EP3015775A1 - Innenraumeinheit für eine klimaanlagenvorrichtung - Google Patents

Innenraumeinheit für eine klimaanlagenvorrichtung Download PDF

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Publication number
EP3015775A1
EP3015775A1 EP14816588.9A EP14816588A EP3015775A1 EP 3015775 A1 EP3015775 A1 EP 3015775A1 EP 14816588 A EP14816588 A EP 14816588A EP 3015775 A1 EP3015775 A1 EP 3015775A1
Authority
EP
European Patent Office
Prior art keywords
blade
air
impeller
regions
blades
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.)
Granted
Application number
EP14816588.9A
Other languages
English (en)
French (fr)
Other versions
EP3015775A4 (de
EP3015775B1 (de
Inventor
Takashi Ikeda
Mitsuhiro Shirota
Seiji Hirakawa
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3015775A1 publication Critical patent/EP3015775A1/de
Publication of EP3015775A4 publication Critical patent/EP3015775A4/de
Application granted granted Critical
Publication of EP3015775B1 publication Critical patent/EP3015775B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans

Definitions

  • the present invention relates to an indoor unit for an air-conditioning apparatus.
  • Patent Literature 1 there is proposed a cross-flow fan having a step recessed on a blade outer peripheral-side distal end portion side, which is formed at a blade outer peripheral-side end portion of a suction surface, in which a step leading edge portion or a step trailing edge portion of the step is extended obliquely with respect to the blade outer peripheral-side distal end portion.
  • Patent Literature 2 there is proposed a cross-flow fan having a sawtooth pattern formed on a blade surface of a blade, and a step formed at a position located at a predetermined distance from a blade edge along which the sawtooth pattern is formed.
  • Patent Literature 3 there is proposed a cross-flow fan in which, when a length of the blade in a longitudinal direction is divided into a plurality of regions, namely, first regions each adjacent to a support plate, a second region corresponding to a blade central portion, and third regions between the first regions and the second region, a blade outlet angle at the blade outer peripheral end portion in each of the regions becomes larger in the order of second region ⁇ first region ⁇ third region.
  • a height of the step is uniform in a fan rotation axis direction of the blade, and the height of the step is excessively large in a region where an air velocity is low relative to a difference in air velocity in the fan rotation axis direction. As a result, separation may occur in some regions to increase noise in a broad band.
  • the separation may occur due to the difference in air velocity. Further, on a fan air inlet side, the separation may occur because appropriate measures are not sufficiently taken against fluctuation to be caused by a variation in air velocity in each rotation of the fan.
  • the present invention has been made in view of the above, and it is an object of the present invention to provide an indoor unit for an air-conditioning apparatus capable of suppressing separation and reducing increase in noise.
  • an indoor unit for an air-conditioning apparatus including: a main body including an air inlet and an air outlet; a cross-flow fan arranged inside the main body in a rotatable manner, the cross-flow fan including an impeller for causing air to be taken into the main body through the air inlet and causing the air to be blown out through the air outlet; and a stabilizer for partitioning a space inside the main body into an air inlet-side flow passage on an upstream side with respect to the cross-flow fan and an air outlet-side flow passage on a downstream side with respect to the cross-flow fan, in which the impeller includes a plurality of blades, in which the plurality of blades each include, in vertical sectional view, a step formed between an outer peripheral-side end portion and an inner peripheral-side end portion of the blades on at least one of a suction surface or a pressure surface being surfaces of the blades, in which the step is formed
  • the step may include projections and recesses that are formed along the surfaces of the blades to be projected and recessed in a direction orthogonal to a longitudinal direction of each of the blades.
  • the impeller may include a plurality of support plates, and the plurality of blades arranged between a corresponding pair of the support plates at intervals in a circumferential direction.
  • the blades may each include at least a pair of first regions, a second region, and at least a pair of third regions as a plurality of regions that are different from each other in blade cross-section orthogonal to the rotation axis of the impeller.
  • the first regions may be respectively parts that are adjacent to the support plates under a state in which the support plates are mounted to the impeller.
  • the second region may be a part that is arranged between the corresponding pair of first regions.
  • the third regions may be respectively arranged between the corresponding pair of first regions and between the second region and the corresponding first regions.
  • a blade outlet angle of the first region, a blade outlet angle of the second region, and a blade outlet angle of the third region may be different from each other.
  • the step may be formed in a boundary portion between an inner peripheral-side part in which three patterns of the first regions, the second region, and the third regions in the blade cross-section have the same shape, and an outer peripheral-side part in which the three patterns of the first regions, the second region, and the third regions in the blade cross-section have different shapes.
  • the separation can be suppressed and the increase in noise can be reduced.
  • FIG. 1 is a view for illustrating an installation state of an air-conditioning apparatus according to a first embodiment of the present invention when viewed from an inside of a room.
  • FIG. 2 is a vertical sectional view for illustrating the air-conditioning apparatus.
  • FIG. 3 is a view for illustrating front and lateral sides of an impeller of a cross-flow fan to be mounted to the air-conditioning apparatus. Specifically, the part illustrated on the left side of the drawing sheet of FIG. 3 is a front view for illustrating the impeller, and the part illustrated on the right side of the drawing sheet of FIG. 3 is a side view for illustrating the impeller. Further, FIG. 4 to FIG. 6 are each a sectional view taken along the line III-III in FIG.
  • FIG. 7 is a perspective view of one of the blades of the impeller when viewed from a pressure surface side. Note that, in FIG. 4 to FIG. 6 , hatching is omitted for the sake of clarity of illustration of an inside between blade surfaces.
  • the blades of the cross-flow fan to be mounted to the indoor unit are improved so as to be able to suppress noise and reduce electric power consumption of a fan motor.
  • a main body 1 serving as an outer shell of an indoor unit 100 includes a front panel 1a, a pair of lateral surfaces 1b, and an upper surface 1c.
  • the indoor unit 100 is an indoor unit of a wall hanging type to be installed to a wall 11a of a room 11 being a space to be air-conditioned, but the present invention is not limited thereto.
  • the indoor unit 100 is not limited to be installed in the room 11, and may be installed, for example, in a room in a building or in a storage.
  • an air inlet 2 for allowing indoor air to be sucked therethrough into the indoor unit 100 is formed.
  • an air outlet 3 for allowing conditioned air to be supplied therethrough into the room, and a guide wall 10 for guiding air discharged from a cross-flow fan 8 described later into the air outlet 3.
  • a filter 5 for removing, for example, dust in the air sucked through the air inlet 2
  • a heat exchanger 7 for transferring heating energy or cooling energy of refrigerant into air so as to generate the conditioned air
  • a stabilizer 9 for partitioning an air inlet-side air passage E1 and an air outlet-side air passage E2 from each other
  • the cross-flow fan 8 for causing the air to be sucked through the air inlet 2 and causing the air to be blown out through the air outlet 3
  • vertical airflow direction vanes 4a and horizontal airflow direction vanes 4b for adjusting a direction of the air blown out of the cross-flow fan 8.
  • the air inlet 2 is an opening for allowing the indoor air to be forcibly sucked by the cross-flow fan 8 into the indoor unit 100.
  • the air inlet 2 is formed only in the opening through the upper surface of the main body 1 in the example illustrated in FIG. 1 and FIG. 2 , but may be formed in an opening through the front panel 1a. Further, the air inlet 2 is not particularly limited in shape.
  • the air outlet 3 is an opening for allowing the air, which is taken through the air inlet 2 and passes through the heat exchanger 7, to be supplied through the air outlet 3 into the room.
  • the air outlet 3 is opened through the front panel 1a. Note that, the air outlet 3 is not particularly limited in shape.
  • the guide wall 10 is configured to form the air outlet-side air passage E2 cooperatively with a lower surface side of the stabilizer 9.
  • the guide wall 10 forms a slope inclined from the cross-flow fan 8 toward the air outlet 3. It is preferred that the slope be formed so as to correspond to, for example, a part of a spiral shape.
  • the filter 5 is formed, for example, into a mesh-like shape to remove the dust in the air sucked through the air inlet 2.
  • the filter 5 is arranged in an air passage from the air inlet 2 to the air outlet 3 (central portion in the main body 1), specifically, on a downstream side with respect to the air inlet 2 and on an upstream side with respect to the heat exchanger 7.
  • the heat exchanger 7 (indoor heat exchanger) functions as an evaporator during a cooling operation to cool the air, and functions as a condenser (radiator) during a heating operation to heat the air.
  • the heat exchanger 7 is arranged in the air passage from the air inlet 2 to the air outlet 3 (central portion in the main body 1), specifically, on a downstream side with respect to the filter 5 and on an upstream side with respect to the cross-flow fan 8. Note that, in FIG. 2 , the heat exchanger 7 is formed into a shape surrounding a front portion and an upper portion of the cross-flow fan 8, but is not particularly limited thereto.
  • the heat exchanger 7 is connected to an outdoor unit including a compressor, an outdoor heat exchanger, an expansion device, and the like to form a refrigeration cycle. Further, as an example of the heat exchanger 7, there is given a fin-and-tube heat exchanger of a cross fin type including heat transfer tubes and a large number of fins.
  • the stabilizer 9 is arranged under the heat exchanger 7 so as to partition the air inlet-side air passage E1 and the air outlet-side air passage E2 from each other.
  • the air inlet-side air passage E1 is formed on an upper surface side of the stabilizer 9, and the air outlet-side air passage E2 is formed on the lower surface side of the stabilizer 9.
  • the stabilizer 9 includes a drain pan 6 for temporarily accumulating dew condensation water adhering to the heat exchanger 7.
  • the cross-flow fan 8 is configured to suck the indoor air through the air inlet 2, and to blow out the conditioned air through the air outlet 3.
  • the cross-flow fan 8 is arranged in the air passage from the air inlet 2 to the air outlet 3 (central portion in the main body 1), specifically, on a downstream side with respect to the heat exchanger 7 and on an upstream side with respect to the air outlet 3.
  • the cross-flow fan 8 includes an impeller 8a, a motor 12 for rotating the impeller 8a, and a motor shaft 12a for transmitting rotation of the motor 12 to the impeller 8a.
  • the impeller 8a is made of a thermoplastic resin such as an ABS resin, and is rotated to suck the indoor air through the air inlet 2 and send the conditioned air into the air outlet 3.
  • the impeller 8a includes a plurality of impeller elements 8d coupledto each other.
  • the impeller elements 8d each include a plurality of blades 8c and a ring 8b serving as a support plate fixed on an endportion side of the plurality of blades 8c.
  • the impeller 8a is an integral member formed by welding and coupling the plurality of impeller elements 8d each including the plurality of blades 8c that are sequentially formed to extend substantially perpendicularly from a lateral surface of an outer peripheral portion of the disk-like ring 8b at predetermined intervals in a circumferential direction of the ring 8b.
  • the impeller 8a includes a fan boss 8e and a fan shaft 8f.
  • the fan boss 8e is a part projecting to an inside of the impeller 8a.
  • the motor shaft 12a is fixed to the fan shaft 8f with a screw or the like.
  • One side of the impeller 8a is supported by the motor shaft 12a through intermediation of the fan boss 8e, and another side of the impeller 8a is supported by the fan shaft 8f.
  • the impeller 8a can be rotated in a rotation direction RO about a rotation axis center O of the impeller 8a under a state in which both the end sides thereof are supported, and, as illustrated in FIG. 2 , the impeller 8a can suck the indoor air through the air inlet 2 and send the conditioned air into the air outlet 3.
  • the vertical airflow direction vanes 4a are configured to adjust a vertical direction of the air blown out of the cross-flow fan 8
  • the horizontal airflow direction vanes 4b are configured to adjust a horizontal direction of the air blown out of the cross-flow fan 8.
  • the vertical airflow direction vanes 4a are arranged on a downstream side with respect to the horizontal airflow direction vanes 4b. As illustrated in FIG. 2 , the vertical airflow direction vanes 4a are mounted to the guide wall 10 so that upper portions of the vertical airflow direction vanes 4a are freely turnable.
  • the horizontal airflow direction vanes 4b are arranged on an upstream side with respect to the vertical airflow direction vanes 4a. As illustrated in FIG. 1 , the vertical airflow direction vanes 4a are turned under a state in which both end portion sides of the vertical airflow direction vanes 4a are supported by parts that define the air outlet 3 in the main body 1.
  • an outer peripheral-side end portion 15a and an inner peripheral-side end portion 15b of the blade 8c are each formed into, for example, a circular-arc shape.
  • the blade 8c is formed so that the outer peripheral-side end portion 15a is tilted forward along the impeller rotation direction RO with respect to the inner peripheral-side end portion 15b.
  • a pressure surface 13a and a suction surface 13b of the blade 8c are curved forward along the impeller rotation direction RO as being shifted from the rotation axis O of the impeller 8a toward an outer side of the blade 8c.
  • the blade 8c is formed into such an arcuate shape that a vicinity of a center of the blade 8c is farthest from a straight line connecting the outer peripheral-side end portion 15a and the inner peripheral-side end portion 15b to each other.
  • a center of a circle corresponding to the circular-arc shape formed on the outer peripheral-side end portion 15a is represented by P1 (also referred to as “circular-arc center P1")
  • a center of a circle corresponding to the circular-arc shape formed on the inner peripheral-side end portion 15b is represented by P2 (also referred to as “circular-arc center P2").
  • a line segment connecting the circular-arc centers P1 and P2 to each other is defined as a chord line L.
  • a length of the chord line L is represented by Lo (hereinafter also referred to as "chord length Lo").
  • the blade 8c has the pressure surface 13a as a surface on a forward side in the rotation direction RO of the impeller 8a, and the suction surface 13b as a surface on a rearward side in the rotation direction RO of the impeller 8a.
  • the blade 8c is formed into a concave shape curved in a vicinity of a center of the chord line L in a direction from the pressure surface 13a toward the suction surface 13b.
  • both the pressure surface 13a and the suction surface 13b are curved in a concavedmanner toward the rearward side in the rotation direction RO.
  • an outer peripheral side of the impeller 8a and an inner peripheral side of the impeller 8a are different from each other in radius of a circle corresponding to a circular-arc shape on the pressure surface 13a side.
  • a surface of the blade 8c on the pressure surface 13a side includes an outer peripheral-side curved surface Bp1 having a radius (circular-arc radius) Rp1, which corresponds to a circular-arc shape on the outer peripheral side of the impeller 8a, and an inner peripheral-side curved surface Bp2 having a radius (circular-arc radius) Rp2, which corresponds to a circular-arc shape on the inner peripheral side of the impeller 8a.
  • the surface of the blade 8c on the pressure surface 13a side is a circular-arc curved surface having a plurality of curvatures.
  • a flat surface Qp having a flat surface shape and being connected to an end portion of the inner peripheral-side curved surface Bp2 on the inner peripheral side.
  • the surface of the blade 8c on the pressure surface 13a side is formed of the outer peripheral-side curved surface Bp1, the inner peripheral-side curved surface Bp2, and the flat surface Qp that are connected continuously with each other.
  • a surface of the blade 8c on the suction surface 13b side is a surface corresponding to the surface on the pressure surface 13a side.
  • the surface of the blade 8c on the suction surface 13b side includes an outer peripheral-side curved surface Bs1 having a radius (circular-arc radius) Rs1, which corresponds to the circular-arc shape on the outer peripheral side of the impeller 8a, and an inner peripheral-side curved surface Bs2 having a radius (circular-arc radius) Rs2, which corresponds to the circular-arc shape on the inner peripheral side of the impeller 8a.
  • a flat surface Qs having a flat surface shape and being connected to an end portion of the inner peripheral-side curved surface Bs2 on the inner peripheral side.
  • the surface of the blade 8c on the suction surface 13b side is formed of the outer peripheral-side curved surface Bs1, the inner peripheral-side curved surface Bs2, and the flat surface Qs that are connected continuously with each other.
  • a blade thickness t1 of the outer peripheral-side end portion 15a is smaller than a blade thickness t2 of the inner peripheral-side end portion 15b.
  • the blade thickness t1 is twice as large as a radius R1 of the inscribed circle at the outer peripheral-side end portion 15a
  • the blade thickness t2 is twice as large as a radius R2 of a circle forming the circular arc of the inner peripheral-side end portion 15b.
  • the blade 8c when the diameter of the inscribed circle that is tangent to the pressure surface 13a and the suction surface 13b of the blade 8c is defined as the blade thickness, the blade 8c is formed so that the blade thickness is smaller at the outer peripheral-side end portion 15a than at the inner peripheral-side end portion 15b, gradually increased from the outer peripheral-side end portion 15a toward the center to become largest at a predetermined position in the vicinity of the center, gradually reduced toward the inner peripheral side, and is substantially uniform in a straight portion Q.
  • the blade thickness of the blade 8c is gradually increased from the outer peripheral-side end portion 15a toward the center of the blade 8c, reaches a maximum thickness t3 at the predetermined position in the vicinity of the center of the chord line L, and is gradually reduced toward the inner peripheral-side end portion 15b. Then, the blade thickness is maintained substantially at a fixed value of the inner peripheral-side end portion thickness t2 within a range of the straight portion Q, specifically, a range between the flat surface Qp and the flat surface Qs.
  • the suction surface 13b of the blade 8c includes a plurality of circular arcs and the straight portion Q bent therefrom, which are formed from the outer peripheral side to the inner peripheral side of the impeller.
  • a step 16 is formed at a position between the outer peripheral-side end portion 15a and the inner peripheral-side end portion 15b in a chord direction of the blade.
  • the step 16 is formed so that, on each of the surfaces (corresponding pressure surface 13a and corresponding suction surface 13b) of the blade, a fan inner peripheral-side part with respect to the step 16 is further projected (larger in blade thickness) than a fan outer peripheral-side part with respect to the step 16.
  • the step 16 is formed so as to extend obliquely with respect to the impeller rotation axis, and to vary (gradually increase or decrease) in height over a direction of the impeller rotation axis.
  • the step 16 is formed along a step base line 16a that is inclined at a predetermined angle ⁇ with respect to a straight line O1 parallel to the impeller rotation axis O so that the step height is gradually increased in a direction in which the step base line 16a is separated from the blade outer peripheral-side end portion 15a.
  • a pressure surface-side step height Hd1 and a suction surface-side step height Hd2 are gradually varied in a longitudinal direction of the blade.
  • a tangent point between the pressure surface 13a and a parallel line Wp that is tangent to the pressure surface 13a and parallel to the chord line L is defined as a maximum camber position Mp
  • a tangent point between the suction surface 13b and a parallel line Ws that is tangent to the suction surface 13b and parallel to the chord line L is defined as a maximum camber position Ms.
  • an intersection between the chord line L and a perpendicular line that is perpendicular to the chord line L and passes through the maximum camber position Mp is defined as a maximum chord camber-point Pp
  • an intersection between the chord line L and a perpendicular line that is perpendicular to the chord line L and passes through the maximum camber position Ms is defined as a maximum chord camber-point Ps
  • a distance between the circular-arc center P2 and the maximum chord camber-point Pp is defined as the maximum chord camber-length Lp
  • a distance between the circular-arc center P2 and the maximum chord camber-point Ps is defined as the maximum chord camber-length Ls.
  • a distance of a line segment between the maximum camber position Mp and the maximum chord camber-point Pp is defined as a maximum camber height Hp
  • a distance of a line segment between the maximum camber position Ms and the maximum chord camber-point Ps is defined as a maximum camber height Hs.
  • the blade 8c is formed so that the maximum camber positions fall within an optimum range.
  • the circular-arc radii of the inner peripheral-side curved surfaces Bs2 and Bp2 of the blade 8c are small. Further, when the circular-arc radii of the inner peripheral-side curved surfaces Bs2 and Bp2 of the blade 8c are small, the blade 8c is sharply cambered to form a steep curve.
  • the air outlet-side air passage E2 the air stream having passed along the flat surface Qs and the flat surface Qp through the inner peripheral-side end portion 15b cannot flow along the inner peripheral-side curved surfaces Bs2 and Bp2. As a result, the air stream is separated to cause pressure fluctuation.
  • the ratios Ls/Lo and Lp/Lo are each more than 50%, and the maximum camber positions are located on the impeller outer peripheral side, the circular-arc radii of the outer peripheral-side curved surfaces Bs1 and Bp1 of the blade 8c are large. Further, when the circular-arc radii of the outer peripheral-side curved surfaces Bs1 and Bp1 of the blade 8c are large, the camber of the blade 8c is small. Thus, the air streams are separated from the outer peripheral-side curved surfaces Bs1 and Bp1 of the blade 8c, with the result that trailing vortices are intensified.
  • the ratios Lp/Lo and Ls/Lo each fall within a range of from 40% to 50%, when the relationship of Ls/Lo>Lp/Lo is satisfied, the maximum camber position of the suction surface 13b is located closer to the outer peripheral side than that of the pressure surface 13a. With this, intervals between the adjacent blades 8c each repeatedly fluctuate from the inner peripheral-side end portion 15b toward the outer peripheral-side end portion 15a. As a result, pressure fluctuation occurs.
  • the blade 8c is formed so as to satisfy the relationship of 40% ⁇ Ls/Lo ⁇ Lp/Lo ⁇ 50%.
  • the air streams can be suppressed from being separated from the blade surfaces on both the air inlet side and the air outlet side of the impeller.
  • noise can be suppressed, and electric power consumption of the fan motor can be reduced.
  • the indoor unit 100 for the air-conditioning apparatus having mounted thereto the cross-flow fan 8 with excellent quietness and high energy efficiency can be provided.
  • the circular-arc radii of the curved surfaces may be small to cause excessively sharp cambering. Meanwhile, when the maximum camber heights Hp and Hs are excessively small, the circular-arc radii of the curved surfaces may be large to cause excessively small cambering. Further, when the intervals between the adjacent blades 8c are excessively large, the air stream cannot be controlled. As a result, separation vortices may be formed between the blade surfaces to generate fluid abnormal noise. In contrast, when the intervals are excessively small, the air velocity may be increased to generate louder noise. As a countermeasure, in this embodiment, the blade 8c is formed so that the maximum camber heights fall within an optimum range.
  • Hp and Hs respectively represent the maximum camber heights of the pressure surface 13a and the suction surface 13b, and hence the relationship of Hs>Hp is established.
  • ratios Hs/Lo and Hp/Lo are each less than 10%, the circular-arc radii of the curved surfaces are large to cause excessively small cambering.
  • the intervals between the adjacent blades 8c are excessively large, and hence the air stream cannot be controlled.
  • the separation vortices may be formed between the blade surfaces to generate the fluid abnormal noise.
  • a noise level may be abruptly increased.
  • the ratios Hs/Lo and Hp/Lo are each more than 25%, the intervals between the adjacent blades are excessively small, with the result that the air velocity may be increased to abruptly worsen noise.
  • the blade 8c is formed so as to satisfy the relationship of 25% ⁇ Hs/Lo>Hp/Lo ⁇ 10%.
  • the air streams can be suppressed from being separated from the blade surfaces on both the air inlet side and the air outlet side of the impeller.
  • noise can be suppressed, and electric power consumption of the fan motor can be reduced.
  • the indoor unit 100 for the air-conditioning apparatus having mounted thereto the cross-flow fan 8 with excellent quietness and high energy efficiency can be provided.
  • a center of an inscribed circle that is tangent to a connection position (first connection position) between the inner peripheral-side curved surface Bp2 and the flat surface Qp and a connection position (second connection position) between the inner peripheral-side curved surface Bs2 and the flat surface Qs is represented by P4.
  • a center line of the blade 8c, which passes between the inner peripheral-side curved surface Bp2 and the inner peripheral-side curved surface Bs2 on the outer peripheral side with respect to the straight portion Q in the blade 8c, is defined as a thickness center line Sb.
  • a straight line passing through the center P4 and the circular-arc center P2 is defined as an extending line Sf.
  • a tangent line that is tangent to the thickness center line Sb at the center P4 is represented by Sb1.
  • An angle formed between the tangent line Sb1 and the extending line Sf is defined as a bending angle ⁇ e.
  • a distance between a perpendicular line that is perpendicular to the chord line L and passes through the circular-arc center P2, and a perpendicular line that is perpendicular to the chord line L and passes through the center P4 is defined as a straight portion chord length Lf.
  • a center of an inscribed circle that is tangent to a thickest portion of the blade is represented by P3.
  • An intersection between a perpendicular line that is perpendicular to the chord line and passes through the center P3 and the chord line is represented by Pt.
  • a distance between the perpendicular line that is perpendicular to the chord line L and passes through the center P3, and the perpendicular line that is perpendicular to the chord line L and passes through the circular-arc center P2 is defined as a thickest portion length Lt.
  • the reference symbol ⁇ b represents a blade outlet angle.
  • chord length Lf of the straight portion Q is excessively small with respect to the chord length Lo, that is, when the inner peripheral side of the blade is formed mostly of the curved surfaces, there arises a problem in that negative pressure is not generated on the suction surface 13b after the air stream impinges on the inner peripheral-side end portion 15b, and hence the air stream is separated without being re-adhered to cause louder noise.
  • airflow resistance is increased by a large amount of dust accumulated on the filter 5, such a problem conspicuously occurs.
  • the blade 8c is formed so as to satisfy the relationship of 30% ⁇ Lf/Lo ⁇ 5%.
  • the air streams can be suppressed frombeing separated from the blade surfaces on both the air inlet side and the air outlet side of the impeller.
  • noise can be suppressed, and electric power consumption of the fan motor can be reduced.
  • the indoor unit 100 for the air-conditioning apparatus having mounted thereto the cross-flow fan 8 with excellent quietness and high energy efficiency can be provided.
  • the blade formed as described above provides advantages as described below.
  • the air streams can be suppressed from being separated from the blade surfaces on both the air inlet side and the air outlet side of the impeller.
  • noise can be suppressed, and electric power consumption of the fan motor can be reduced.
  • the indoor unit 100 having mounted thereto the cross-flow fan 8 with excellent quietness and high energy efficiency can be provided.
  • FIG. 8 is a view for illustrating the second embodiment of the present invention in the same manner as that of FIG. 7 . Note that, except for the parts described below, the second embodiment is similar to the first embodiment described above.
  • a blade 8c' of an impeller has a step 16' including a plurality of projections and recesses that are formed forward to the blade outer peripheral side and rearward therefrom along the direction of the chord L continuously over the direction of the impeller rotation axis.
  • the step 16' includes projections and recesses that are formed along the blade surface to be projected and recessed in a direction orthogonal to the longitudinal direction of the blade (direction parallel to the impeller rotation axis). Further, those projections and recesses are formed of acute peaks and valleys that are alternately arrayed along a step base line 16a'.
  • the step 16' formed as described above provides such a function that, even when the air stream is almost separated at the step, a longitudinal vortex generated by the projections and the recesses forces down the air stream onto the blade surface. With this, the effective flow passage between the blades is enlarged to reduce airflow resistance between the blades, and hence passage loss is reduced. Thus, the load torque is reduced, with the result that electric power consumption of the fan motor is reduced. In this way, an indoor unit for an air-conditioning apparatus with high energy efficiency can be provided.
  • FIG. 9 is a view for illustrating the third embodiment of the present invention in the same manner as that of FIG. 7 .
  • FIG. 10 is a view for illustrating a state of the blade of FIG. 9 when viewed along an extension direction of the outer peripheral-side end portion, that is, when viewed along the arrow X in FIG. 6 .
  • the step 16 is formed along the step base line 16a forming the predetermined angle ⁇ with respect to the straight line O1 parallel to the impeller rotation axis O, and the step 16' includes the projections and the recesses that are formed alternately along the step base line 16a.
  • the heights of those steps 16 and 16' are gradually increased over the longitudinal direction of the blade.
  • the present invention is not limited thereto, and includes such a mode that the height of the step is increased and reduced over the longitudinal direction.
  • FIG. 9 and FIG. 10 are illustrations of an example of such a mode, in particular, a mode that the step includes convex portions and concave portions formed alternately along the step base line, and that the height of the step is increased and reduced over the longitudinal direction.
  • a step 16" is formed in such a mode that a plurality of convex portions and a plurality of concave portions are formed forward and rearward in the direction of the chord L continuously over the direction of the impeller rotation axis. Further, a forward amount and a rearward amount of the convex portions and the concave portions become larger as a position of the step approaches to one side in the longitudinal direction of the blade. In addition, a height of the step 16" is increased or reduced over the longitudinal direction of the blade. More specifically, an increasing rate of the height of the step 16" becomes higher as the position of the step approaches to one side in the longitudinal direction of the blade.
  • the step is formed at the predetermined angle ⁇ with respect to the impeller rotation axis O.
  • the step causes the air stream to be forced down onto an adjacent suction surface. With this, the separation can be suppressed.
  • the mode in the illustration corresponds to an example in which the height of the step of the second embodiment is increased and reduced over the longitudinal direction, but the third embodiment may also be carried out in such a mode that the height of the step of the first embodiment is increased and reduced over the longitudinal direction.
  • FIG. 11 is a view for illustrating the fourth embodiment of the present invention in the same manner as that of FIG. 3 .
  • FIG. 12 is a view for illustrating cross-sections taken along the line A-A, the line B-B, and the line C-C in FIG. 11 in a superimposed manner.
  • FIG. 13 is a perspective view of the blade of the impeller of FIG. 11 when viewed from the pressure surface side. Note that, in FIG. 12 , hatching is omitted for the sake of clarity of illustration of the inside between the blade surfaces. Further, except for the parts described below, the fourth embodiment is similar to the first embodiment described above.
  • a blade 108c according to the fourth embodiment is roughly divided into three regions along a width in a longitudinal direction of the blade 108c. Those three regions include blade ring near portions 8ca arranged on both the end portion sides adjacent to the rings 8b under a state in which the rings 8b are mounted to the impeller, a blade central portion 8cb arranged at a central portion of the blade, and blade intermediate portions 8cc arranged between the blade ring near portions 8ca and the blade central portion 8cb.
  • the blade ring near portions 8ca are also referred to as first regions
  • the blade central portion 8cb is also referred to as a second region
  • the blade intermediate portions 8cc are also referred to as third regions.
  • coupling portions 8g that are curved in conformity with a concave shape of the blade 108c are formed as first coupling portions.
  • the first regions and the third regions are connected to each other with the coupling portions 8g.
  • coupling portions 8g that are curved in conformity with the concave shape of the blade 108c are formed as second coupling portions.
  • the third regions and the second region are connected to each other with the coupling portions 8g.
  • the coupling portions 8g are each inclined from a region on one side toward a region on another side.
  • the coupling portions 8g are inclined not only in a transverse direction in conformity with the concave shape of the blade 108c, but also in the longitudinal direction.
  • the coupling portions 8g are inclined so that the third regions are arranged on a recessed side in the blade rotation direction with respect to the first regions. In other words, the coupling portions 8g are inclined so that the third regions are located on the depth side in the drawing sheet with respect to the first regions. Further, the coupling portions 8g are inclined so that the third regions are arranged on the recessed side in the blade rotation direction with respect to the second region. In other words, the coupling portions 8g are inclined so that the third regions are located on the depth side in the drawing sheet with respect to the second region.
  • the components of the blade 108c are sequentially arranged along its longitudinal direction as described below.
  • the blade 108c includes the components in the following order, that is, the ring 8b serving as a support plate on one side, the blade ring near portion 8ca on the one side, the coupling portion 8g, the blade intermediate portion 8cc on the one side, the coupling portion 8g, the blade central portion 8cb, the coupling portion 8g, the blade intermediate portion 8cc on another side, the coupling portion 8g, the blade ring near portion 8ca on the another side, and the ring 8b serving as a support plate on the another side.
  • the blade 108c includes the five regions and the four coupling portions 8g between the rings 8b on both the end portion sides.
  • the blade ring near portions 8ca, the blade central portion 8cb, and the blade intermediate portions 8cc of the blade 108c according to the fourth embodiment are formed into the same shape in the longitudinal direction respectively within regions having predetermined lengths WL1, WL2, and WL3.
  • the reference symbol WL4 represents a blade length in each of the coupling portions.
  • the blade ring near portions 8ca, the blade central portion 8cb, and the blade intermediate portions 8cc are substantially equal to each other in outer diameters Ro of straight lines O-P1 connecting the impeller rotation center O and the circular-arc centers P1 of the outer peripheral-side end portions 15a in the circular-arc shape of the blade 108c.
  • a diameter of a circumscribed circle of all the blades that is, a radius of an effective impeller outer diameter is substantially uniform over the longitudinal direction.
  • values of the outer diameters Ro in the vertical cross-sections are substantially equal to each other.
  • the blade 108c according to the fourth embodiment is formed so that, in each of the blade cross-sections that are orthogonal to the impeller rotation axis of the cross-flow fan 8, an outer diameter corresponding to a line segment connecting the impeller rotation axis and the outer peripheral-side end portion 15a of the blade 108c to each other is substantially uniform from the one end portion side to the another end portion side in the longitudinal direction corresponding to the direction of the impeller rotation axis.
  • the outer diameter of the outer peripheral-side end portion 15a of the blade 108c is substantially uniform in the blade sectional views that are orthogonal to the impeller rotation axis.
  • leakage of the air stream around the stabilizer for partitioning an air inlet region and an air outlet region of the impeller from each other can be suppressed. As a result, higher efficiency can be achieved.
  • an outer part of the camber line Sb with respect to a predetermined radius R03 from the impeller rotation center O can be defined as an outer peripheral-side camber line S1a
  • an inner part of the camber line with respect to the predetermined radius R03 from the impeller rotation center O can be defined as an inner peripheral-side camber line Sa2.
  • a single tangent line that is tangent to a circle formed around the impeller rotation center O and passes through the circular-arc center P1 of the outer peripheral-side end portion 15a of the blade 108c can be drawn at the circular-arc center P1.
  • the blade outlet angle refers to a narrow angle formed between this tangent line and the outer peripheral-side camber line S1a.
  • a blade outlet angle defined in each of the first regions is represented by ⁇ b1
  • a blade outlet angle defined in the second region is represented by ⁇ b2
  • a blade outlet angle defined in each of the third regions is represented by ⁇ b3.
  • the first regions (blade ring near portions 8ca), the second region (blade central portion 8cb), and the third regions (blade intermediate portions 8cc between the blade ring near portions 8ca and the blade central port ion 8cb) are different from each other in blade outlet angle.
  • values of the blade outlet angles ⁇ b1, the blade outlet angle ⁇ b2, and the blade outlet angles ⁇ b3 are set unequal to each other.
  • an outer peripheral side of the blade central portion 8cb be shaped more forward in the impeller rotation direction RO than any other regions, and that, in contrast, an outer peripheral side of each of the blade intermediate portions 8cc be rearmost.
  • the outer peripheral-side end portion 15a has a blade cross-sectional shape that is recessed most toward a reverse side in the rotation direction in each of the third regions, and is foremost in the rotation direction in the second region. More specifically, it is preferred that the blade outlet angle ⁇ b1, the blade outlet angle ⁇ b2, and the blade outlet angle ⁇ b3 satisfy the relationship of ⁇ b2 ⁇ b1 ⁇ b3.
  • an angle formed between a straight line passing through the impeller rotation center O and the circular-arc center P2 of the inner peripheral-side end portion 15b of the blade 108c and the straight line passing through the impeller rotation center O and the circular-arc center P1 of the outer peripheral-side end portion 15a of the blade 108c is defined as a forward angle.
  • a forward angle defined in each of the first regions is represented by ⁇ 1
  • a forward angle defined in the second region is represented by ⁇ 2
  • a forward angle defined in each of the third regions is represented by ⁇ 3.
  • ⁇ b2 ⁇ b1 ⁇ b3 which is satisfied between the above-mentioned blade outlet angles ⁇ b, may be expressed as ⁇ 3 ⁇ 1 ⁇ 2 by using a forward angle ⁇ instead of the blade outlet angle ⁇ b.
  • the blade 108c is divided into a plurality of regions in the longitudinal direction between the pair of support plates, specifically, divided into the first regions at both the end portions adjacent to the support plates under the state in which the support plates are mounted to the impeller, the second region at the blade central portion, and the third regions located on both sides of the blade central portion between the first regions and the second region.
  • the blade outlet angles and the forward angles are set to appropriate values unequal to each other in the respective regions so that separation of the air stream can be suppressed to reduce noise.
  • the air velocity in each of the impeller elements is distributed in a height direction of the air outlet so as to be relatively higher in the blade central portion 8cb and relatively lower in the blade ring near portions 8ca due to influence of friction loss on surfaces of the rings 8b.
  • the air velocity distribution is equalized.
  • the blade central portion 8cb is formed at the smallest blade outlet angle ⁇ b2 (largest blade forward angle), and is projected forward in the blade rotation direction RO so that the distances between the blades are small.
  • the air streams can be suppressed frombeing excessively biased in the central portion in the longitudinal direction between the rings.
  • the blade intermediate portions 8cc are each formed at the largest blade outlet angle ⁇ b3 (smallest blade forward angle).
  • the air is blown out relatively in a radial direction in comparison with the other regions (first regions and second region).
  • the distances between the adjacent blades in the blade rotation direction RO (circumferential direction) are increased. With this, the air velocity can be reduced.
  • the ring near portions 8ca in which the air streams flow at a low velocity, are each formed at the small blade outlet angle ⁇ b1 (large forward angle) to reduce the distance between the blades.
  • the turbulence is not suppressed by forming a corrugated pattern gradually curved along the longitudinal direction at the outer peripheral-side end portion so that the air stream is diffused at the outer peripheral-side end portion.
  • the regions are formed into rectangular shapes that respectively have predetermined uniform widths and the different blade outlet angles ⁇ b so that the blade varies in shape, to thereby adjust a blow-out direction of the impeller over the longitudinal direction. With this, the air velocity distribution toward the air outlet on a downstream side is equalized.
  • the five regions different from each other in blade outlet angle are connected to each other not with substantially perpendicular steps but with the coupling portions 8g each forming an inclined surface.
  • the air stream is not abruptly diverted on the blade surface, and hence turbulence due to the steps does not occur.
  • the air velocity distribution is equalized in the flow direction, and hence locally-high air velocity regions are eliminated.
  • the load torque is reduced, and hence electric power consumption of the motor can be reduced.
  • a locally-high velocity air stream does not impinge also on the airflow direction vanes arranged on the downstream side. With this, airflow resistance is reduced, and hence the load torque can be further reduced.
  • the velocity of the air into the airflow direction vanes is equalized, and hence locally-high velocity regions are eliminated. With this, noise to be caused by turbulence in boundary layers between surfaces of the airflow direction vanes can also be reduced.
  • the blade is formed so that, in each of the first, second, and third regions, the straight portion having a substantially uniform thickness and a flat surface is formed on the inner peripheral-side end portion 15b side, that the blade cross-sectional shape on the outer peripheral side varies over the longitudinal direction of the impeller, and that the blade cross-sectional shape of the straight portion is uniform over the longitudinal direction of the impeller.
  • negative pressure is generated on the flat surface Qs.
  • the flat surface Qs is flat, and hence the blade thickness t is not abruptly increased toward the impeller outer periphery in comparison with the case of a curved surface. With this, frictional resistance can be suppressed.
  • the portion having the uniform shape is formed along the impeller axis direction.
  • the fourth embodiment has a feature in that the blade, which provides the advantageous effect as described above, further includes the step 16.
  • the step 16 is formed in a vicinity of a boundary between an inner peripheral-side part in which the three patterns of the first regions, the second region, and the third regions in the blade cross-section have the same shape, and an outer peripheral-side part in which the three patterns of the first regions, the second region, and the third regions in the blade cross-section have different shapes.
  • the step 16 is formed along the step base line 16a that is inclined at the predetermined angle ⁇ with respect to the straight line O1 parallel to the impeller rotation axis O so that the step height is gradually increased in the direction in which the step base line 16a is separated from the blade outer peripheral-side end portion 15a.
  • the step 16 is formed in this way, advantages as described below can be obtained. Particularly under a state in which airflow resistance is increased by dust accumulated on the filter, in each rotation of the fan, the air velocity distribution is significantly changed on the fan air inlet side. Thus, even when the blade outlet angle is changed in the longitudinal direction, separation may occur on the blade surfaces.
  • the step 16 is formed in the fourth embodiment. With this, even when the separation occurs on the suction surface, the air stream is re-adhered to the blade surface. Meanwhile, on the pressure surface, the step causes the air stream to be forced out onto the adjacent suction surface, to thereby suppress the separation. With this, the effective flow passage width between the blades is secured.
  • the step 16 when the air stream is almost separated after passing along the inner peripheral-side end portion 15b of the blade, the step 16 generates negative pressure to cause the air stream to flow along the blade surface.
  • the outer peripheral-side end portion 15a at which different blade outlet angles are formed, causes the air stream to be spread over the rotation direction of the fan.
  • the air stream is diffused over the entire air outlet, and hence further suppressed from being drifted.
  • load torque is reduced.
  • electric power consumption of the fan motor is reduced.
  • an indoor unit for an air-conditioning apparatus with high energy efficiency can be provided.
  • the above description of the fourth embodiment is made on the premise that the step 16 described in the first embodiment is provided, but the fourth embodiment may be carried out by providing, instead of such a step 16, the step described above in the second embodiment or the step described above in the third embodiment.
  • the step is formed on both the pressure surface and the suction surface, but the present invention may be carried out in such an embodiment that the step described above is formed on at least one of the pressure surface or the suction surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
EP14816588.9A 2013-06-28 2014-06-25 Innenraumeinheit für eine klimaanlagenvorrichtung Not-in-force EP3015775B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP2013/067849 WO2014207908A1 (ja) 2013-06-28 2013-06-28 空気調和装置の室内機
PCT/JP2014/066863 WO2014208608A1 (ja) 2013-06-28 2014-06-25 空気調和装置の室内機

Publications (3)

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EP3015775A1 true EP3015775A1 (de) 2016-05-04
EP3015775A4 EP3015775A4 (de) 2017-02-22
EP3015775B1 EP3015775B1 (de) 2018-06-13

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JP6625213B2 (ja) * 2016-06-27 2019-12-25 三菱電機株式会社 多翼ファン及び空気調和機
JP7524776B2 (ja) 2021-01-26 2024-07-30 株式会社富士通ゼネラル 多翼ファン及び室内機

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JPS6023650U (ja) * 1983-07-25 1985-02-18 株式会社東芝 空気調和機
JPH0587295U (ja) * 1991-09-05 1993-11-26 三光合成株式会社 筒状羽根車
ITVI20030176A1 (it) * 2003-09-17 2005-03-18 Bei Gianluca De Climatizzatore
JP3995010B2 (ja) 2005-09-28 2007-10-24 ダイキン工業株式会社 多翼送風機の羽根車及びその製造方法
US8256241B2 (en) * 2007-03-14 2012-09-04 Mitsubishi Electric Corporation Air conditioner
JP4840343B2 (ja) 2007-11-30 2011-12-21 三菱電機株式会社 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
JP4993791B2 (ja) * 2010-06-28 2012-08-08 シャープ株式会社 ファン、成型用金型および流体送り装置

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Title
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EP3015775A4 (de) 2017-02-22
JP6000454B2 (ja) 2016-09-28
WO2014208608A1 (ja) 2014-12-31
JPWO2014208608A1 (ja) 2017-02-23
EP3015775B1 (de) 2018-06-13
WO2014207908A1 (ja) 2014-12-31

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