WO2015063850A1 - Ventilateur tangentiel et climatiseur - Google Patents

Ventilateur tangentiel et climatiseur Download PDF

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Publication number
WO2015063850A1
WO2015063850A1 PCT/JP2013/079215 JP2013079215W WO2015063850A1 WO 2015063850 A1 WO2015063850 A1 WO 2015063850A1 JP 2013079215 W JP2013079215 W JP 2013079215W WO 2015063850 A1 WO2015063850 A1 WO 2015063850A1
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WO
WIPO (PCT)
Prior art keywords
blade
cross
impeller
blades
rotation axis
Prior art date
Application number
PCT/JP2013/079215
Other languages
English (en)
Japanese (ja)
Inventor
池田　尚史
平川　誠司
代田　光宏
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2013/079215 priority Critical patent/WO2015063850A1/fr
Priority to JP2015545256A priority patent/JPWO2015064617A1/ja
Priority to EP14859194.4A priority patent/EP3064777A4/fr
Priority to PCT/JP2014/078719 priority patent/WO2015064617A1/fr
Publication of WO2015063850A1 publication Critical patent/WO2015063850A1/fr

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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
    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the present invention relates to a cross-flow fan and an air conditioner using the cross-flow fan.
  • Patent Document 1 discloses a cross-flow fan in which each blade is inclined at a predetermined angle with respect to the fan shaft, and the blade mounting pitch is set at unequal intervals.
  • the blades are thin in the longitudinal direction of the impeller.
  • Patent Document 2 discloses an axial fan in which a blade cross section orthogonal to a rotation axis is formed so as to become smaller from a root portion of a blade portion continuously provided on a main surface toward a tip portion. Further, in such an axial fan, the center of the blade cross section orthogonal to the rotation axis is displaced toward the front side or the rear side in the rotation direction about the rotation axis as it goes from the root part of the blade part toward the tip part. Further, the blade cross section is curved outward in the radial direction.
  • Patent Document 3 discloses a fan configured by alternately stacking first component parts in which the blade tip is inclined in the rotation direction from the root and second component parts in the counter-rotation direction. Is disclosed.
  • the present invention has been made in view of the above, and an object of the present invention is to provide a cross-flow fan that can suitably disperse a flow in the direction of the rotation axis as viewed in the entire fan.
  • 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 wings arranged at intervals in the circumferential direction between the pair of support plates, and each of the plurality of wings has an outer diameter and an inner diameter between the corresponding pair of support plates in the rotation axis direction. It has at least one region that is the same and is advanced or retracted with respect to the rotational direction. Further, each of the plurality of blades may have at least two different blade exit angles between a pair of corresponding support plates.
  • each of the plurality of blades has the same outer diameter and inner diameter in the direction of the rotation axis between the corresponding pair of the support plates, and has the same cross-sectional shape and blade exit angle over the rotation axis direction, and the rotation axis. You may comprise so that it may have two or more area
  • each of the plurality of blades is formed symmetrically about a central cross-section, and in order in a direction away from the central cross-section, a pair of blade-ring center portions 8cb, a pair of blade-to-blade portions 8cc,
  • the plurality of blades include a blade exit angle ⁇ b2 and a blade inclination deviation angle ⁇ 2 at the center between the blade rings, and a blade exit angle ⁇ b3 and a blade inclination at the inter-blade portion, respectively.
  • 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. 1 It is a figure which shows the installation state when it sees from the room regarding the air conditioner which shows Embodiment 1 of this invention. It is a longitudinal cross-sectional view of the air conditioner of FIG. It is a figure which shows the front and side of the impeller of a once-through fan mounted in the air conditioner of FIG. It is the perspective view seen from the impeller rotation direction side surface (blade pressure surface) regarding one blade of the impeller of the once-through fan. It is a figure which shows the whole wing
  • FIG. 4 is a diagram for explaining a blade shape of a cross section taken along line AA in FIG. 3.
  • FIG. 4 is a diagram for explaining a blade shape of a cross section taken along line AA in FIG. 3.
  • FIG. 4 is a diagram for explaining a blade shape of a cross section taken along line AA in FIG. 3.
  • FIG. 4 is a diagram for explaining a blade shape of a cross section taken along line AA in FIG. 3.
  • 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. It is a figure which shows the front and side of the impeller of a once-through fan mounted in the air conditioner of FIG.
  • 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. And 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. .
  • AS resin Styrene-AcryloNitrile copolymer
  • 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 perpendicular to the side surface, and the plurality of blades 8c are connected to the ring 8b.
  • the impeller 8a is formed by welding a plurality of such impellers 8d and connecting them together.
  • 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. 4 is a perspective view of one blade of the cross-flow fan as viewed from the impeller rotation direction side surface (blade pressure surface).
  • FIG. 5 is a diagram showing the entire blade in a projected manner from the direction of the rotation axis.
  • R01 is the blade inner diameter
  • R02 is the blade outer diameter
  • ⁇ represents the forward tilt angle in the blade rotation axis direction.
  • the blade 8c is formed symmetrically about the central cross section 51.
  • the central cross section 51 is a portion with a cross section located at the center of the blade 8c in the rotational axis direction among the cross sections orthogonal to the rotational axis direction.
  • the wings 8c are sequentially arranged in a direction away from the central cross section 51, a pair of wing-ring center portions 8cb, a pair of center side connection portions 8ce, a pair of blade-to-blade portions 8cc, a pair of end side connection portions 8cd, and a pair of wings. It has a ring vicinity 8ca. Further, in FIG. 4, the cross-sectional portions 53, 55, 57, and 59 are illustrated for convenience.
  • the cross-sectional portion 53 forms a boundary between the blade ring vicinity portion 8ca and the end-side connecting portion 8cd
  • the cross-sectional portion 55 forms a boundary between the end-side connecting portion 8cd and the inter-blade portion 8cc
  • the part 57 forms a boundary between the inter-blade part 8cc and the central side connection part 8ce
  • the cross-sectional part 59 forms a boundary between the central side connection part 8ce and the central part 8cb between the blade rings.
  • FIG. 6 is a view showing the blade ring vicinity portion 8ca of the blade in a projected manner from the direction of the rotation axis.
  • the blade ring vicinity portion 8ca recedes in the rotation direction as it approaches the rotation axis direction central portion (central cross section 51).
  • the blade ring vicinity portion 8ca has a constant blade inclination deviation angle (a straight line contacting the outer peripheral end portion and the inner peripheral end portion of the blade, an arc center of the blade inner peripheral end portion, and an impeller rotational axis center point O).
  • FIG. 7 is a diagram showing the end side connecting portion 8cd in the blade in a projected manner from the direction of the rotation axis.
  • the end-side connecting portion 8cd is retracted in the rotational direction as it approaches the central portion in the rotational axis direction.
  • the blade inclination deviation angle ⁇ 3 of the cross section 55 is smaller than the blade inclination deviation angle ⁇ 1 of the cross section 53, and the blade outlet angle ⁇ b3 of the cross section 55 is larger than the blade outlet angle ⁇ b1 of the cross section 53.
  • the blade inclination angle becomes smaller and the blade outlet angle becomes larger toward the central portion in the rotation axis direction.
  • FIG. 8 is a diagram showing the inter-blade portion 8 cc of the wing in a projected manner from the direction of the rotation axis. As shown in FIGS. 4 and 8, the inter-blade portion 8 cc is retracted in the rotational direction as it approaches the central portion in the rotational axis direction. Further, the inter-blade portion 8cc has a constant blade inclination angle ⁇ 3 and a constant blade outlet angle ⁇ b3.
  • FIG. 9 is a diagram showing the center side connecting portion 8ce in the wing in a projected manner from the direction of the rotation axis. As shown in FIG. 4 and FIG. 9, most of the center side connecting portion 8ce except the portion on the outer peripheral side end portion 15a recedes in the rotation direction as it approaches the center portion in the rotation axis direction. Further, the blade inclination deviation angle ⁇ 2 of the cross section 59 is larger than the blade inclination deviation angle ⁇ 3 of the cross section 57, and the blade outlet angle ⁇ b2 of the cross section 59 is smaller than the blade outlet angle ⁇ b3 of the cross section 57.
  • the blade inclination angle becomes larger and the blade outlet angle becomes smaller toward the central portion in the rotation axis direction.
  • the blade inclination deviation angle ⁇ 2 of the cross section 59 is larger than the blade inclination deviation angle ⁇ 1 of the cross section 53, and the blade outlet angle ⁇ b2 of the cross section 59 is smaller than the blade outlet angle ⁇ b1 of the cross section 53.
  • FIG. 10 is a diagram projectively showing the center part 8cb between the blade rings in the blade from the direction of the rotation axis.
  • the inter-blade ring central portion 8 cb is retracted in the rotational direction as it approaches the central portion in the rotational axis direction.
  • the inter-blade ring central portion 8cb has a constant blade inclination angle ⁇ 2 and a constant blade outlet angle ⁇ b2.
  • the blade 8c has the same outer diameter and inner diameter in the direction of the rotation axis, the same cross-sectional shape and blade exit angle over the rotation axis direction, and the rotation axis direction.
  • the blade 8c has at least two different blade exit angles between a pair of rings. More specifically, the blade 8c is formed so that the blade outlet angle ⁇ b2 ⁇ b1 ⁇ b3 and the blade inclination angle ⁇ 3 ⁇ 1 ⁇ 2.
  • the inner peripheral end 15b of the blade 8c includes a shape that retreats in the rotation direction from one corresponding ring to the other corresponding ring, and then advances in the rotation direction again
  • the outer peripheral side end portion 15a also includes a shape that retreats in the rotation direction from the corresponding one ring toward the other corresponding ring and then advances again in the rotation direction.
  • the plurality of blades 8c each have an inner end 15b and an outer end 15a that are upside down V-shaped. It has a shape.
  • the blades are located on the outer side (side away from the central cross-section portion 51) of each of the pair of blade ring vicinity portions 8ca, the positions of the inner peripheral side end portion 15b and the outer peripheral side end portion 15a, and the blade exit angle.
  • a portion extending while maintaining the blade inclination deviation angle in the rotation axis direction may be provided.
  • 11 to 13 are diagrams for explaining the blade shape of the cross section taken along the line AA of FIG.
  • the outer peripheral end 15a and the inner peripheral 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 (rotary axis) O of the impeller 8a toward the outside of the blade 8c. Curved in the vehicle rotation direction RO.
  • 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 (blade chord) L
  • the chord line L has a length Lo as shown in FIG. 13 (hereinafter also referred to as a 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. 12, the surface of the blade 8c on the blade pressure surface 13a side 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 (thickness) t When the diameter of a circle inscribed in the blade surface when the blade 8c is viewed in a longitudinal section is the blade thickness (thickness) t, as shown in FIG. 12, 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. Correspond.
  • 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.
  • each of the plurality of blades 8c has the same outer diameter and inner diameter in the direction of the rotation axis between the corresponding pair of rings, and has the same cross-sectional shape and blade exit angle over the rotation axis direction, and the rotation axis.
  • each blade has at least one region that is advanced or retracted relative to the direction of rotation over the direction, and at least two different blade exit angles. For this reason, unlike the case where the outer peripheral side end of each blade is uniformly inclined from one ring toward the other ring, the blade is inclined and rotated in a plurality of modes in the direction of the rotation axis for each blade. Since a flow inclined in a plurality of directions in the direction is repeatedly blown out one after another, the flow is blown out uniformly between the pair of rings, and a very uniform blowout distribution is obtained as a continuous flow state accompanying the rotation of the cross-flow fan. be able to. Even when viewed in the direction of the rotation axis, the entire fan can flow and be suitably dispersed.
  • the air flows through the inner peripheral side end 15b, the air flows along the blade 8c as a flow in which separation is suppressed with a blade tip vortex having the inner peripheral side end 15b as an end. Therefore, by suppressing the separation, the blowout at the outer peripheral side end portion 15a is suitably maintained, and the flow dispersion is also promoted by this.
  • the negative pressure 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 flow of the blade surface when the blade 8c passes through the suction side air passage E1. Is peeled off at the outer peripheral curved surface Bs1, the flow is reattached by the inner peripheral curved surface Bs2 having a different arc radius.
  • 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 pressure surface 13a of the blade 8c is also formed by multiple arcs and straight portions (planes) from the outer peripheral side to the inner peripheral side of the impeller. For this reason, when the air flows from the outer peripheral curved surface Bp1 to the inner peripheral curved surface Bp2 having a different arc radius, the flow is gradually accelerated and a pressure gradient is generated on the negative pressure surface 13b. do not do.
  • 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 thickness t2 of the inner peripheral side end portion 15b is thick, the flow can be directed to the suction surface 13b. The wake vortex when flowing into the impeller from the 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 after passing through the plane Qs, the blade thickness t gradually increases toward the center of the chord on the inner circumferential curved surface Bs2, and therefore the separation can be suppressed along the flow.
  • the blade 8c has the outer peripheral side curved surface Bs1 with different arc radii on the downstream side of the inner peripheral side curved surface Bs2, the separation of the flow is suppressed, and the effective blowing side air passage from the impeller can be expanded.
  • the blown wind speed can be reduced and made uniform, and the load torque applied to the blade surface can be reduced.
  • the blade exit angle differs between the blade ring side portion 8ca, the center portion 8cb between the blade rings, and the inter-blade portion 8cc, and the blade exit angles ⁇ b1, ⁇ b2, and ⁇ b3 are formed such that ⁇ b2 ⁇ b1 ⁇ b3. Therefore, the exit angle ⁇ b2 of the central portion 8cb between the blade rings protrudes forward in the blade rotation direction at a minimum. Therefore, the flow does not concentrate too much in the central portion in the longitudinal direction between the rings. Furthermore, in the inter-blade portion 8cc, the exit angle is the largest, and the air is blown relatively in the radial direction compared to other regions, and the wind speed is reduced by increasing the distance between the blades adjacent to each other in the rotational direction. it can. In the low-speed blade ring vicinity 8ca, by reducing the exit angle and reducing the distance between the blades, turbulence generation due to flow instability can be prevented, and the wind speed can be increased.
  • the blade inclination deviation angle ⁇ differs between the blade ring side portion 8ca, the center portion 8cb between the blade rings, and the interblade portion 8cc, and the blade inclination deviation angles ⁇ 1, ⁇ 2, and ⁇ 3 are ⁇ 3 ⁇ 1 ⁇ 2. Therefore, the blade inclination deviation angle ⁇ 2 of the center portion 8cb between the blade rings protrudes forward in the rotational direction, and the flow does not concentrate too much at the center portion in the longitudinal direction between the rings.
  • the blade inclination deviation angle ⁇ 3 is the smallest, the air is blown relatively in the radial direction as compared with other regions, and the wind speed can be reduced by increasing the distance between the blades adjacent to each other in the rotation direction. Further, the low-speed blade ring side portion 8ca can prevent the generation of turbulence due to the instability of the flow and increase the wind speed by reducing the blade inclination deviation angle ⁇ 1 and reducing the inter-blade distance.
  • the blade 8c has the same blade cross section orthogonal to the impeller rotation axis, and the central portion between the blade rings in the impeller rotation direction with respect to the impeller rotation direction.
  • the clearance with the stabilizer 9 facing the impeller is the same, and the leakage flow caused by the circulating vortex g1 is increased due to the difference in the longitudinal direction, which was a problem in the conventional configuration. Therefore, the efficiency can be increased and the motor power to be driven can be reduced.
  • the blade since the blade has a region where the blade is retracted with respect to the impeller rotation direction and the blade end portion is inclined with respect to the impeller rotation axis, when the blade passes around the stabilizer 9 facing the impeller, the blade Since it is dispersed without being subjected to pressure fluctuations in the entire region of the blade tip in the longitudinal direction of the vehicle, an annoying rotational sound (NZ sound) resulting from the rotational speed and the number of blades can be reduced, and noise can be reduced. 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 indoor unit 100 equipped with the quiet and energy-saving once-through fan 8 can be obtained.
  • FIG. 14 is a view of the same aspect as FIG. 3 relating to the second embodiment of the present invention
  • FIG. 15 is a view for explaining a blade shape of a cross section taken along line BB of FIG.
  • the configuration of the second embodiment is the same as that of the first embodiment described above except for the parts described below.
  • each of the plurality of blades 108c has the same outer diameter and inner diameter in the rotation axis direction, and only the region where the pair of rings are moving forward or backward in the rotation direction. Consists of. One ring-side wing portion and the other ring-side wing portion are offset by an angle ⁇ .
  • FIG. 16 is a diagram of the same mode as FIG. 3 relating to the third embodiment of the present invention
  • FIG. 17 is a diagram of the same mode as FIG. 4 relating to the third embodiment of the present invention
  • FIG. It is a figure explaining the wing
  • the configuration of the third embodiment is the same as that of the first embodiment described above except for the portions described below.
  • each of the plurality of blades 208c has an outer diameter and an inner diameter that are the same in the rotation axis direction, and only a region where the pair of rings are moving forward with respect to the rotation direction or a region that is moving backward And a pair of ring-side portions 220 that are located on both sides of the region and extend along the rotation axis direction without moving forward or backward in the rotation direction.
  • One ring side portion and the other ring side portion are shifted by an angle ⁇ .
  • the above-described first embodiment can be implemented by using a wing configured in a V shape instead of an upside down V shape by reversing the advancing and retreating relationship of each part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne un ventilateur tangentiel (8) comprenant une turbine (8a) et un arbre supportant rotatif la turbine (8a). La turbine (8a) du ventilateur tangentiel (8) comporte une pluralité de plaques de support (8b) et une pluralité de pales (8c) agencées à des intervalles dans la direction périphérique entre des paires de plaques de support (8b). Chaque pale parmi la pluralité de pales (8c) présente le même diamètre externe et diamètre interne à travers la direction d'axe de rotation entre des paires de plaques de support (8b), et comporte au moins une zone dans laquelle celles-ci avancent ou reculent par rapport à la direction de rotation.
PCT/JP2013/079215 2013-10-29 2013-10-29 Ventilateur tangentiel et climatiseur WO2015063850A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2013/079215 WO2015063850A1 (fr) 2013-10-29 2013-10-29 Ventilateur tangentiel et climatiseur
JP2015545256A JPWO2015064617A1 (ja) 2013-10-29 2014-10-29 貫流ファン及び空気調和機
EP14859194.4A EP3064777A4 (fr) 2013-10-29 2014-10-29 Ventilateur à flux transversal et climatiseur
PCT/JP2014/078719 WO2015064617A1 (fr) 2013-10-29 2014-10-29 Ventilateur à flux transversal et climatiseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/079215 WO2015063850A1 (fr) 2013-10-29 2013-10-29 Ventilateur tangentiel et climatiseur

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WO2015063850A1 true WO2015063850A1 (fr) 2015-05-07

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PCT/JP2014/078719 WO2015064617A1 (fr) 2013-10-29 2014-10-29 Ventilateur à flux transversal et climatiseur

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PCT/JP2014/078719 WO2015064617A1 (fr) 2013-10-29 2014-10-29 Ventilateur à flux transversal et climatiseur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108194386A (zh) * 2018-02-07 2018-06-22 广东纽恩泰新能源科技发展有限公司 一种贯流式风机
CN108758825A (zh) * 2018-07-27 2018-11-06 青岛海尔空调器有限总公司 壁挂式空调室内机

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JPS61144294U (fr) * 1985-02-28 1986-09-05
JPH09250493A (ja) * 1996-03-12 1997-09-22 Hitachi Ltd 貫流ファン
US20090104017A1 (en) * 2007-10-23 2009-04-23 Park Jeong Taek Cross-flow fan and air conditioner
JP2011122522A (ja) * 2009-12-10 2011-06-23 Mitsubishi Electric Corp 貫流ファン及びこれを備えた空気調和機
EP2345814A2 (fr) * 2010-01-13 2011-07-20 LG Electronics Inc. Ventilateur à flux croisé et climatiseur doté de celui-ci
JP2012255628A (ja) * 2011-06-10 2012-12-27 Mitsubishi Electric Corp 空気調和機
WO2013150673A1 (fr) * 2012-04-06 2013-10-10 三菱電機株式会社 Unité interne de dispositif de conditionnement d'air

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JP3107711B2 (ja) 1994-08-09 2000-11-13 株式会社東芝 横流ファン
JPH09158890A (ja) 1995-12-08 1997-06-17 Fujitsu General Ltd 空気調和機
CN1603631A (zh) * 2004-10-29 2005-04-06 吴劲松 斜式干涉降噪型离心风机
JP4549416B2 (ja) 2008-10-22 2010-09-22 シャープ株式会社 貫流ファン、送風機および羽根車の成形機

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Publication number Priority date Publication date Assignee Title
JPS61144294U (fr) * 1985-02-28 1986-09-05
JPH09250493A (ja) * 1996-03-12 1997-09-22 Hitachi Ltd 貫流ファン
US20090104017A1 (en) * 2007-10-23 2009-04-23 Park Jeong Taek Cross-flow fan and air conditioner
JP2011122522A (ja) * 2009-12-10 2011-06-23 Mitsubishi Electric Corp 貫流ファン及びこれを備えた空気調和機
EP2345814A2 (fr) * 2010-01-13 2011-07-20 LG Electronics Inc. Ventilateur à flux croisé et climatiseur doté de celui-ci
JP2012255628A (ja) * 2011-06-10 2012-12-27 Mitsubishi Electric Corp 空気調和機
WO2013150673A1 (fr) * 2012-04-06 2013-10-10 三菱電機株式会社 Unité interne de dispositif de conditionnement d'air

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108194386A (zh) * 2018-02-07 2018-06-22 广东纽恩泰新能源科技发展有限公司 一种贯流式风机
CN108758825A (zh) * 2018-07-27 2018-11-06 青岛海尔空调器有限总公司 壁挂式空调室内机

Also Published As

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WO2015064617A1 (fr) 2015-05-07
JPWO2015064617A1 (ja) 2017-03-09
EP3064777A4 (fr) 2017-07-19
EP3064777A1 (fr) 2016-09-07

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