Ms is defined as the maximum warp chord point Ps.
- the distance between the arc center P2 and the maximum warp chord point Pp is the chord maximum warp length Lp
- the distance between the arc center P2 and the maximum warp chord point Ps is the chord maximum warp length Ls. .
- the line segment distance between the maximum warp position Mp and the maximum warp chord point Pp is the maximum warp height Hp
- the line segment distance between the maximum warp position Ms and the maximum warp chord point Ps is the maximum warp height Hs.
- the noise can be reduced by setting the chord maximum warp lengths Lp and Ls and the ratios Lp / Lo and Ls / Lo of the chord length Lo as follows.
- the blade 8c is formed so as to be the maximum warped position in the optimum range.
- the blade suction surface 13b is more warped than the blade pressure surface 13a if Ls / Lo> Lp / Lo.
- the position is on the outer peripheral side, and the interval between the adjacent blades 8c repeatedly increases and decreases from the inner peripheral side end 15b to the outer peripheral side end 15a, resulting in pressure fluctuation.
- the blade 8c is formed so as to have the maximum warp height in the optimum range.
- Hp and Hs are the maximum warp heights of the blade pressure surface 13a and the blade suction surface 13b, respectively, the relationship is Hs> Hp.
- Hs / Lo and Hp / Lo are less than 10%, the curved arc radius is large and the warpage is too small, the distance between adjacent blades 8c is too wide, and the flow cannot be controlled, and a separation vortex is generated on the blade surface. Abnormal fluid noise may occur, and there is a risk that the noise level will deteriorate rapidly.
- Hs / Lo and Hp / Lo are larger than 25%, the distance between adjacent blades is too narrow, and the wind speed increases, and there is a risk that noise will deteriorate rapidly.
- the air conditioner 100 equipped with the quiet and energy-saving once-through fan 8 can be obtained.
- a tangent at the center P4 of the thickness center line Sb is defined as Sb1.
- An angle formed between the tangent line Sb1 and the extension line Sf is defined as a bending angle ⁇ e.
- a distance between a perpendicular line of the chord line L passing through the arc center P2 and a perpendicular line of the chord line L passing through the center P4 is defined as a straight portion chord length Lf.
- the distance between the perpendicular of the chord line L passing through the center P3 and the perpendicular of the chord line L passing through the arc center P2 is the maximum thickness portion length Lt (in FIG. 9, the chord length Lt3 of the third region is shown). .
- chord length Lf of the straight portion Q of the inner peripheral end 15b of the blade 8c is too large with respect to the chord length Lo, the outer peripheral curved surfaces Bp1 and Bs1 on the outer peripheral side of the straight portion Q and the inner peripheral side as a result.
- the curved surfaces Bp2 and Bs2 have small arc radii and large warpage. For this reason, the flow tends to be separated, the loss increases, and the fan motor input increases.
- the distance between the blades 8c changes extremely from the inner peripheral side to the outer peripheral side and pressure fluctuation occurs, noise increases.
- the flow collides on the plane Qp on the pressure surface side and peels off on the plane Qs on the suction surface side. And the flow will stall.
- the bending angle ⁇ e is greater than 15 °, the flow is suddenly bent in the plane Qp that is the pressure side surface of the straight portion Q in the suction side air passage E1, and the flow is concentrated to increase the wind speed. End up. Further, the flow is separated at the plane Qs that is the surface of the straight portion Q on the suction surface side, and the wake vortex is greatly expanded and released, thereby increasing the loss.
- the blade is divided into a plurality of regions in the longitudinal direction between the pair of support plates, and the regions at both ends adjacent to the support plate in the state formed in the impeller are the first region and the blade ring central portion is the first region.
- the third region is disposed on both sides of the central portion of the blade ring between the two regions, the first region and the second region, each region has a different blade outlet angle and an appropriate blade outlet angle.
- flow separation can be suppressed and noise can be reduced. Therefore, an energy-saving and quiet air conditioner equipped with a cross-flow fan with higher efficiency and lower noise than that having the same blade shape in the longitudinal direction can be obtained.
- 16 and 17 show an example in which only one of the ribs is formed in the direction of the impeller rotational axis, but the effect of the flow in the vicinity of the support plate and the blade ring is not achieved even when only one of the ribs is formed. The effect is obtained at least as compared with the case without ribs.
- FIG. 18 shows another wing form.
- the chord length of the wing ring central portion 8cb at the central portion in the rotation axis direction is longer than that of the wing ring vicinity portion 8ca, and an inclined surface whose shape gradually changes is formed between these regions. Connected and formed at the connecting portion. Even in such a form, the same effect as in the case of the above basic form can be obtained, and the effect can be obtained by providing ribs at least between regions having different blade cross sections.
- the connecting portion 8ce is an inclined surface in which the adjacent blade cross-sectional shape gradually changes, there is no sudden change in the impeller rotational axis direction in the flow on the blade surface, that is, disturbance due to a step occurs. Absent. Further, since stress concentration can be avoided, there is no risk of blade damage, and strength can be improved.
- the load torque is reduced, so the power consumption of the motor can be reduced. Further, since the local high-speed flow does not hit the wind direction vanes disposed on the downstream side, the ventilation resistance is reduced and the load torque can be further reduced.
- the blade shape of the present invention is capable of preventing separation and uniforming the wind speed distribution on both the outer peripheral side and the inner peripheral side of the impeller, and is equipped with a high-efficiency, low-noise cross-flow fan and the like.
- the air conditioner 100 equipped with the energy-saving and quiet cross-flow fan 8 can be obtained.
- the rib is formed in a region between the outer diameter of the blade outer peripheral end and the inner diameter of the blade inner peripheral end, the outer peripheral side can ensure good workability while having the rib, and the impeller. The suction flow is not disturbed, so noise can be reduced. Further, when the blades are rotating through the impeller blowing region on the inner peripheral side, the ribs do not protrude toward the inner peripheral side, so that the flow on the inlet side of the blades is not disturbed, so that noise can be reduced.
- the rib is formed so as to straddle both the outer peripheral end of the blade and the inner peripheral end, when only the outer peripheral side is installed or only the inner peripheral side is installed, the flow by the rib on the downstream side where the rib is eliminated Therefore, the phenomenon that the flow becomes unstable at once and the flow is separated from the blade surface can be suppressed. Therefore, a low-noise cross-flow fan and an air conditioner equipped with the fan can be obtained.
- the rib outer peripheral end 14a of the blade suction surface side rib 14 is used in the region between the outer diameter of the blade outer peripheral end and the inner diameter of the blade inner peripheral end.
- the rib inner circumferential end 14b are inclined surfaces in contact with the arcuate blade outer circumferential end 15a and the blade inner circumferential end 15b, respectively, and the tip of the blade suction surface side rib 14 is formed in an arc shape.
- the thickness of the rib is not less than the minimum thickness of the wing and not more than the maximum thickness, the resin hot water in the molding die at the time of resin molding with a thickness thinner than the minimum thickness becomes worse, or more than the maximum thickness Since it is possible to prevent the occurrence of sink marks due to thick wall, the moldability is improved, and the change in blowing performance due to the variation in shape can be reduced. Therefore, a high quality cross-flow fan and an air conditioner equipped with the fan are obtained.
- the thickness of the rib is tapered from the blade surface to the tip, and the tips on the outer peripheral side and inner peripheral side of the blade are arc-shaped, so that the blade bites into the mold and breaks during mold release. This eliminates the risk of forming and improves moldability. Also, because the tip is not an edge but an arc shape, when cleaning the cross-flow fan, it is not a sharp edge, so it ensures good workability without imposing excessive tension on the operator, and if the flow flows in smoothly Since it flows in, no disturbance occurs and noise can be reduced. Therefore, a cross-flow fan with high manufacturability, high safety, and low noise and an air conditioner equipped with the cross-flow fan can be obtained.
- the rib height is at least half of the adjacent blade pitch
- the rib is located at the same rotational axis direction position in the impeller rotational axis direction. When installed, they do not interfere with each other and are not damaged. Also, if these ribs are installed in the vicinity of the connecting portions at different positions in the rotation axis direction, the gap between the ribs is narrowed and the passing wind speed is locally increased, so that abnormal fluid noise may occur. Loss and quality is maintained. Therefore, a high quality cross-flow fan and an air conditioner equipped with the fan are obtained.
- the blade suction surface which is the opposite side of the impeller rotation direction on the blade surface, tends to generate an unstable flow compared to the blade pressure surface, and this blade suction surface flows on the blade surfaces of different blade cross-sections adjacent to each other at the connecting part.
- the flow is unstable in the direction of the impeller rotation axis, the flow is concentrated in a certain area and the wind speed is high, and the flow tends to be peeled and disturbed at a low wind speed.
- the height of the ribs formed on both the impeller rotation direction side and the opposite side of the blade surface should be higher on the opposite side (blade suction surface side) than the impeller rotation direction side surface (blade pressure surface side).
- the unstable flow is regulated by forming the blade suction surface side where the unstable flow is likely to occur higher.
- the rib height is lowered at the blade pressure surface where the chord flow in the direction perpendicular to the axis of rotation is easy to form on the blade surface, reducing flow interference and bringing the ribs closer together. Abnormal fluid noise due to high-speed flow in the gap due to excess can be suppressed. Therefore, a smooth and quiet once-through fan and an air conditioner equipped with the fan can be obtained.
- the ribs were formed so that the position of the impeller rotational axis direction was different between the blade pressure surface and the negative pressure surface.
- the blade cross-sectional shape of the impeller is formed such that a forward region having a convex shape in the rotational direction and a backward region having a concave shape in the rotational direction appear alternately when viewed in the impeller rotational axis direction. Further, the forward region and the backward region are connected by a connecting portion.
- the rib When the rib is installed in such a blade shape, the rib has different shapes on the blade pressure surface and the suction surface.
- the rib is provided on the connecting portion or the advance region in the vicinity of the connecting portion on either the blade pressure surface side or the suction surface side.
- the rib is formed so as to be connected to the blade surface at an obtuse angle, so that the space is locally narrowed and the flow is locally prevented from being accelerated at that position. is doing.
- the wind speed distribution can be made uniform.
- the blade forming method includes a method in which the mold is moved radially in the impeller radial direction and released, and a mold is rotated in the impeller rotational direction and then moved in the impeller radial direction to release the mold. There is a way to do it. In both methods, there is a geometric restriction that the blade tip becomes an edge shape in order to move the molding die. Due to such restrictions, there has been a problem that the flow on the wing tends to peel off, and as a result, noise is generated.
- the wing and the support plate are individually formed, and both the outer peripheral side of the support plate have grooves for inserting and fixing the wing, and the support plate is provided with the plurality of wings.
- An impeller is formed by inserting and fixing. For this reason, it is possible to perform molding without the above-mentioned conventional problems, to allow free design, and to further increase efficiency and reduce noise. Therefore, a low-noise and high-efficiency cross-flow fan and an air conditioner equipped with the fan are obtained.
- a high efficiency, low noise, and high quality air conditioner can be obtained by mounting the above-described cross-flow fan having ribs on the blade surface in the air conditioner.
- the present invention relates to a ventilation resistor such as a heat exchanger or an air purifying filter, an impeller, a stabilizer that separates a suction-side flow path and a blow-off flow path, and a spiral guide provided on the blow-out side of the impeller.
- the present invention can be widely applied to devices having walls, and can reduce motor input, fluid abnormal noise due to blade surface separation, noise value reduction, and safety improvement. As a result, it is possible to obtain a high-quality air conditioner with high efficiency and energy saving, good audibility, low noise and quietness, which can prevent the impeller from condensing and releasing condensed water to the outside.
- the present invention may be implemented as an aspect in which the above-described rib is provided only on one of the pressure surface and the suction surface of the blade.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Abstract
Description
また、同目的を達成するため、本発明の空気調和機は、本体内における吸込側風路及び吹出側風路を区画するスタビライザーと、前記吸込側風路及び吹出側風路の間に配置された貫流ファンと、前記本体内に配置された通風抵抗体と、前記貫流ファンから放出された空気を前記本体の吹出口に導くガイドウォールとを備えており、前記貫流ファンは、上記の本発明に係る貫流ファンである。
図1は、本発明の実施の形態1における貫流ファンを搭載した空気調和機の部屋から見たときの設置概要図、図2は、図1の空気調和機の縦断面図、図3は、図1の空気調和機に搭載される貫流ファンの羽根車の正面部分断面図、図4は、図3の貫流ファンの羽根車の翼が1枚設けられた状態の斜視概要図で、吹出側風路(羽根車吹出領域)E2に位置するときの翼圧力面13a側から見た斜視図、図5は、図3の貫流ファンの羽根車の翼が1枚設けられた状態の斜視概要図で、吸込側風路(羽根車吸込領域)E1に位置するときの翼負圧面13b側から見た斜視図である。
「翼基本断面形状の効果」
翼8cのうち内周側端部15bの平面Qp、Qsを表面として有する部分を直線部Qと称する。翼8cの翼負圧面13bは、羽根車外周側から内周側にかけて多重円弧と直線部Qで形成されている。
まず、図8に示すように、翼圧力面13aに接する翼弦線Lとの平行線Wpと翼圧力面13aとの接点を、最大反り位置Mpとし、翼負圧面13bに接する翼弦線Lとの平行線Wsと翼負圧面13bとの接点を最大反り位置Msとする。また、最大反り位置Mpを通る翼弦線Lの垂線との交点を、最大反り翼弦点Ppとし、最大反り位置Msを通る翼弦線Lの垂線との交点を、最大反り翼弦点Psとする。また、円弧中心P2と最大反り翼弦点Ppとの距離を、翼弦最大反り長さLpとし、円弧中心P2と最大反り翼弦点Psとの距離を、翼弦最大反り長さLsとする。さらに、最大反り位置Mpと最大反り翼弦点Ppとの線分距離を最大反り高さHpとし、最大反り位置Msと最大反り翼弦点Psとの線分距離を最大反り高さHsとする。そして、翼弦最大反り長さLp、Lsと、翼弦長Loの比Lp/Lo、Ls/Loとを以下のように設定することで騒音を低減することができる。
最大反り高さHp、Hsが大きすぎると、曲面円弧半径が小さく、反りが大きすぎることがあり、最大反り高さHp、Hsが小さすぎると、曲面円弧半径が大きく、反りが小さすぎることがある。また、隣り合う翼8c同士の間隔が広すぎ流れを制御できず翼面で剥離渦が発生し流体異常音が発生したり、逆に狭すぎ風速が増加し騒音が大きくなったりすることがある。そこで、本実施の形態では、最適範囲の最大反り高さとなるように翼8cを形成することとする。
内周側曲面Bp2と平面Qpとの接続位置(第1接続位置)及び内周側曲面Bs2と平面Qsとの接続位置(第2接続位置)に接するように描かれる内接円の中心をP4(図9参照)とする。翼8cのうち直線部Qより外周側であって、内周側曲面Bp2及び内周側曲面Bs2との間を通る翼8cの中心線を肉厚中心線Sbとする。また、中心P4と円弧中心P2とを通る直線を延長線Sfとする。肉厚中心線Sbの中心P4における接線をSb1とする。接線Sb1と延長線Sfとのなす角度を屈曲角度θeとする。さらに、円弧中心P2を通る翼弦線Lの垂線と、中心P4を通る翼弦線Lの垂線との距離を直線部翼弦長さLfとする。翼の最大肉厚部における内接円の中心P3とする。中心P3を通る翼弦線に対する垂線と翼弦線との交点をPtとする。中心P3を通る翼弦線Lの垂線と、円弧中心P2を通る翼弦線Lの垂線との距離を最大肉厚部長さLt(図9では第3領域の翼弦長Lt3が図示)とする。
翼8cの羽根車内周側に形成した直線部Qの表面である平面Qs、Qpで形成された直線部Qが、羽根車外周側の多重円弧形状部に対し接することにより、または、羽根車回転方向へ屈曲することにより、内周側端部15bの翼肉厚t2が厚肉でも直線表面がない場合に比べ翼負圧面13bへ流れを向けることで内周側端部15bから羽根車内部へ流入する時の後流渦を抑制できる。しかし、屈曲角度が大きすぎると逆に後流渦幅が拡大したり、又は吹出側風路E2において、内周側端部15bで剥離が大きく発生したりし、効率が悪化しファンモータ入力が増加してしまう恐れがある。
翼8cの最大肉厚部が翼弦線Lの中点より羽根車外周側の場合(つまりLt/Loが50%より大きい場合)には、翼8cの負圧面と、この翼8cと隣り合う翼8cの圧力面とに接するように描かれる内接円の直径であらわされる翼間距離が狭くなる。これにより、通過風速が増加し、通風抵抗が増加し、ファンモータ入力が増加してしまう。
(19)貫流ファンの羽根車回転軸方向である長手方向において、羽根車回転軸に直交する翼断面図における翼の外周端部の外径は略同一であるので、従来のように外径が羽根車回転軸方向で異なるような翼形状に比べ、羽根車吸込領域と吹出領域を分離するスタビライザーでの漏れ流れを抑制でき効率向上できる。
(21)翼の翼圧力面13a及び13bの羽根車回転軸方向におけるリング8b近傍部である翼リング近傍部8caと隣り合う翼間部8ccとの連結部8ce近傍の翼リング近傍部8ca上に羽根車回転軸に略直交し、隣接する翼へ向け所定高さで立設するリブ14、16を形成しているので、リブが無い場合は連結部8ceで隣り合う異なる翼断面の翼の表面を流れる流れが羽根車回転軸方向に揺れ不安定となり、一部の領域に流れが集中し高風速となり、逆に流れが剥離気味となり低風速で乱れる恐れがあったが、風速の均一化や乱れの抑制を図れるので、貫流ファンの低騒音化並びに送風効率の向上によるモータ入力の低減が図れ、静粛で省エネな貫流ファン及びそれを搭載した空気調和機が得られる。
また、連結部8ceは隣り合う翼断面形状が徐々に変化する傾斜面であるので、翼面上の流れに、羽根車回転軸方向の急激な変化が生じないので、すなわち、段差による乱れが生じない。また、応力集中が回避できるので翼の破損の恐れも無くなり強度向上が図れる。
リブは、翼外周側端部の外径と翼内周側端部の内径との間の領域内に形成されるので、外周側はリブがありながら良好な作業性を確保でき、かつ羽根車の吸込流れを乱さないので低騒音化が図れる。また内周側も羽根車吹出領域を翼が回転通過しているとき、リブが内周側に突出しないため翼の入口側の流れを乱さないので低騒音化が図れる。さらに、リブが翼の外周側端部から内周側端部の両方にまたぐように形成されているので、外周側のみ設置や内周側のみ設置した場合、リブが無くなる下流側でリブによる流れの規制が無くなるため、一挙に流れが不安定になり翼表面から流れが剥離する現象を抑制できる。よって、低騒音な貫流ファン及びそれを搭載した空気調和機を得られる。
前記リブの変形例として図19のように、翼外周側端部の外径と翼内周側端部の内径との間の領域内において、翼負圧面側リブ14のリブ外周側端部14a及びリブ内周側端部14bは、それぞれ円弧形状の翼外周側端部15a及び翼内周側端部15bに接する傾斜面で、かつ翼負圧面側リブ14の先端を円弧形状で形成した場合、リブ外周側端部及びリブ内周側端部に流れがそれぞれ流入する時、流れの衝突が抑制されるので、下流側へ向かうにつれ後流幅の発達が抑制でき、乱れを抑制できるので、低騒音化できる。よって、低騒音な貫流ファン及びそれを搭載した空気調和機を得られる。
前記リブの肉厚は、翼の最小肉厚以上、最大肉厚以下であるので、最小肉厚より薄肉による樹脂成形時における成形金型での樹脂湯回りが悪くなることや、最大肉厚より厚肉によるヒケが生じることを防止できるので、成形性が向上し、形状のバラツキによる送風性能の変化が小さくできる。よって、高品質な貫流ファン及びそれを搭載した空気調和機が得られる。
前記リブの肉厚は、翼面から先端へ向け先細り形状で、かつ翼の外周側及び内周側の先端は円弧形状であるので、成形での離型の際、翼が金型に食い込み破損する恐れが無くなり、成形性が向上する。また、先端がエッジでなく円弧形状なので、貫流ファンを掃除するとき、シャープエッジではないので作業者に過度な緊張を強いることなく良好な作業性が確保され、また流れが流入した場合、滑らかに流入するので乱れが起きず低騒音化が図れる。よって、製造性が高く、安全性も高く、低騒音な貫流ファン及びそれを搭載した空気調和機が得られる。
また、リブ高さは、少なくとも隣接する翼ピッチの半分以下であるので、リブが翼の圧力面、負圧面の両方に配置される場合、羽根車回転軸方向で同一回転軸方向位置にリブが設置された時に、互いに干渉せず破損の恐れがない。また、それらのリブが回転軸方向で異なる位置で、それぞれ連結部付近に設置されると、リブ間での隙間が狭くなり通過風速が局所的に高速となるため流体異常音が発生することが無くなり、品質が保たれる。よって、高品質な貫流ファン及びそれを搭載した空気調和機が得られる。
翼表面の羽根車回転方向の逆側である翼負圧面は、翼圧力面に比べ不安定な流れになりやすく、この翼負圧面では、連結部で隣り合う異なる翼断面の翼の表面を流れる流れが羽根車回転軸方向に揺れ不安定となり、一部の領域に流れが集中し高風速となり、逆に流れが剥離気味となり低風速で乱れる恐れがあるところ、本実施の形態では、リブを翼負圧面に形成することで、リブにより風速の均一化や乱れの抑制を図ることができる。
また、リブを翼表面の羽根車回転方向側である翼圧力面に形成した場合、隣り合う翼の領域で、羽根車回転方向に対し、前進している領域から後退している領域へ流れが移動してしまう現象を抑え、各領域で流れを羽根車回転軸の直交方向へ導風するので、圧力上昇を阻害せず安定した流れが形成される。よって、送風効率が向上し、ファンモータ入力が低減し、省エネな貫流ファン及びそれを搭載した空気調和機が得られる。
リブを翼表面の羽根車回転方向側(翼圧力面側)、回転方向逆側(翼負圧面側)の両方に形成した場合、翼負圧面において、流れは連結部で隣り合う異なる翼断面の翼表面上の流れが羽根車回転軸方向に揺れる不安定流れ現象が抑制され、かつ翼負圧面、翼圧力面の両方では、隣り合う翼の領域で、羽根車回転方向に対し、前進している領域から後退している領域へ流れが移動してしまう現象を抑え、各領域で流れを羽根車回転軸の直交方向へ導風するので、圧力上昇を阻害せず安定した流れが形成される。また、両翼面にリブが形成されることで、さらに支持板とリブとの間の空間が仕切られることで、支持板近傍で別途翼間流路が形成されるので流れが規制され不安定現象が抑制される。よって、送風効率が向上し、ファンモータ入力が低減し、不安定現象による圧力変動が抑制される。その結果、省エネで低騒音な貫流ファン及びそれを搭載した空気調和機が得られる。
翼表面の羽根車回転方向側、逆側の両方に形成したリブの高さは、羽根車回転方向側面(翼圧力面側)に対し逆側(翼負圧面側)の方を高く形成することで、すなわち、不安定流れが生じやすい翼負圧面側の方を高く形成することで、不安定な流れが規制される。これは、同時に、もともと翼面で回転軸に直交方向の翼弦方向流れが形成しやすい翼圧力面でリブ高さを低くすることにもなり、流れの干渉を抑制し、リブ同士の接近しすぎによる隙間での高速流による流体異常音を抑制できる。よって、聴感の滑らかで静粛な貫流ファン及びそれを搭載した空気調和機を得られる。
また、リブは、翼圧力面、負圧面で羽根車回転軸方向位置が異なるように形成した。羽根車の翼断面形状は、回転方向に凸形状となる前進領域と、回転方向に凹形状となる後退領域が、羽根車回転軸方向で見ると交互に現れるように形成されている。また、前進領域と後退領域との間は、連結部にて接続されている。このような翼形状にリブを設置する場合は、リブを翼圧力面と負圧面とで異なる形状にしている。リブは、翼圧力面側及び負圧面側の何れにおいても、連結部、または連結部近傍の前進領域にリブを設けている。これにより、翼圧力面及び翼負圧面では、圧力の高い前進領域から、相対的に圧力の低い後退領域への流れを抑制することが出来る。加えて、翼負圧面では、リブが翼面に鈍角で接続するように形成することで、局所的に空間が狭くなることを抑制し、その位置で流れが局所的に高速になることを抑制している。これにより風速分布の均一化が図れる。その結果、低騒音化及び流れの漏れ抑制による送風効率向上が図れ、低騒音並びに高効率な貫流ファン及びそれを搭載した空気調和機が得られる。
翼の成形方法としては、成形金型を羽根車径方向に放射状に移動して離型する方法と、成形金型を羽根車回転方向に回転させた後に羽根車径方向に移動して離型する方法とがある。両方法とも、成形金型を移動させる為に翼端部がエッジ形状になるという形状的制約があった。このような制約により、翼上のながれが剥離しやすくなり、その結果騒音が発生するという問題が起きていた。これに対し、本実施の形態では、翼と支持板とをそれぞれ個別に成形し、支持板の外周側の両面に、翼を挿入し固着する溝部を有し、支持板に前記複数の翼を挿入、固着することで羽根車を形成する。このため、上記の従来の問題を伴わない成形が可能で、自由設計が可能となり、さらなる高効率化、低騒音化が可能となる。よって、低騒音で高効率な貫流ファン及びそれを搭載した空気調和機が得られる。
上述した翼面にリブを形成した貫流ファンを、空気調和機に搭載することで、高効率、低騒音、高品質な空気調和機が得られる。
Claims (15)
- 羽根車と、該羽根車を回転可能に支持するシャフトとを備える貫流ファンであって、
前記羽根車は、複数の支持板と、対応する一対の前記支持板の間に周方向に間隔をおいて配置された複数の翼とを有し、
前記翼は、羽根車回転軸に直交する翼断面が異なっている複数の領域を有し、
前記複数の領域は、前記翼において、前記羽根車回転軸の方向に並んでおり、
前記翼はさらに、前記複数の領域を連結する連結部を有しており、
前記翼は、少なくとも一つのリブを有しており、該リブは、前記連結部に形成されているか、あるいは、該連結部と隣り合う領域において、該連結部からその隣り合う領域の回転軸方向の長さの20%分まで離れた範囲内に形成されている、
貫流ファン。 - 前記翼は、前記複数の領域として、少なくとも一対の第1領域と、第2領域と、少なくとも一対の第3領域とを含んでおり、
前記第1領域はそれぞれ、羽根車に形成した状態での支持板に隣接する部分であり、
前記第2領域は、対応する一対の前記第1領域の間にある部分であり、
前記第3領域はそれぞれ、前記対応する一対の前記第1領域の間にあって、且つ、前記第2領域と対応する前記第1領域との間にあり、
前記第1領域と前記第3領域、及び、前記第2領域と前記第3領域は、それぞれ、前記連結部によって連結されており、
前記第1領域における翼出口角、前記第2領域における翼出口角、前記第3領域における翼出口角は相互に異なっている、
請求項1の貫流ファン。 - 前記連結部は対応する隣り合う前記領域における翼断面形状が徐々に変化した傾斜面で形成されている、
請求項1又は2の貫流ファン。 - 前記リブは、翼外周側端部の外径と翼内周側端部の内径との間の領域内に形成されている、
請求項1乃至3の何れか一項の貫流ファン。 - 前記リブにおけるリブ外周側端部及びリブ内周側端部は、それぞれ円弧形状の翼外周側端部及び翼内周側端部に接する傾斜面であり、
前記リブ外周側端部の先端及び前記リブ内周側端部の先端は、円弧形状に形成されている、
請求項1乃至4の何れか一項の貫流ファン。 - 前記リブの肉厚は、翼の最小肉厚以上であって最大肉厚以下である、
請求項1乃至5の何れか一項の貫流ファン。 - 前記リブの肉厚は、翼面から先端へ向け先細り形状であり、
前記リブ外周側端部の先端及び前記リブ内周側端部の先端は、円弧形状に形成されている、
請求項1乃至6の何れか一項の貫流ファン。 - 前記リブのリブ高さは、隣接する翼ピッチの半分以下である、
請求項1乃至7の何れか一項の貫流ファン。 - 前記リブは、翼表面のうち、少なくとも羽根車回転方向の逆側である翼負圧面に形成されている、
請求項1乃至8の何れか一項の貫流ファン。 - 前記リブは、翼表面のうち、少なくとも羽根車回転方向側である翼圧力面に形成されている、
請求項1乃至8の何れか一項の貫流ファン。 - 前記リブは、翼表面のうち、羽根車回転方向の逆側である翼負圧面と、羽根車回転方向側である翼圧力面との双方に形成されている、
請求項1乃至8の何れか一項の貫流ファン。 - 前記翼負圧面に形成された前記リブの高さは、前記翼圧力面に形成された前記リブの高さよりも高い、
請求項11の貫流ファン。 - 前記翼負圧面に形成された前記リブの羽根車回転軸方向の形成位置と、前記翼圧力面に形成された前記リブの羽根車回転軸方向の形成位置とは、相互に異なっている、
請求項11又は12の貫流ファン。 - 前記複数の支持板と前記複数の翼とはそれぞれ個別に成形されており、
前記支持板の側面には、対応する前記複数の翼を挿入する溝部が形成されており、
前記羽根車は、前記複数の翼を対応する前記溝部に挿入して固着する態様で構成されている、
請求項1乃至13の何れか一項の貫流ファン。 - 本体内における吸込側風路及び吹出側風路を区画するスタビライザーと、
前記吸込側風路及び吹出側風路の間に配置された貫流ファンと、
前記本体内に配置された通風抵抗体と、
前記貫流ファンから放出された空気を前記本体の吹出口に導くガイドウォールとを備えた空気調和機であって、
前記貫流ファンは、請求項1乃至14の何れか一項の貫流ファンである、
空気調和機。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014548576A JP6041895B2 (ja) | 2012-11-22 | 2013-11-19 | 空気調和機 |
EP13856078.4A EP2924296B1 (en) | 2012-11-22 | 2013-11-19 | Air conditioner |
CN201380066183.0A CN104870823B (zh) | 2012-11-22 | 2013-11-19 | 空调机 |
US14/646,077 US9995303B2 (en) | 2012-11-22 | 2013-11-19 | Air conditioner |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JPPCT/JP2012/080332 | 2012-11-22 | ||
PCT/JP2012/080332 WO2014080494A1 (ja) | 2012-11-22 | 2012-11-22 | 空気調和機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014080899A1 true WO2014080899A1 (ja) | 2014-05-30 |
Family
ID=50775699
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2012/080332 WO2014080494A1 (ja) | 2012-11-22 | 2012-11-22 | 空気調和機 |
PCT/JP2013/081150 WO2014080899A1 (ja) | 2012-11-22 | 2013-11-19 | 空気調和機 |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2012/080332 WO2014080494A1 (ja) | 2012-11-22 | 2012-11-22 | 空気調和機 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9995303B2 (ja) |
EP (1) | EP2924296B1 (ja) |
JP (1) | JP6041895B2 (ja) |
CN (1) | CN104870823B (ja) |
WO (2) | WO2014080494A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150184663A1 (en) * | 2013-12-30 | 2015-07-02 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
WO2023089658A1 (ja) * | 2021-11-16 | 2023-05-25 | 三菱電機株式会社 | クロスフローファン |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013150569A1 (ja) * | 2012-04-06 | 2013-10-10 | 三菱電機株式会社 | 空気調和装置の室内機 |
US10634168B2 (en) * | 2015-10-07 | 2020-04-28 | Mitsubishi Electric Corporation | Blower and air-conditioning apparatus including the same |
KR101769817B1 (ko) * | 2015-10-30 | 2017-08-30 | 엘지전자 주식회사 | 가습청정장치 |
EP3163178B1 (en) * | 2015-10-30 | 2020-10-07 | LG Electronics Inc. | Air conditioner |
WO2017134762A1 (ja) * | 2016-02-03 | 2017-08-10 | 三菱電機株式会社 | 空気調和機の室内機 |
JP6642498B2 (ja) * | 2017-03-14 | 2020-02-05 | ダイキン工業株式会社 | 両吸込型遠心ファン |
CN107687671B (zh) * | 2017-08-25 | 2023-11-14 | 珠海凌达压缩机有限公司 | 室内机和空调*** |
CN108105152B (zh) * | 2017-12-11 | 2024-05-14 | 珠海格力电器股份有限公司 | 贯流风叶叶片、贯流风叶、室内机和空调器 |
CN108180166A (zh) * | 2017-12-26 | 2018-06-19 | 博耐尔汽车电气***有限公司 | 一种空调电机风扇叶轮结构 |
DE202019100291U1 (de) * | 2018-01-19 | 2019-05-09 | Lg Electronics Inc. | Luftreiniger |
DE202019100290U1 (de) | 2018-01-19 | 2019-06-24 | Lg Electronics Inc. | Luftreiniger |
DE202019100292U1 (de) | 2018-01-19 | 2019-05-09 | Lg Electronics Inc. | Luftreiniger |
JP7446066B2 (ja) * | 2018-11-01 | 2024-03-08 | エルジー エレクトロニクス インコーポレイティド | 空気清浄機 |
KR102101680B1 (ko) * | 2019-06-03 | 2020-04-17 | 지플라이 주식회사 | 휴대용 공기 청정기 |
JP7271356B2 (ja) * | 2019-07-19 | 2023-05-11 | シャープ株式会社 | 送風装置、空気調和機 |
CN110749076B (zh) * | 2019-11-29 | 2024-03-29 | 广东美的制冷设备有限公司 | 导风板组件和空调器 |
CN114962288A (zh) * | 2021-02-22 | 2022-08-30 | 约克广州空调冷冻设备有限公司 | 用于离心风机的叶轮和离心风机 |
CN114543342B (zh) * | 2022-01-24 | 2024-04-19 | 青岛海尔空调器有限总公司 | 竖摆叶、风道组件、室内机及空调器 |
CN117450612A (zh) * | 2023-12-26 | 2024-01-26 | 兴恒环境科技集团有限公司 | 一种紫外线空气杀菌装置及空调器 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1077989A (ja) | 1996-09-02 | 1998-03-24 | Toshiba Corp | 横流ファン |
JP2006329100A (ja) | 2005-05-27 | 2006-12-07 | Daikin Ind Ltd | クロスフローファン |
JP2011196387A (ja) * | 2011-05-20 | 2011-10-06 | Mitsubishi Electric Corp | 貫流ファン及び空気調和機 |
JP4896213B2 (ja) | 2009-12-10 | 2012-03-14 | 三菱電機株式会社 | 貫流ファン及びこれを備えた空気調和機 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH09126190A (ja) | 1995-10-30 | 1997-05-13 | Sanyo Electric Co Ltd | 遠心式送風機 |
JP2006077723A (ja) * | 2004-09-13 | 2006-03-23 | Matsushita Electric Ind Co Ltd | 多翼ファン |
JP4973249B2 (ja) * | 2006-03-31 | 2012-07-11 | ダイキン工業株式会社 | 多翼ファン |
KR101649379B1 (ko) | 2010-01-13 | 2016-08-30 | 엘지전자 주식회사 | 횡류팬 및 이를 구비한 공기 조화기 |
CN102269169A (zh) * | 2010-06-02 | 2011-12-07 | 珠海格力电器股份有限公司 | 贯流风机及具有其的空调器 |
DE102010042325A1 (de) * | 2010-10-12 | 2012-04-12 | Behr Gmbh & Co. Kg | Lüfter mit Lüfterschaufeln |
JP5269036B2 (ja) * | 2010-11-08 | 2013-08-21 | 三菱電機株式会社 | 貫流ファン、およびそれを備えた空気調和機 |
JP5203478B2 (ja) * | 2011-03-02 | 2013-06-05 | シャープ株式会社 | 貫流ファン、成型用金型および流体送り装置 |
JP5369141B2 (ja) * | 2011-06-10 | 2013-12-18 | 三菱電機株式会社 | 空気調和機 |
-
2012
- 2012-11-22 WO PCT/JP2012/080332 patent/WO2014080494A1/ja active Application Filing
-
2013
- 2013-11-19 CN CN201380066183.0A patent/CN104870823B/zh active Active
- 2013-11-19 WO PCT/JP2013/081150 patent/WO2014080899A1/ja active Application Filing
- 2013-11-19 JP JP2014548576A patent/JP6041895B2/ja active Active
- 2013-11-19 EP EP13856078.4A patent/EP2924296B1/en active Active
- 2013-11-19 US US14/646,077 patent/US9995303B2/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1077989A (ja) | 1996-09-02 | 1998-03-24 | Toshiba Corp | 横流ファン |
JP2006329100A (ja) | 2005-05-27 | 2006-12-07 | Daikin Ind Ltd | クロスフローファン |
JP4896213B2 (ja) | 2009-12-10 | 2012-03-14 | 三菱電機株式会社 | 貫流ファン及びこれを備えた空気調和機 |
JP2011196387A (ja) * | 2011-05-20 | 2011-10-06 | Mitsubishi Electric Corp | 貫流ファン及び空気調和機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2924296A4 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150184663A1 (en) * | 2013-12-30 | 2015-07-02 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
US9885361B2 (en) * | 2013-12-30 | 2018-02-06 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
WO2023089658A1 (ja) * | 2021-11-16 | 2023-05-25 | 三菱電機株式会社 | クロスフローファン |
Also Published As
Publication number | Publication date |
---|---|
JP6041895B2 (ja) | 2016-12-14 |
EP2924296B1 (en) | 2018-10-03 |
US9995303B2 (en) | 2018-06-12 |
JPWO2014080899A1 (ja) | 2017-01-05 |
WO2014080494A1 (ja) | 2014-05-30 |
CN104870823A (zh) | 2015-08-26 |
CN104870823B (zh) | 2017-09-19 |
EP2924296A4 (en) | 2016-08-03 |
US20150292508A1 (en) | 2015-10-15 |
EP2924296A1 (en) | 2015-09-30 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6041895B2 (ja) | 空気調和機 | |
WO2013150673A1 (ja) | 空気調和装置の室内機 | |
JP4973249B2 (ja) | 多翼ファン | |
JP5806327B2 (ja) | クロスフローファン | |
WO2012002081A1 (ja) | ファン、成型用金型および流体送り装置 | |
WO2013031046A1 (ja) | 空気調和機 | |
JP2000065418A (ja) | 空気調和機 | |
JP5774206B2 (ja) | 空気調和装置の室内機 | |
JP5179638B2 (ja) | ファン、成型用金型および流体送り装置 | |
JP6000454B2 (ja) | 空気調和装置の室内機 | |
WO2015064617A1 (ja) | 貫流ファン及び空気調和機 | |
JP6710337B2 (ja) | 空気調和機 | |
WO2015063851A1 (ja) | 貫流ファン及び空気調和機 | |
JP2008070110A (ja) | 空気調和機 | |
JP6625213B2 (ja) | 多翼ファン及び空気調和機 | |
NZ700985B2 (en) | Indoor unit for air conditioning device | |
NZ716887B2 (en) | Indoor unit for air-conditioning apparatus |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13856078 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2014548576 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14646077 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2013856078 Country of ref document: EP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |