WO2013099182A1 - Climatiseur - Google Patents

Climatiseur Download PDF

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Publication number
WO2013099182A1
WO2013099182A1 PCT/JP2012/008185 JP2012008185W WO2013099182A1 WO 2013099182 A1 WO2013099182 A1 WO 2013099182A1 JP 2012008185 W JP2012008185 W JP 2012008185W WO 2013099182 A1 WO2013099182 A1 WO 2013099182A1
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WO
WIPO (PCT)
Prior art keywords
impeller
outer peripheral
peripheral surface
motor
airflow
Prior art date
Application number
PCT/JP2012/008185
Other languages
English (en)
Japanese (ja)
Inventor
竜佑 太田黒
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2013099182A1 publication Critical patent/WO2013099182A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • 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
    • F04D17/06—Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • F24F2013/205—Mounting a ventilator fan therein

Definitions

  • the present invention relates to an air conditioner equipped with a mixed flow type or centrifugal type impeller.
  • centrifugal blowers and mixed flow blowers have been used in air conditioners.
  • the centrifugal blower has a centrifugal impeller, and has a structure in which air sucked into the impeller in the axial direction is blown away in a direction away from the rotation shaft (centrifugal direction).
  • the mixed flow blower has a mixed flow type impeller, and has a structure in which air sucked into the impeller in the axial direction is blown in a direction inclined with respect to the centrifugal direction.
  • Patent Document 1 discloses a ceiling-embedded air conditioner having a mixed flow impeller.
  • the top plate of the housing is formed so as to smoothly introduce the airflow blown from the mixed flow impeller into the guide path, and the ceiling-embedded air with high efficiency and low noise. It is described that a harmony machine can be provided.
  • a heat exchanger is provided so as to surround the entire periphery of the impeller, and the airflow blown from the impeller smoothly flows through the heat exchanger provided around the impeller. Then, the air is supplied into the room through the air outlet of the case.
  • the airflow blown out from the impeller toward the area where the heat exchanger is provided blows through the heat exchanger smoothly and then enters the room through the outlet of the case. Supplied.
  • the airflow blown out from the impeller toward the area where no heat exchanger is provided is bounced back on the inner surface of the side plate adjacent to the impeller, and then the hub supporting the impeller and the back supporting the motor. It flows into the narrow gap between the plates vigorously.
  • Such a vortex tends to stay while swirling in and around the gap.
  • the vortex flow interferes with the air flow (main flow) blown out from the impeller, disturbs the main flow, and reduces the resistance when the main flow flows by narrowing the width of the main flow passage (effective flow passage) in the case. Increase.
  • the noise of the air conditioner further increases.
  • An object of the present invention is to suppress an increase in noise while reducing the size of an air conditioner in which a heat exchanger is provided around a part of an impeller.
  • the air conditioner of the present invention includes a case having a front plate and a back plate facing each other, a heat exchanger provided in the case, a back plate supported by the back plate, and a rotation axis intersecting the back plate.
  • the impeller is surrounded by a plurality of inner wall surfaces located on the radially outer side of the impeller, and the plurality of inner wall surfaces include a first inner wall surface and a second inner wall surface. .
  • the heat exchanger is interposed between the first inner wall surface and the impeller.
  • the heat exchanger is not interposed between the second inner wall surface and the impeller.
  • the distance between the second inner wall surface and the impeller is shorter than the distance between the first inner wall surface and the impeller.
  • the airflow guide portion has an outer peripheral surface, and the outer peripheral surface is between the back plate and the hub and between the motor and at least the second inner wall surface along the rotational direction of the impeller.
  • the outer peripheral surface is inclined or curved so that the distance from the rotating shaft becomes smaller toward the front plate.
  • FIG. 3 is a sectional view taken along line III-III in FIG. 1.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 2. It is an axial sectional view showing a blower in the air conditioner.
  • A) is a perspective view which shows the positional relationship of the case in the said air conditioner, a motor, and an airflow guide part
  • B) is a perspective view which shows the said airflow guide part.
  • (A) is a perspective view which shows the positional relationship of the hub of the impeller in the said air conditioner, a motor, and an airflow guide part, The cross section cut
  • (B) is an axial sectional view showing a part of the airflow guide and the back plate.
  • (A) is an axial sectional view showing Modification 1 of the airflow guide section
  • (B) is an axial sectional view showing Modification 2 of the airflow guide section
  • (D) is a front view which shows the modification 4 of the said airflow guide part schematically.
  • (A) is the perspective view which shows roughly the flow of the air which blows off from an impeller and flows in into the space between a hub and a back board in the said air conditioner
  • (B) is the flow of the said air
  • (C) is an axial sectional view schematically showing the air flow. It is a perspective view which shows the positional relationship of the hub of the impeller, the motor, and fixing member in the air conditioner of the modification 5. The cross section cut
  • (A) is a top view which shows roughly the positional relationship of the motor and fixing member in the air conditioner which concerns on the modification 5
  • (B) is the air conditioner which concerns on the modification 5, from an impeller.
  • FIG. 2C is an axial cross-sectional view schematically showing the air flow.
  • the indoor unit 11 of the present embodiment is arranged on a mixed flow or centrifugal impeller 51, a motor 49 that rotates the impeller 51, and both sides of the impeller 51.
  • a pair of heat exchangers 15 and 15, a drain pan 30 that stores condensed water generated in these heat exchangers 15 and 15, an airflow guide unit 90, and a case 20 that stores them are provided.
  • the impeller 51 and the motor 49 constitute the blower 13.
  • the airflow guide unit 90 guides an airflow that is blown out from the impeller 51 and flows into a space between the hub 53 and the back plate 26 described later. The structure of the airflow guide unit 90 will be described later.
  • the upper U, lower D, right R, left L, front F, and rear B of the indoor unit 11 are directions indicated by arrows in FIGS. 1 and 2.
  • the case 20 of the indoor unit 11 has a rectangular parallelepiped shape with a small thickness in the front-rear direction and a larger width in the left-right direction than the height in the vertical direction.
  • the indoor unit 11 has a blower 13 (a mixed flow blower or a centrifugal blower) disposed in the case 20 in a posture in which the axial direction of the rotation axis A of the motor 49 is directed in the front-rear direction, compared with a case where a cross flow fan is used. And thinned in the front-rear direction.
  • the indoor unit 11 is thinned in the front-rear direction by inclining the heat exchanger 15 with respect to the front-rear direction and placing it in the case 20.
  • the indoor unit 11 is downsized in the vertical direction by disposing the heat exchanger 15 on both sides of the blower 13 and not disposing the heat exchanger above and below the blower 13.
  • the air sucked from the front part of the case 20 flows in a direction inclined backward B (back plate 26 side) with respect to the centrifugal direction or the centrifugal direction of the impeller 51, and the right side R or the left side.
  • the air is blown into the room from both sides of the front surface of the case 20 (see FIG. 4).
  • the case 20 includes a bottom plate 21, a top plate 22, a right side plate 23, a left side plate 24, a front plate (front plate) 25, a back plate 26, and a bell mouth 28. is doing.
  • the front plate 25 includes a suction port opening / closing plate 251 and a pair of outlet opening / closing plates 252 and 252 arranged on both sides of the suction port opening / closing plate 251.
  • the suction port opening / closing plate 251 is disposed in front F of the impeller 51 and has a rectangular shape that occupies most of the area of the front plate 25.
  • the right outlet opening / closing plate 252 is disposed in front F of the right heat exchanger 15 and has a rectangular shape that is long in the vertical direction.
  • the left outlet opening / closing plate 252 is disposed in front F of the left heat exchanger 15 and has a rectangular shape that is long in the vertical direction.
  • the case 20 is provided with a pair of air outlets 25b for blowing the air in the case 20 into the room.
  • the pair of air outlets 25b are provided on the right side R and the left side L of the air inlet 25a in a front view, and are located behind the air outlet opening / closing plates 252 and 252.
  • the suction opening / closing plate 251 is supported by the bottom plate 21 and the top plate 22 via a support member (not shown) so as to be movable back and forth in the front-rear direction with respect to the bottom plate 21 and the top plate 22.
  • the suction opening / closing plate 251 is in a closed state in which the suction opening 25a is closed as shown by a solid line in FIG.
  • the suction port opening / closing plate 251 moves forward F as shown by a two-dot chain line in FIG.
  • the upper edge portion 251a, the lower edge portion 251b and the side edge portion of the inlet opening / closing plate 251 and the front edge portion 21a of the bottom plate 21, the front edge portion 22a of the top plate 22 and the outlet opening / closing plate 252 are used.
  • 252 are formed between the side edge portions, and air flows into the case 20 from these gaps.
  • the right outlet opening / closing plate 252 is supported by the front edge portion 21a of the bottom plate 21 and the front edge portion 22a of the top plate 22 so as to be rotatable around the left edge portion 252a.
  • the air outlet 25b is closed by the air outlet opening / closing plate 252 as shown by a solid line in FIG.
  • the air outlet opening / closing plate 252 rotates forward F around the left edge 252a, and the right edge 252b of the air outlet opening / closing plate 252 and the right edge 252b of the air outlet opening / closing plate 252 as shown in FIG.
  • a gap is formed between the front edge portion 23a of the right side plate 23, and the air in the case 20 flows into the room from this gap.
  • the operation of the left outlet opening / closing plate 252 is the same as this.
  • an inclined wall 26R (see FIG. 4) that is inclined so as to be positioned forward F toward the right R.
  • the right heat exchanger 15 is disposed so that the side portion thereof is adjacent to the inclined wall 26R.
  • an inclined wall 26 ⁇ / b> L (see FIG. 4) is provided that is inclined so as to be positioned forward F toward the left L.
  • the left heat exchanger 15 is arranged so that the side portion thereof is adjacent to the inclined wall 26L.
  • the bell mouth 28 has a suction port 25 a that opens circularly in the front-rear direction, is disposed between the front plate 25 and the impeller 51, and guides air to the impeller 51. To do.
  • the indoor unit 11 further includes a plate-shaped partition member 41 that partitions the air flow path from the impeller 51 to each heat exchanger 15 and the water storage space of the drain pan 30.
  • the partition member 41 is disposed below the impeller 51 in a posture parallel to the bottom plate 21.
  • the partition member 41 is bridged between the front wall 30F and the rear wall 30B of the drain pan 30.
  • the impeller 51 is surrounded by a plurality of inner wall surfaces S located on the radially outer side.
  • the plurality of inner wall surfaces S include a first inner wall surface S1 (right first inner wall surface S1) that is an inner surface of the right side plate 23, and a first inner wall surface S1 (left first inner wall surface S1) that is an inner surface of the left side plate 24.
  • the second inner wall surface S2 (upper second inner wall surface S2) that is the lower surface of the top plate 22 and the second inner wall surface S2 (lower second inner wall surface S2) that is the upper surface of the partition member 41 are included.
  • a right heat exchanger 15 is interposed between the right first inner wall surface S1 and the impeller 51, and a left heat exchanger 15 is interposed between the left first inner wall surface S1 and the impeller 51. is doing.
  • the heat exchanger 15 is not interposed between the upper second inner wall surface S2 and the impeller 51, and the heat exchanger 15 is interposed between the lower second inner wall surface S2 and the impeller 51. Not done.
  • the distance between the upper second inner wall surface S2 and the impeller 51 and the distance between the lower second inner wall surface S2 and the impeller 51 are the distance between the right first inner wall surface S1 and the impeller 51 and the left first inner wall surface S1. And closer to the impeller 51.
  • the blower 13 is a mixed flow blower including a mixed flow impeller 51.
  • the impeller 51 includes a circular hub 53 fixed to the motor 49 in front view, a shroud 54 having an opening into which the rear end of the bell mouth 28 is inserted (see FIG. 3), the shroud 54 and the hub 53. And a plurality of blades 55 arranged along the circumferential direction.
  • the motor 49 is an outer rotor type motor having a stator 43, a rotor 45, and a non-rotating shaft 80.
  • the motor 49 is fixed to the inner surface of the back plate 26 of the case 20, and as described above, the impeller 51 and the motor 49 have the axial direction of the rotation axis A in the front-rear direction (in this embodiment, the back plate 26 It is arranged in the case 20 in a posture facing in the direction perpendicular to the direction.
  • the stator 43 has a flat, generally cylindrical shape whose thickness in the front-rear direction is smaller than the diameter.
  • the stator 43 is disposed such that the back surface thereof faces the inner surface of the back plate 26 of the case 20.
  • a flange portion 48 extending outward in the radial direction is provided at the rear end portion of the stator 43.
  • the motor 49 is fixed to the back plate 26 by an airflow guide portion 90 to be described later attached to the flange portion 48.
  • a coil 44 is disposed inside the stator 43.
  • a through hole 46 penetrating in the front-rear direction is formed at the center of the stator 43.
  • the non-rotating shaft 80 is a columnar member extending in the direction of the rotating shaft A.
  • the non-rotating shaft 80 is supported by the stator 43 by arranging the rear B side portion (rear shaft portion) of the non-rotating shaft 80 in the through hole 46 of the stator 43.
  • a portion (front shaft portion) on the front F side of the non-rotating shaft 80 projects forward F from the stator 43.
  • the non-rotating shaft 80 is fixed to the stator 43 by a bolt B1.
  • the rotor 45 includes an annular fixed portion 45a having an insertion hole penetrating in the front-rear direction in the center, and a rotor main body 45b extending in a cylindrical shape from the periphery of the fixed portion 45a to the rear B.
  • the rotor 45 is fixed to the hub 53 in a state where the front surface of the fixing portion 45 a is in contact with the back surface of the hub 53 of the impeller 51.
  • the front shaft portion of the non-rotating shaft 80 is inserted through the insertion hole of the fixed portion 45a.
  • the rotor main body 45 b is arranged on the outer side in the radial direction of the stator 43 so as to cover the outer peripheral surface of the stator 43.
  • a predetermined gap is provided between the rotor 45 and the stator 43 so that they do not come into contact with each other when the rotor 45 rotates.
  • the hub 53 includes a front end surface 53F positioned at the front end in the direction of the rotation axis A, a rear edge 53B positioned at the rear end, an inclined surface 53K positioned between the front end surface 53F and the rear edge 53B, and a front end surface 53F. And the above-described back surface to which the fixing portion 45a of the rotor 45 is fixed.
  • the rear edge 53B of the hub 53 is also the rear end of the inclined surface 53K.
  • the inclined surface 53K has an outer diameter that increases toward the rear B.
  • the rear end portion of each blade 55 is joined to the inclined surface 53K.
  • the trailing edge 53B is located on the radially outer side of the stator 43 and the rotor body 45b.
  • the hub 53 has a through-hole penetrating in the front-rear direction at the center.
  • a front shaft portion of the non-rotating shaft 80 and a bearing portion 60 are disposed in the through hole.
  • the bearing portion 60 is provided between the front shaft portion of the non-rotating shaft 80 and the impeller 51.
  • the bearing unit 60 supports the impeller 51 so that the impeller 51 can rotate around the non-rotating shaft 80.
  • the right heat exchanger 15 is arranged on the right side R of the impeller 51, and the left heat exchanger 15 is arranged on the left side L of the impeller 51.
  • Each heat exchanger 15 is located downstream of the impeller 51 in the air flow direction.
  • Each heat exchanger 15 has a rectangular parallelepiped shape that is long in the vertical direction, a lower end portion thereof is positioned in a drain pan 30 described later, and an upper end portion thereof is close to or in contact with the top plate 22.
  • the right heat exchanger 15 is disposed so as to be inclined with respect to the front-rear direction so that the front surface portion 15F is located on the left side L with respect to the rear surface portion 15B.
  • the left heat exchanger 15 is disposed so as to be inclined with respect to the front-rear direction so that the front surface portion 15F is positioned on the right side R with respect to the rear surface portion 15B.
  • each heat exchanger 15 includes a plurality of metal tubes having a flat shape and a plurality of heat transfer fins, but is not limited thereto.
  • the heat exchanger 15 of the present embodiment is a microchannel type heat exchanger (for example, an aluminum laminated heat exchanger) that is small and has high heat exchange efficiency, but is not limited thereto.
  • the metal tube for example, a multi-hole tube in which a plurality of refrigerant channels are formed can be used, and as the heat transfer fin, for example, a corrugated fin can be used.
  • the drain pan 30 is disposed below the impeller 51 and the pair of heat exchangers 15 and 15.
  • the drain pan 30 is open at the top and has a water storage space for storing water.
  • the water storage space is provided in a range that spans the right heat exchanger 15 and the left heat exchanger 15.
  • the drain pan 30 has a bottom portion that faces the lower ends of the pair of heat exchangers 15 and 15 and a wall portion that rises upward from the peripheral edge of the bottom portion.
  • the water accommodation space is a space partitioned by a bottom portion and a wall portion.
  • the drain pan 30 is disposed at a position higher than the bottom plate 21 of the case 20, and an accommodation space 58 is formed between the lower surface of the drain pan 30 and the upper surface of the bottom plate 21 of the case 20. Yes.
  • the housing space 58 houses the electrical component case 100, the drain hose 56, and the like.
  • the airflow guide unit 90 guides the airflow that is blown out from the impeller 51 and flows into the space between the hub 53 and the back plate 26. As shown in FIGS. 3 and 4, the airflow guide portion 90 is provided between the back plate 26 and the hub 53. Further, the airflow guide unit 90 is disposed around the stator 43 of the motor 49. The airflow guide portion 90 is provided between the stator 43 of the motor 49 and the plurality of inner wall surfaces S1 and S2.
  • the airflow guide 90 is an annular member surrounding the rotation axis A.
  • the airflow guide portion 90 is configured by a plurality of arc-shaped members 93 having substantially the same shape (four arc-shaped members 93 in the present embodiment), but is not limited thereto. These arc-shaped members 93 are arranged so as to form one continuous ring around the rotation axis A.
  • the airflow guide portion 90 by the plurality of arc-shaped members 93, it is possible to improve moldability and assemblability (workability).
  • the airflow guide section 90 includes an outer peripheral surface 91 extending along the rotation direction of the impeller 51, and a front surface 94 positioned on the hub 53 side with respect to the outer peripheral surface 91 and extending along the rotation direction.
  • the outer peripheral surface 91 and the front surface 94 have a ring shape (circular shape) that is continuous in the rotation direction and surrounds the rotation axis A.
  • the front surface 94 is a surface that is smoothly continuous with the outer peripheral surface 91.
  • the front surface 94 is a surface facing the hub 53 and is a flat surface parallel to the back plate 26 or a convex curved surface convex toward the hub 53 side.
  • the outer peripheral surface 91 is a straight portion inclined at an angle ⁇ 1 with respect to the inner surface of the back plate 26 in the axial sectional view of the airflow guide portion 90 shown in FIG.
  • the end of the outer peripheral surface 91 on the back plate 26 side (end on the outside in the radial direction) is provided at a position close to the back plate 26.
  • a chamfered portion 98 is provided at an end portion (corner portion) on the radially outer side of the airflow guide portion 90.
  • the chamfered portion 98 is interposed between the outer peripheral surface 91 and the inner surface of the back plate 26.
  • the outer peripheral surface 91 is inclined so that the distance from the rotation axis A becomes smaller toward the front plate 25 side. As shown in FIG. 7B, the angle ⁇ 1 formed by the outer peripheral surface 91 and the inner surface of the back plate 26 is an obtuse angle.
  • the inclination angle ⁇ 1 of the outer peripheral surface 91 may be appropriately set in consideration of the airflow guiding effect that changes depending on the positional relationship with the impeller 51, the motor 49, and the like, and is not particularly limited.
  • the airflow guide section 90 further includes an inner peripheral surface 95 (see FIG. 6B) extending downward from a radially inner edge of the front surface 94, and a plurality of recesses 92 recessed from the inner peripheral surface 95 radially outward. It has a back surface 97 (see FIG. 7B).
  • the inner peripheral surface 95 is located on the radially outer side than the stator 43 and the rotor 45 of the motor 49.
  • the plurality of concave portions 92 are arranged at substantially equal intervals in the circumferential direction.
  • a substantially C-shaped elastic member 96 formed of synthetic rubber or the like and a flange portion 48 of the stator 43 are fitted in each recess 92.
  • a bolt (not shown) is inserted into the through hole 26a provided in the back plate 26 and screwed into the screw hole 90a provided in the back surface 97. Yes.
  • the motor 49 is fixed to the back plate 26. Therefore, the airflow guide section 90 also has a function as a fixing member for fixing the motor 49 to the back plate 26. Therefore, it is not necessary to provide a fixing member separately, and it is possible to reduce the number of parts and save space.
  • the radially outer end of the airflow guide portion 90 (the radially outer end of the outer peripheral surface 91) is located on the radially inner side of the hub 53 on the radially outer end. Moreover, the airflow guide part 90 is located in the radial direction outer side than the rotor main body 45b. The front plate 25 side end of the airflow guide portion 90 is located closer to the back plate 26 than the hub 53, but may be located closer to the front plate 25 than the hub 53.
  • the outer peripheral surface 91 is curved in a concave shape or a convex shape so that the distance from the rotation axis A becomes smaller toward the front plate 25 side. It may be in the form.
  • the outer peripheral surface 91 is a convex curved surface
  • the outer peripheral surface 91 is a concave curved surface.
  • the tangent line L1 at the end of the outer peripheral surface 91 on the hub 53 side is preferably inclined toward the rotation axis A side.
  • FIG. 8C is a front view schematically showing Modification 3 of the airflow guide section 90.
  • the airflow guide portion 90 includes a plurality of arcuate members 93 (two arcuate members in the present embodiment) arranged in a part around the rotation axis A. 93).
  • Each arcuate member 93 is disposed between the second inner wall surface S ⁇ b> 2 and the impeller 51.
  • the central angle ⁇ 2 of each arc-shaped member 93 is 90 degrees is illustrated, but the present invention is not limited to this.
  • the central angle ⁇ 2 of the arcuate member 93 is, for example, the length when the arcuate member 93 is viewed in plan (the length in the left-right direction when the arcuate member 93 is viewed from the top plate 22 side), for example, It can be set to be equal to or larger than the diameter.
  • the arc-shaped member 93 can cover many areas of the path of the airflow that bounces back at the second inner wall surface S2 and flows into the gap between the hub 53 and the back plate 26.
  • route of the airflow which flows into the said clearance gap are covered, there exists the following merit. That is, more airflows out of the airflow flowing into the gap can be guided more smoothly in the direction of the heat exchanger 15.
  • the airflow quickly flows out from the gap, interference with the mainstream is reduced, and turbulence of the mainstream can be reduced. Further, the air flow quickly flows out from the gap, thereby suppressing the flow path (effective flow path) of the air flow in the case 20 from being narrowed. As a result, the resistance of the flow when evaluated with the entire airflow blown out from the impeller 51 and reaching the heat exchanger 15 is reduced. As described above, since the disturbance of the main flow is suppressed and the effective flow path of the air flow is suppressed from being narrowed, noise can be greatly reduced.
  • FIG. 8D is a front view schematically showing Modification 4 of the airflow guide section 90.
  • the fourth modification is the same as the third modification in that the two arcuate members 93 are line-symmetrical with respect to the rotation axis A, but differs from the third modification in the following points. That is, in the fourth modification, as shown in FIG. 8D, the two arcuate members 93 are not provided at positions facing the vertical direction (vertical direction) as shown in FIG. 8C. In addition, two arc-shaped members 93 are provided at positions shifted in the rotation direction C of the impeller 51 with the rotation axis A as the center.
  • each arcuate member 93 is provided at a position where it intersects with a vertical line V (vertical line V) passing through the rotation axis A in the vertical direction.
  • V vertical line
  • the circumferential length in the region on the rotation direction C side from the straight line V is larger than the circumferential length in the region on the opposite side of the rotation direction C from the straight line V.
  • each arc-shaped member 93 in the modified example 4 is adjusted in a range similar to the central angle ⁇ 2 of the modified example 3.
  • This modification 4 is effective when the path of the airflow that bounces back at the second inner wall surface S2 and flows into the gap between the hub 53 and the back plate 26 is shifted in the rotation direction C.
  • each arcuate member 93 is also arranged at a position shifted in the rotational direction C, each arcuate member 93 is bounced back at the second inner wall surface S2 and the gap between the hub 53 and the back plate 26. Many areas of the airflow path flowing into the can be covered.
  • the velocity of the air flowing out from the impeller 51 tends to be larger in the airflow flowing in the region near the rear B.
  • the blower 13 is a mixed flow blower
  • the air flows out obliquely backward from the impeller 51, so that the velocity of the airflow passing through the heat exchanger 15 is closer to the rear B than the airflow F3 closer to the front F.
  • the air flow F1 becomes larger. That is, when the speeds of the airflow F1, the airflow F2, and the airflow F3 are compared, the speed of the airflow F1 is the highest and the speed of the airflow F3 is the lowest. Therefore, when there is an inner wall surface close to the impeller 51, the air flow blown out from the impeller 51 easily flows into the gap between the hub 53 and the back plate 26, which causes noise.
  • the second inner wall surface S2 side which is a region where the heat exchanger 15 is not provided, is provided.
  • the airflow blown out from the impeller 51 toward the region is bounced back at the second inner wall surface S2 and then flows into the narrow gap between the hub 53 and the back plate 26 vigorously.
  • a part of the airflow that has flowed into the gap vigorously reaches the outer peripheral surface 91 of the airflow guide portion 90 before reaching the motor 49, and is guided by the outer peripheral surface 91 to be substantially in the circumferential direction of the outer peripheral surface 91. It becomes the flow along. Accordingly, the airflow that has flowed into the gap vigorously is smoothly discharged from the gap (see FIG. 9B).
  • the outer peripheral surface 91 of the airflow guide section 90 is inclined so that the distance from the rotation axis A decreases toward the hub 53 side (front plate 25 side), the airflow that has reached the outer peripheral surface 91 Further, it is suppressed that the outer peripheral surface 91 is bounced back. As a result, the airflow that has reached the outer peripheral surface 91 is likely to flow in the substantially circumferential direction along the inclined shape of the outer peripheral surface 91 (the collision of the airflow on the outer peripheral surface 91 is mitigated, and the outer peripheral surface 91 receives the airflow).
  • the air flow that has reached the outer peripheral surface 91 of the air flow guide unit 90 is the flow of air due to the rotation of the impeller 51. Under the influence, it becomes a flow along the substantially circumferential direction of the outer peripheral surface 91 of the airflow guide portion 90, and then is smoothly discharged from the gap. Accordingly, since the generation of vortex is suppressed in the gap between the hub 53 and the back plate 26, an increase in noise can be suppressed.
  • FIG. 10 is a perspective view showing a positional relationship among the hub 53 of the impeller 51, the motor 49, and the airflow guide section 90 in the air conditioner according to the fifth modification, and this perspective view has a cross section cut in the axial direction. It is drawn.
  • FIG. 11A is a plan view schematically showing the positional relationship between the motor 49 and the airflow guide section 90 in the air conditioner according to Modification Example 5, and
  • FIG. 11B shows the air according to Modification Example 5.
  • a conditioner it is sectional drawing which shows roughly the flow of the air which blows off from the impeller 51 and flows in into the space between a hub and a backplate.
  • the outer peripheral surface 91 of the airflow guide section 90 has a curved surface (concave curved surface) 911 positioned on the inner surface side of the back plate 26, and the curved surface 911. And a vertical surface (surface parallel to the rotation axis A) 912 located on the front plate 25 side (hub 53 side).
  • the fifth modified example since the area occupied by the vertical surface 912 in the outer peripheral surface 91 is very small, an effect of guiding the airflow that has reached the outer peripheral surface 91 in the substantially circumferential direction along the shape of the curved surface 911 can be obtained. . Therefore, in the modified example 5, noise can be reduced as compared with a reference example described later in which the entire outer peripheral surface is a vertical surface.
  • the airflow guide part 90 is comprised by the several member 99 (four members 99 in this embodiment) of substantially the same shape. These members 99 are arranged at equal intervals in the circumferential direction.
  • the region where the member 99 is provided around the motor 49 is smaller than the region where the member 99 is not provided.
  • the area where the member 99 is provided around the motor 49 is larger than the area where the member 99 is not provided.
  • the airflow guide section 90 of the modification 5 also has a function of fixing the motor 49.
  • the airflow guide section 90 of the modified example 5 has the vertical surface 912 in a part of the outer peripheral surface 91, and the area where the member 99 is provided around the motor 49 is less than the area where the member 99 is not provided. . Therefore, the airflow guiding effect is higher in the airflow guiding portion 90 shown in FIGS. 7A and 7B and FIGS. 8A and 8B than in the fifth modification.
  • FIG. 12 (A) is a perspective view schematically showing the flow of air blown out from the impeller and flowing into the space between the hub and the back plate in the air conditioner of the reference example
  • FIG. FIG. 12 is a plan view schematically showing the air flow
  • FIG. 12C is an axial sectional view schematically showing the air flow.
  • the outer peripheral surface 191 of the motor mounting member 190 is a surface parallel to the rotation axis A as a whole. Therefore, in this reference example, the airflow flowing into the gap between the hub 53 and the back plate 26 vigorously flows into the outer peripheral surface 191 of the fixing member (support component) 190 and the rotor that fix the motor to the back plate within the gap. It collides with the outer peripheral surface of the main body 45b. The collided air current is bounced off at these outer peripheral surfaces and becomes a vortex as shown in FIG. Such a vortex tends to stay while swirling in and around the gap.
  • the vortex flow interferes with the air flow (main flow) blown out from the impeller 51 and disturbs the main flow, and the main flow flows when the width of the main flow passage (effective flow passage) in the case 20 is reduced. Increase resistance. As a result, the noise of the air conditioner further increases.
  • the airflow guide portion 90 having the outer peripheral surface 91 as described above is provided, in the air conditioner in which the heat exchanger 15 is provided in a part of the periphery of the impeller 51, the compactness is achieved. It is possible to suppress an increase in noise.
  • the outer peripheral surface 91 of the airflow guide part 90 has an annular shape that is continuous in the rotation direction, the airflow is compared with the case where the outer peripheral surface 91 is discontinuous in the rotation direction and has cuts and steps. Since the disturbance of the noise is further suppressed, noise can be further reduced.
  • the radially outer end of the airflow guide portion 90 is positioned radially inward of the radially outer end of the hub 53, so that the main flow channel (effective It is possible to further suppress the narrowing of the width of the flow path). Thereby, it can further suppress that resistance when a mainstream flows increases.
  • the motor 49 is an outer rotor type motor 49. Since an outer rotor type motor generally has a large diameter, when used in combination with a mixed flow blower or a centrifugal blower, the airflow flowing into the gap between the hub 53 and the back plate 26 is the outer peripheral surface of the rotor 45 (the outer periphery of the rotor main body 45b). Surface). When the airflow reaches this outer peripheral surface, eddy currents are likely to occur in the gap and the vicinity thereof. When a vortex is generated in the gap and the vicinity thereof, interference with the mainstream is likely to occur. Therefore, when using in combination with an outer rotor type motor and a mixed flow blower or a centrifugal blower, the provision of the air flow guide unit 90 is particularly effective in terms of noise reduction.
  • the airflow guide portion 90 is located on the radially outer side of the rotor 45 of the motor 49, so that the contact between the rotor 45 and the airflow guide portion 90 can be reliably prevented.
  • the airflow guide unit 90 is a separate member from the case 20
  • the present invention is not limited to this.
  • the airflow guide unit 90 may be formed integrally with the back plate 26 to form a part of the case 20.
  • the motor 49 a motor of a type in which the rotor is disposed inside the stator can also be used.
  • the airflow guide unit 90 is ring-shaped is illustrated, but the present invention is not limited to this.
  • the airflow guide portion 90 may be provided only between the motor 49 and the second inner wall surface S2.
  • the airflow guide unit 90 may have a non-circular shape such as an elliptical shape or a polygonal shape.
  • the radially outer end portion of the airflow guide portion 90 is located on the radially inner side with respect to the radially outer end portion of the hub 53 .
  • the end portion may be located on the radially outer side than the radially outer end portion of the hub 53.
  • one second inner wall surface S2 is the upper surface of the partition member 41
  • the present invention is not limited to this.
  • one second inner wall surface S2 may be the upper surface of the bottom plate 21 as shown in FIGS.
  • the indoor unit 11 includes a pair of heat exchangers 15 and 15, a pair of first inner wall surfaces S ⁇ b> 1 that are provided on the radially outer side of the impeller 51, and a radially outer side of the impeller 51.
  • the case where a pair of second inner wall surfaces S ⁇ b> 2 opposed to each other provided in the above is illustrated, but is not limited thereto.
  • the heat exchanger 15 may be arranged in a substantially U shape around the impeller 51. In the case of this form, for example, the heat exchanger 15 is interposed between the three first inner wall surfaces S1 in which the heat exchanger 15 is interposed between the plurality of inner wall surfaces S and the impeller 51, and the impeller 51.
  • the structure which consists of one 2nd inner wall surface S2 which is not performed is mentioned.
  • the airflow guide unit 90 also has a function of fixing the motor 49 is exemplified, but the present invention is not limited to this.
  • the fixing member that fixes the motor 49 may be provided separately from the airflow guide section 90.
  • the air conditioner includes a case having a front plate and a back plate facing each other, a heat exchanger provided in the case, a direction supported by the back plate, and a rotation axis intersecting the back plate.
  • a mixed flow or centrifugal impeller provided in the case and having a hub attached to the motor, and a space between the hub and the back plate blown out from the impeller
  • An airflow guide for guiding the airflow flowing into the airflow.
  • the impeller is surrounded by a plurality of inner wall surfaces located on the radially outer side of the impeller, and the plurality of inner wall surfaces include a first inner wall surface and a second inner wall surface. .
  • the heat exchanger is interposed between the first inner wall surface and the impeller, and the heat exchanger is not interposed between the second inner wall surface and the impeller.
  • the distance between the second inner wall surface and the impeller is shorter than the distance between the first inner wall surface and the impeller.
  • the airflow guide has an outer peripheral surface. The outer peripheral surface extends along the rotational direction of the impeller between the back plate and the hub and between the motor and at least the second inner wall surface.
  • the outer peripheral surface is inclined or curved so that the distance from the rotating shaft becomes smaller toward the front plate.
  • the airflow guide portion having the outer peripheral surface as described above is provided, in the air conditioner in which the heat exchanger is provided in a part around the impeller, an increase in noise can be suppressed while being downsized. .
  • the airflow blown out from the impeller toward the region on the second inner wall surface side where the heat exchanger is not provided is on the second inner wall surface that is close to the impeller. After being rebounded, it flows into the narrow gap between the impeller hub and the back plate that supports the motor. A part of the airflow that has flowed into the gap vigorously reaches the outer peripheral surface of the airflow guide portion before reaching the motor, and is guided by the outer peripheral surface to flow along the substantially circumferential direction of the outer peripheral surface.
  • the airflow guide portion is inclined or curved so that the distance from the rotation shaft becomes smaller toward the front plate side, the airflow that reaches the outer peripheral surface is rebounded on the outer peripheral surface. As a result, it becomes easy to flow in the substantially circumferential direction along the inclined shape or curved shape of the outer peripheral surface. That is, in the gap, since the air flow in the rotation direction is formed by the rotation of the impeller, the air flow that has reached the outer peripheral surface of the air flow guide is affected by the air flow due to the rotation of the impeller. It becomes a flow along the substantially circumferential direction of the outer peripheral surface of the airflow guide portion, and then is smoothly discharged from the gap. Therefore, since the generation of vortex is suppressed in the gap between the hub and the back plate, an increase in noise can be suppressed.
  • the outer peripheral surface of the airflow guide portion has a ring shape continuous in the rotation direction. In this case, since the turbulence of the airflow is further suppressed as compared with the case where the outer peripheral surface is discontinuous in the rotation direction and has cuts or steps, noise can be further reduced.
  • an end portion on the radially outer side of the airflow guide portion is positioned on an inner side in the radial direction than an end portion on the radially outer side of the hub. In this case, it is possible to further suppress the narrowing of the width of the main flow path (effective flow path) in the case. Thereby, it can further suppress that resistance when a mainstream flows increases.
  • the motor is an outer rotor type motor, and the airflow guide portion is located radially outside the rotor of the motor. In this case, contact between the rotor and the airflow guide can be reliably prevented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

La présente invention concerne une roue à ailettes (51) entourée par les surfaces des parois intérieures (S) d'un boîtier (20) situées à l'extérieur de la roue à ailettes (51) dans la direction radiale. Les surfaces des parois intérieures (S) comportent des surfaces de parois intérieures primaires (S1) et des surfaces de parois intérieures secondaires (S2). Des échangeurs de chaleur (15) sont présents entre la roue à ailettes (51) et les surfaces de parois intérieures primaires (S1). Aucun échangeur de chaleur (15) n'est présent entre la roue à ailettes (51) et les surfaces de parois intérieures secondaires (S2). La distance entre la roue à ailettes (51) et les surfaces de parois intérieures secondaires (S2) est inférieure à la distance entre la roue à ailettes (51) et les surfaces de parois intérieures primaires (S1). Une section de guidage du flux d'air (90) présente une surface périphérique externe (91). La surface périphérique externe (91) s'étend le long de la direction de rotation de la roue à ailettes (51) au niveau d'une position entre une plaque arrière (26) et un moyeu (53) et entre un moteur (49) et au moins les surfaces de parois intérieures secondaires (S2). La surface périphérique externe (91) est inclinée ou courbée de telle sorte que la distance entre la surface périphérique externe (91) et un axe de rotation (A) diminue vers une plaque avant (25) dans la direction de l'axe de rotation (A).
PCT/JP2012/008185 2011-12-27 2012-12-21 Climatiseur WO2013099182A1 (fr)

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JP2011-286805 2011-12-27

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JP6456179B2 (ja) * 2015-02-18 2019-01-23 サンデンホールディングス株式会社 送風機

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JPH10148353A (ja) * 1996-11-20 1998-06-02 Toshiba Corp 天井カセット形空気調和装置のファンモータ取付構造
JPH11337108A (ja) * 1998-05-26 1999-12-10 Toshiba Corp 空気調和機
JP2001091039A (ja) * 1993-04-09 2001-04-06 Daikin Ind Ltd 空気調和装置
JP2002021790A (ja) * 2000-07-06 2002-01-23 Denso Corp 遠心式送風機
JP2004156886A (ja) * 2002-11-08 2004-06-03 Mitsubishi Heavy Ind Ltd 空調用室内ユニットおよび天井埋込型空気調和機
JP2005133710A (ja) * 2003-10-07 2005-05-26 Daikin Ind Ltd 遠心送風機およびこれを用いた空気調和機
JP2007051790A (ja) * 2005-08-15 2007-03-01 Hitachi Ltd 空調用室内機
JP2009024936A (ja) * 2007-07-19 2009-02-05 Daikin Ind Ltd 空気調和機

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JPS599436A (ja) * 1982-07-08 1984-01-18 Matsushita Seiko Co Ltd 空冷ヒ−トポンプ式空気調和機
JPS60159529A (ja) * 1984-01-26 1985-08-21 Sanyo Electric Co Ltd 熱交換ユニツト
JPS62196531A (ja) * 1986-02-24 1987-08-29 Hitachi Ltd 天井埋込型空気調和機
JP2009097778A (ja) * 2007-10-16 2009-05-07 Daikin Ind Ltd 空気調和機

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Publication number Priority date Publication date Assignee Title
JPS6326013U (fr) * 1986-08-05 1988-02-20
JP2001091039A (ja) * 1993-04-09 2001-04-06 Daikin Ind Ltd 空気調和装置
JPH10148353A (ja) * 1996-11-20 1998-06-02 Toshiba Corp 天井カセット形空気調和装置のファンモータ取付構造
JPH11337108A (ja) * 1998-05-26 1999-12-10 Toshiba Corp 空気調和機
JP2002021790A (ja) * 2000-07-06 2002-01-23 Denso Corp 遠心式送風機
JP2004156886A (ja) * 2002-11-08 2004-06-03 Mitsubishi Heavy Ind Ltd 空調用室内ユニットおよび天井埋込型空気調和機
JP2005133710A (ja) * 2003-10-07 2005-05-26 Daikin Ind Ltd 遠心送風機およびこれを用いた空気調和機
JP2007051790A (ja) * 2005-08-15 2007-03-01 Hitachi Ltd 空調用室内機
JP2009024936A (ja) * 2007-07-19 2009-02-05 Daikin Ind Ltd 空気調和機

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