WO2012169183A1 - Ventilateur et climatiseur - Google Patents

Ventilateur et climatiseur Download PDF

Info

Publication number
WO2012169183A1
WO2012169183A1 PCT/JP2012/003706 JP2012003706W WO2012169183A1 WO 2012169183 A1 WO2012169183 A1 WO 2012169183A1 JP 2012003706 W JP2012003706 W JP 2012003706W WO 2012169183 A1 WO2012169183 A1 WO 2012169183A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
impeller
blower
stator
rotor
Prior art date
Application number
PCT/JP2012/003706
Other languages
English (en)
Japanese (ja)
Inventor
真輔 原田
安尾　晃一
亨 繁澤
竜佑 太田黒
浩和 藤井
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 WO2012169183A1 publication Critical patent/WO2012169183A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D25/062—Details of the bearings
    • 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
    • F04D25/0653—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the motor having a plane air gap, e.g. disc-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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings

Definitions

  • the present invention relates to a blower including a centrifugal or mixed flow impeller, and an air conditioner including the blower.
  • centrifugal blowers and mixed flow blowers have been used in the field of ventilation and air conditioning.
  • the centrifugal blower has a centrifugal impeller, and has a structure in which air sucked in the axial direction into the impeller is blown out in the centrifugal direction (radially outward).
  • 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 out in a direction inclined with respect to the centrifugal direction (radially outward). Therefore, the centrifugal and mixed flow impellers are more complex and more heavy than the relatively simple axial flow impellers used for axial blowers such as propeller fans. Cheap. For this reason, the bearing that rotatably supports the centrifugal or mixed flow impeller needs to be durable enough to withstand the load applied when the impeller rotates, and has a structure that stably supports the impeller. I need it.
  • Patent Document 1 discloses a blower including an outer rotor type motor having a non-rotating shaft and a centrifugal impeller.
  • the centrifugal impeller is rotatably supported on a non-rotating shaft by two bearing portions.
  • the two bearing portions are arranged around the non-rotating shaft with a predetermined interval in the axial direction of the non-rotating shaft.
  • the impeller in order to withstand the load applied when the impeller rotates and to stably support the impeller, the impeller is disposed at a predetermined interval.
  • the two bearing parts are supported on the non-rotating shaft in a both-sided state.
  • the hub In order to reduce the load applied to the bearing, it is necessary to bring the center of gravity of the impeller closer to the bearing.
  • the hub has to be disposed so that the hub largely wraps around the stator. That is, since it is necessary to design the shape of the hub so that the hub surrounds not only the front portion around the stator but also the rear portion around the stator, the shape of the impeller is restricted.
  • An object of the present invention is to provide a centrifugal blower or a mixed flow blower that can withstand a load applied when the impeller rotates and can stably support the impeller and that has a small restriction on the shape of the impeller, and an air conditioner including the same. Is to provide a machine.
  • the blower of the present invention comprises an outer rotor type motor (49) having a stator (43), a rotor (45) and a non-rotating shaft (80), and a centrifugal or mixed flow type fixed to the rotor (45).
  • the non-rotating shaft (80) has an outer shaft portion (86) positioned on the outer side in the axial direction than the stator (43).
  • the bearing portion (60) is interposed between the outer shaft portion (86) and the impeller (51) or the rotor (45).
  • the center of gravity (51G) of the impeller (51) is located within the range (60S) of the bearing portion (60).
  • FIG. 1 It is a perspective view which shows the air conditioner provided with the air blower which concerns on one Embodiment of this invention. It is a perspective view which shows the internal structure of the said air conditioner. It is the III-III sectional view taken on the line of FIG. It is sectional drawing which shows the said air blower. It is sectional drawing which expanded a part of air blower shown in FIG. (A) is sectional drawing which shows the air blower concerning the reference example 1, (B) is sectional drawing which shows the air blower concerning the reference example 2.
  • FIG. It is a fragmentary sectional view showing an air blower concerning a modification of the embodiment. It is the fragmentary sectional view which expanded a part of air blower shown in FIG.
  • FIG. 1 A one-dot chain line A in the figure indicates a rotation center A of an impeller 51 and an axis A of a non-rotating shaft 80, which will be described later, and is directed in the front-rear direction (horizontal direction).
  • the indoor unit 11 includes a blower 13, a pair of heat exchangers 15 and 15 disposed on both sides of the blower 13, and a lower side of the blower 13 and the heat exchangers 15 and 15.
  • a drain pan 30 which is disposed in D and stores the dew condensation water generated in the heat exchangers 15 and 15 and a case 20 for storing them are provided.
  • the case 20 has a rectangular parallelepiped shape with a small thickness in the front-rear direction and a larger width in the left-right direction than in the vertical direction.
  • a blower 13 in this embodiment, a mixed flow blower having a mixed flow or centrifugal impeller is disposed in the case 20 in a posture in which the direction of the rotation center A is directed in the front-rear direction.
  • the thickness is reduced in the front-rear direction compared to the case of using a cross flow fan.
  • 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.
  • the air sucked from the front part of the case 20 flows to the outside in the radial direction of the blower 13, and after heat exchange is performed in the heat exchanger 15 on the right R or left L, The air is blown into the room from the side (see FIGS. 1 and 3).
  • the case 20 has a bottom plate 21, a top plate 22, a right side plate 23, a left side plate 24, a front plate 25 and a back plate 26.
  • the decorative front plate 25 includes a suction port opening / closing plate 251 and a pair of outlet opening / closing plates 252 and 252 disposed on both sides of the suction port opening / closing plate 251.
  • the air inlet opening / closing plate 251 is disposed in front F of the blower 13 and has a rectangular shape that occupies most of the area of the decorative 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 when viewed from the front, and are located directly 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 port opening / closing plate 251 is in a closed state in which the suction port 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. 1, and the upper edge portion 251a, the lower edge portion 251b, and the side edge portions of the suction port opening / closing plate 251 are moved.
  • a gap is formed between the front edge portion 21a of the bottom plate 21, the front edge portion 22a of the top plate 22, and the side edge portions of the air outlet opening / closing plates 252 and 252, 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 portion 252a, and the right edge portion 252b of the air outlet opening / closing plate 252 and the right edge portion 252b of 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.
  • the right heat exchanger 15 is arranged on the right side R of the blower 13, and the left heat exchanger 15 is arranged on the left side L of the blower 13. Each heat exchanger 15 is positioned downstream of the blower 13 in the air flow direction. Each heat exchanger 15 has a rectangular parallelepiped shape that is long in the vertical direction, the lower end portion is located in the drain pan 30, and the upper end portion is close to or abuts on the top plate 22. As shown in FIG. 3, the right heat exchanger 15 is disposed 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. Similarly, 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.
  • the blower 13 of this embodiment shown in FIGS. 2 to 4 is a mixed flow blower.
  • the blower 13 includes a mixed flow impeller 51, a motor 49 that rotates the impeller 51, and a bearing unit 60.
  • the motor 49 is an outer rotor type motor having a stator 43, a rotor 45, and a non-rotating shaft 80.
  • the impeller 51 includes a circular hub 53 that is fixed to the motor 49 in front view, a circular shroud 54 that is disposed in front F of the hub 53 and opens in the front-rear direction, and the shroud 54 and hub 53. And a plurality of blades 55 arranged along the circumferential direction.
  • the bearing portion 60 is interposed between the non-rotating shaft 80 of the motor 49 and the impeller 51, and supports the impeller 51 so as to be rotatable with respect to the non-rotating shaft 80.
  • the bearing portion 60 has an annular shape when viewed from the front, and has a through hole 60H that penetrates in the direction of the axis A of the non-rotating shaft 80 (direction in which the axis A extends).
  • the bearing portion 60 has a predetermined length in the direction of the axis A.
  • the center of gravity 51G of the impeller 51 is located in the range 60S of the bearing portion 60 in the direction of the axis A (axial direction).
  • the state where the center of gravity 51G is located within the range 60S of the bearing part 60 means that the center of gravity 51G is located between the front end 60F and the rear end 60B of the bearing part 60 in the direction of the axis A, and the center of gravity 51G is a bearing. That is, it is located on the radially inner side of the outer peripheral surface 60P of the portion 60.
  • the center of gravity 51G of the impeller 51 is preferably located in the range 60S of the bearing part 60 and in the through hole 60H of the bearing part 60. More preferably, the center of gravity 51G of the impeller 51 is located in the through hole 60H of the bearing portion 60 and on the axis A. The center of gravity 51G of the impeller 51 is located in the through hole 60H of the bearing portion 60, is located on the shaft center A, and is located in the center of the front end 60F and the rear end 60B of the bearing portion 60 in the direction of the shaft center A. More preferably.
  • the arrow of the dashed-two dotted line extended below from the gravity center 51G shown in FIG. 4 has shown the direction of gravity.
  • the blower 13 will be described in more detail.
  • the stator 43 has a flat, generally cylindrical shape whose thickness in the front-rear direction is smaller than the diameter.
  • 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 connected to the back plate by an unillustrated bolt inserted in an unillustrated insertion hole provided in the flange portion 48 in a state where the back surface of the stator 43 is arranged to face the inner surface of the back plate 26 of the case 20. It is fixed to 26.
  • a coil 44 is disposed inside the stator 43.
  • a through hole 46 that penetrates in the front-rear direction is formed at the center of the stator 43.
  • the through hole 46 has a first hole 46a located in the front F, a second hole 46b having a smaller inner diameter than the first hole 46a and located in the rear B of the first hole 46a, and a second hole 46a. And a third hole 46c having an inner diameter larger than that of the hole 46b and positioned rearward B of the second hole 46b.
  • a part of the non-rotating shaft 80 is disposed in the through hole 46.
  • the non-rotating shaft 80 is a columnar member extending in the direction of the axis A and is supported by the stator 43.
  • the non-rotating shaft 80 includes an outer shaft portion 86 positioned outside the stator 43 in the direction of the axis A, that is, at a front F of the stator 43, and an inner shaft portion 87 disposed inside the through hole 46 of the stator 43. And have.
  • the outer shaft portion 86 includes a front end portion 81 located at the front F, a flange portion 83 located at the rear B, and an intermediate portion 82 located between the front end portion 81 and the flange portion 83.
  • the distal end portion 81 is the smallest and the flange portion 83 is the largest.
  • the intermediate part 82 has a step surface 82a at the boundary with the tip part 81.
  • the step surface 82a is an annular surface in front view facing the front F.
  • the outer diameter of the flange portion 83 is larger than the inner diameter of the first hole portion 46a of the through hole 46.
  • the non-rotating shaft 80 is positioned with respect to the stator 43 with the flange portion 83 in contact with the front surface of the stator 43.
  • a screw hole 87b is formed at the front end of the outer shaft portion 86 toward the rear B, and has an internal thread on the inner peripheral surface.
  • a bolt B2 which will be described later, is screwed into the screw hole 87b.
  • the inner shaft portion 87 includes a first column portion 84 extending rearward B from the flange portion 83 and a second column portion 85 having an outer diameter smaller than that of the first column portion 84.
  • the outer diameter of the first column portion 84 is approximately the same as the inner diameter of the first hole portion 46a of the stator 43, and is disposed in the first hole portion 46a.
  • the second column portion 85 has an outer diameter that is approximately the same as the inner diameter of the second hole portion 46b of the stator 43, and is disposed in the second hole portion 46b.
  • a screw hole 87a is formed at the rear end of the inner shaft portion 87 toward the front F and has an internal thread on the inner peripheral surface.
  • the non-rotating shaft 80 is fixed to the stator 43 by a bolt B1 screwed into the screw hole 87a via a washer 74.
  • the washer 74 is disposed in the third hole 46 c of the stator 43 and is in contact with the rear end of the inner shaft portion 87.
  • the rotor 45 includes an annular fixing portion 45a having an insertion hole penetrating in the front-rear direction at the center, and a rotor body 45b extending in a cylindrical shape from the periphery of the fixing 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 45a is in contact with the back surface of the hub 53 of the impeller 51.
  • the outer shaft portion 86 of the non-rotating shaft 80 is inserted through the insertion hole of the fixed portion 45a.
  • An intermediate portion 82 of the outer shaft portion 86 of the non-rotating shaft 80 is disposed on the radially inner side of the insertion hole of the fixed portion 45a.
  • the rotor main body 45b is disposed on the outer side in the radial direction of the stator 43 so as to cover the outer peripheral surface of the stator 43. In other words, the front portion of the stator 43 is inserted into the rotor body 45b. 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 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 hub 53 has a through-hole penetrating in the front-rear direction at the center.
  • the outer shaft portion 86 of the non-rotating shaft 80 is inserted into the through hole.
  • the through-hole of the hub 53 is located in the bearing hole 532 where the bearing 60 is disposed and the front F of the bearing hole 532, and has a smaller inner diameter than the bearing hole 532, and the bolt B2 is inserted therein.
  • a fixing member hole portion 533 which is positioned behind B of the bearing hole portion 532 and has a larger inner diameter than the bearing hole portion 532 and in which the fixing member 73 is disposed.
  • the front end surface 53F is a ring-shaped surface perpendicular to the axis A.
  • the inclined surface 53K is connected to the peripheral edge portion of the front end surface 53F.
  • the inclined surface 53K is directed toward the stator 43 in the direction of the axis A toward the radially outer side. In other words, the outer diameter of the inclined surface 53K 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 rearward B with respect to the fixing portion 45a of the rotor 45.
  • the trailing edge 53B is located on the radially outer side of the stator 43 and the rotor body 45b.
  • the trailing edge 53B is located at a position facing the outer peripheral surface of the rotor body 45b and the outer peripheral surface of the stator 43 in the radial direction.
  • the bearing portion 60 is disposed only in front F of the stator 43 in the direction of the axis A.
  • the bearing portion 60 having a single bearing is provided between the outer shaft portion 86 of the non-rotating shaft 80 and the impeller 51, but is not limited thereto.
  • the bearing unit 60 may include a plurality of bearings as in a modification described later.
  • the bearing portion is not provided inside the stator 43.
  • the bearing portion 60 is disposed in front F of the rotor 45 in the direction of the axis A.
  • the bearing portion 60 is located between the front end surface 53F and the rear edge 53B of the hub 53 in the direction of the axis A.
  • the bearing portion 60 is located between the front edge of the inclined surface 53K (the peripheral edge of the front end surface 53F) and the rear edge of the inclined surface 53K in the direction of the axis A.
  • the bearing unit 60 supports the impeller 51 so that the impeller 51 can rotate around the non-rotating shaft 80.
  • the bearing part 60 has an inner ring part 61 as a first wheel part, an outer ring part 62 as a second wheel part, and a rolling element (not shown) interposed therebetween. Examples of rolling elements include balls and rollers.
  • the outer ring portion 62 can rotate with respect to the inner ring portion 61 by rolling of the rolling elements.
  • the inner ring portion 61 is a ring-shaped member fixed to the outer shaft portion 86 of the non-rotating shaft 80.
  • the fit tolerance between the inner diameter of the inner ring portion 61 and the outer diameter of the distal end portion 81 of the outer shaft portion 86 is a clearance fit.
  • the rear end of the inner ring part 61 is in contact with the step surface 82a of the outer shaft part 86. Thereby, the movement to the back B of the inner ring
  • a washer 71 is in contact with the front end of the inner ring portion 61.
  • the bolt B2 is screwed into the screw hole 87b at the front end of the outer shaft portion 86. Thereby, the movement of the inner ring portion 61 to the front F and the rotation of the inner ring portion 61 with respect to the outer peripheral surface of the tip end portion 81 are restricted.
  • the outer ring portion 62 is a ring-shaped member fixed to the hub 53 of the impeller 51.
  • the fit tolerance between the outer diameter of the outer ring portion 62 and the inner diameter of the bearing hole portion 532 is a clearance fit.
  • the inner diameter of the outer ring portion 62 is larger than the outer diameter of the inner ring portion 61.
  • a spacer 72 is in contact with the front end of the outer ring portion 62.
  • the spacer 72 is a ring-shaped member disposed so as to contact the front end surface of the bearing hole 532. Thereby, the movement to the front F of the outer ring
  • the rear end of the outer ring portion 62 is in contact with the front surface of a ring-shaped fixing member 73 disposed in the fixing member hole 533.
  • the inner diameter of the fixing member 73 is smaller than the outer diameter of the outer ring portion 62.
  • the fixing member 73 is fixed to the fixing member hole 533 of the hub 53. Thereby, the movement of the outer ring portion 62 to the rear B and the rotation with respect to the inner peripheral surface of the bearing hole portion 532 are restricted.
  • FIG. 6A is a cross-sectional view showing a blower according to Reference Example 1
  • FIG. 6B is a cross-sectional view showing the blower according to Reference Example 2.
  • the blower of Reference Example 1 includes a mixed flow impeller 151 and a motor 149 that rotates the impeller 151.
  • the motor 149 is an outer rotor type motor having a stator 143, a rotor 145, a rotating shaft 180, and a bearing portion including a pair of bearings 160 and 160.
  • a rotating shaft 180 is rotatably supported inside the stator 143 via a pair of bearings 160 and 160.
  • the center of gravity 151G of the impeller 151 is located near the front end of the rotating shaft 180, and is located in front F of the stator 143 and the pair of bearings 160 and 160.
  • the center of gravity 151G of the impeller 151 is not within the range of the bearing portion (the pair of bearings 160, 160)
  • a load is applied to a position near the front end of the rotary shaft 180 away from the bearings 160, 160. Will be biased.
  • problems such as deterioration of durability and generation of abnormal noise may occur.
  • the center of gravity 151G of the impeller 151 is positioned within the range of the bearing portion (the pair of bearings 160, 160). It is conceivable to change the shape of the impeller 151.
  • a pair of bearings 160 and 160 are disposed inside the stator 143. Since a coil is disposed inside the stator 143, the size of each bearing 160 (particularly the size in the radial direction) is naturally limited. For this reason, the size of the bearing 160 may not be designed to be sufficiently large according to the required durability.
  • FIG. 7 is a partial cross-sectional view showing a blower 13A according to a modification of the embodiment shown in FIG.
  • FIG. 8 is an enlarged partial cross-sectional view of a part of the blower shown in FIG.
  • This blower 13A is used as a blower mechanism of the indoor unit 11 shown in FIGS. 1 to 3, for example.
  • the configuration of the blower 13A shown in FIG. 7 is different from the configuration of the blower 13 shown in FIG. 4 in that the bearing portion 60 is constituted by a plurality of bearings, and otherwise the configuration of the blower 13 shown in FIG. Is almost the same. Therefore, hereinafter, the bearing unit 60 will be mainly described, and the components other than the bearing unit 60 will be denoted by the same reference numerals as those in FIG.
  • the bearing portion 60 is interposed between the outer shaft portion 86 of the non-rotating shaft 80 and the impeller 51.
  • the bearing portion 60 includes a plurality of bearings arranged in the direction of the axis A (axial direction).
  • the bearing unit 60 includes a first bearing 601 and a second bearing 602.
  • the first bearing 601 and the second bearing 602 are juxtaposed in the axial direction.
  • the bearing portion 60 further includes a bearing housing 603 and a preload member 604.
  • the first bearing 601 and the second bearing 602 are disposed adjacent to each other.
  • the state where the first bearing 601 and the second bearing 602 are disposed adjacent to each other includes not only the case where the first bearing 601 and the second bearing 602 are disposed in contact with each other, The case where these are arranged adjacent to each other with a small gap between the second bearings 602 is also included.
  • the first bearing 601 and the second bearing 602 are arranged adjacent to each other with a small gap between them.
  • the size of the gap is preferably smaller than the thickness (dimension in the axial direction) of one bearing.
  • the first bearing 601 and the second bearing 602 are arranged adjacent to each other via a preload member 604 such as a spring washer or a wave washer. Since the preload member 604 is interposed between the first bearing 601 and the second bearing 602, a gap is formed between the first bearing 601 and the second bearing 602. The size of the gap is about the height of the preload member 604 such as a spring washer and a wave washer (the size of the preload member 604 in the direction of the axis A).
  • Each of the first bearing 601 and the second bearing 602 has an inner ring portion 61 as a first wheel portion, an outer ring portion 62 as a second wheel portion, and a plurality of rolling elements 63 interposed therebetween. ing.
  • Each outer ring portion 62 can rotate with respect to the inner ring portion 61 by rolling of a plurality of rolling elements 63.
  • Each inner ring portion 61 is a ring-shaped member into which the outer shaft portion 86 of the non-rotating shaft 80 is inserted.
  • Each outer ring portion 62 is a ring-shaped member disposed on the radially outer side of the corresponding inner ring portion 61.
  • the bearing housing 603 has a cylindrical shape.
  • a first bearing 601 and a second bearing 602 are disposed inside the bearing housing 603 (hollow region).
  • the bearing housing 603 is press-fitted into a recess provided in the hub 53 of the impeller 51.
  • the bearing housing 603 is fixed to the impeller 51.
  • each outer ring portion 62 is press-fitted into the bearing housing 603.
  • each outer ring portion 62 is fixed to the bearing housing 603. That is, each outer ring portion 62 is fixed to the impeller 51 via the bearing housing 603 (each outer ring portion 62 is fixed to the impeller 501 by the bearing housing 603).
  • the fixing means for fixing the bearing housing 603 to the impeller 51 and the fixing means for fixing each outer ring portion 62 to the bearing housing 603 are not limited to the press-fitting described above. As these fixing means, instead of press-fitting, other means such as adhesion may be employed.
  • the bearing housing 603 has a spacer portion 603a interposed between the outer ring portion 62 of the first bearing 601 and the outer ring portion 62 of the second bearing 602.
  • the spacer portion 603a has a shape that protrudes radially inward from a portion of the inner peripheral surface of the bearing housing 603 adjacent to the spacer portion 603a.
  • the spacer portion 603a has, for example, a ring shape extending in the circumferential direction.
  • the outer ring portion 62 of the first bearing 601 is restricted from moving to the second bearing 602 side (rear B), and the outer ring portion 62 of the second bearing 602 is Movement to the one bearing 601 side (forward F) is restricted.
  • a predetermined gap is secured between the outer ring portion 62 of the first bearing 601 and the outer ring portion 62 of the second bearing 602.
  • the size of the gap (the thickness of the spacer portion 603a) is a state before the preload member 604 described above is disposed between the first bearing 601 and the second bearing 602 (a state in which no external force is applied to the preload member 604). ) Is smaller than the height of the preload member 604.
  • the rear end of the inner ring portion 61 in the second bearing 602 is in contact with the step surface 82a of the outer shaft portion 86. Thereby, the movement to the back B of the inner ring
  • wheel part 61 is controlled.
  • a washer 71 is in contact with the front end of the inner ring portion 61 of the first bearing 601.
  • the bolt B2 is screwed into a screw hole (not shown) provided at the front end of the outer shaft portion 86. Thereby, the movement of each inner ring portion 61 to the front F and the rotation of each inner ring portion 61 with respect to the outer peripheral surface of the tip end portion 81 are restricted.
  • the inner ring part 61 of the first bearing 601 and the inner ring part 61 of the second bearing 602 are fixed to the outer shaft part 86 of the non-rotating shaft 80 by being sandwiched between the step surface 82 a and the washer 71.
  • the bolt B2 is screwed into the screw hole as described above. Then, a force is applied by the washer 71 to the inner ring portion 61 of the first bearing 601 on the inner ring portion 61 side of the second bearing 602. Accordingly, the preload member 604 is elastically deformed in a direction in which the height of the preload member 604 interposed between the inner ring portion 61 of the first bearing 601 and the inner ring portion 61 of the second bearing 602 is reduced.
  • a preload (reaction force) is applied to each inner ring portion 61 by the preload member 604 on the outer side in the axial direction (direction of the axis A).
  • the preload member 604 is provided for the purpose of preventing rattling of the rolling part 63 during rotation of the impeller 51 and improving the durability of the bearing part 60.
  • the center of gravity 51G of the impeller 51 is located within the range 60S of the bearing portion 60. That is, the center of gravity 51G is located between the front end 60F and the rear end 60B of the bearing portion 60 in the direction of the axis A, and is located radially inward from the outer peripheral surface 60P of the bearing portion 60.
  • the front end 60F of the bearing portion 60 is the foremost portion of the bearing housing 603
  • the rear end 60B of the bearing portion 60 is the rearmost portion of the bearing housing 603
  • the outer peripheral surface 60P of the bearing portion 60 These are the outer peripheral surfaces of the bearing housing 603.
  • the center of gravity 51G of the impeller 51 is preferably located between the foremost part of the first bearing 601 and the rearmost part of the second bearing 602. Further, the center of gravity 51G of the impeller 51 is more preferably located on the radially inner side than the inner ring portion 61, and more preferably on the axis A.
  • the bearing portion 60 includes a bearing housing 603, when assembling the blower 13A, a bearing component in which the first bearing 601, the second bearing 602, the bearing housing 603, and the preload member 604 are integrated in advance.
  • the work procedure of attaching the assembled part to the non-rotating shaft 80 fixed to the stator can be adopted after press-fitting into the recess provided in the hub 53 of the impeller 51. Therefore, the working efficiency of the assembly work is excellent, and the impeller can be easily detached.
  • the bearing portion 60 is disposed between the outer shaft portion 86 located on the outer side in the axial direction of the stator 43 and the impeller 51, and the impeller 51
  • the center of gravity 51G is positioned within the range 60S of the bearing portion 60. Therefore, compared to the case where the center of gravity 51G of the impeller 51 and the bearing portion 60 are shifted in the axial direction, the load applied to the bearing portion 60 when the impeller 51 rotates can be reduced. Can be improved.
  • the center of gravity 51G of the impeller 51 is positioned within the range 60S of the bearing portion 60, so that the hub 53 of the impeller 51 does not need to be largely wound around the stator 43.
  • the impeller 51 can be disposed generally near the outer shaft portion 86. Thereby, the restrictions of the shape of the impeller 51 are small compared with the conventional air blower. Therefore, compared to a conventional impeller that employs a shape that greatly encircles the hub 53 around the stator 43, the air flow is less likely to be inhibited inside the impeller 51, and an improvement in fan performance can be expected.
  • the bearing portion 60 is interposed between the outer shaft portion 86 and the impeller 51, so that the bearing portion 60 is provided inside the stator 43 compared to the case where the bearing portion 60 is provided inside the stator 43.
  • the size of the bearing part 60 can be designed to a size corresponding to the durability required for the bearing part (60) without being restricted by the stator 43. Can be improved.
  • the impeller 51 is of a mixed flow type, and the hub 53 of the impeller 51 has an inclined surface 53K that is inclined toward the stator 43 side in the axial direction toward the radially outer side. . That is, in the mixed flow type impeller (51), the surface of the hub 53 is inclined as described above in order to create a flow in a direction inclined with respect to the axial direction. Therefore, in the mixed flow type impeller (51), even if the bearing portion 60 is provided on the outer shaft portion 86 located on the outer side in the axial direction of the stator 43, a relatively large air flow path in the impeller 51 is secured. it can. Therefore, the air flow is less likely to be inhibited in the impeller 51, and the blowing performance can be further improved.
  • the bearing portion 60 since the bearing portion 60 includes a plurality of bearings arranged in the axial direction, durability of the bearing portion 60 is improved as compared with a bearing portion having a single bearing.
  • the durability of the bearing portion 60 can be improved as described above, and the size of the hub 53 of the impeller 51 (axial direction) Can be made as small as possible. That is, since the plurality of bearings are disposed adjacent to each other, the size of the outer shaft portion 86 to which the plurality of bearings are attached can be made as small as possible. Therefore, the size of the hub 53 of the impeller 51 disposed around the outer shaft portion 86 can be reduced as much as possible. This makes it difficult for the air flow to be inhibited inside the impeller 51.
  • the bearing portion 60 since the bearing portion 60 includes a plurality of bearings, the radial size of each bearing can be reduced as compared with the case where the bearing portion is configured by a single bearing. Thereby, the size of the bearing portion 60 in the radial direction can be reduced.
  • the blower 13 In the indoor unit 11 in which the blower 13 is disposed in the case 20 so that the axial direction of the non-rotating shaft 80 is oriented in the horizontal direction, as in the present embodiment and the modification thereof, it is oriented in the direction perpendicular to the axial direction A load caused by gravity is further applied to the bearing portion 60. Therefore, in such an indoor unit 11, the blower 13 of the present embodiment in which the load applied when the impeller 51 rotates is suitable.
  • the bearing portion 60 is interposed between the hub 53 of the impeller 51 and the outer shaft portion 86 of the non-rotating shaft 80 is illustrated, but the present invention is not limited thereto.
  • a structure in which the bearing portion 60 is interposed between the outer shaft portion 86 of the non-rotating shaft 80 and the rotor 45 may be employed.
  • the blower 13 is arranged in the case 20 so that the direction of the axis A of the non-rotating shaft 80 is in the horizontal direction (front-rear direction) is illustrated, but the present invention is not limited to this.
  • the blower 13 may be arranged such that the direction of the axis A is directed in the vertical direction, for example, like a ceiling-embedded indoor unit.
  • the bearing portion 60 includes the first bearing 601, the second bearing 602, the bearing housing 603, and the preload member 604 is illustrated, but the present invention is not limited thereto.
  • the bearing portion 60 including the first bearing 601 and the second bearing 602 one or both of the bearing housing 603 and the preload member 604 may be omitted.
  • the outer ring portion 62 of the first bearing 601 and the outer ring portion 62 of the second bearing 602 are directly connected to the hub 53 of the impeller 51 without passing through the bearing housing 603.
  • the fixed form can be illustrated.
  • the inner ring portion 61 of the first bearing 601 may be disposed so as to be in contact with the inner ring portion 61 of the second bearing 602.
  • the spacer portion 603a of the bearing housing 603 can be omitted.
  • blower 13 is a mixed flow blower
  • the blower 13 may be a centrifugal blower provided with a centrifugal impeller.
  • the blower includes an outer rotor type motor (49) having a stator (43), a rotor (45) and a non-rotating shaft (80), and a centrifugal or mixed flow type fixed to the rotor (45).
  • the non-rotating shaft (80) has an outer shaft portion (86) positioned on the outer side in the axial direction than the stator (43).
  • the bearing portion (60) is interposed between the outer shaft portion (86) and the impeller (51) or the rotor (45).
  • the center of gravity (51G) of the impeller (51) is located within the range (60S) of the bearing portion (60).
  • the bearing portion (60) is disposed between the outer shaft portion (86) located on the outer side in the axial direction of the stator (43) and the impeller (51) or the rotor (45), and the blade
  • the center of gravity (51G) of the vehicle (51) is positioned within the range (60S) of the bearing portion (60). Therefore, compared to the case where the center of gravity (51G) of the impeller (51) and the bearing portion (60) are shifted in the axial direction, the load applied to the bearing portion (60) when the impeller (51) rotates is reduced. Since it can reduce, durability of an air blower can be improved.
  • the hub (53) of the impeller (51) does not need to be largely wound around the stator (43), and the center of gravity (51G) of the impeller (51) is within the range of the bearing portion (60) (60S ),
  • the impeller (51) can be disposed close to the outer shaft portion (86) as a whole.
  • the restriction on the shape of the impeller (51) is smaller than that of the conventional blower. Therefore, compared to a conventional impeller that adopts a shape in which the hub is greatly wound around the stator (a shape in which the hub surrounds not only the front portion around the stator but also the rear portion around the stator), the blade The air flow is less likely to be obstructed inside the car (51), and fan performance can be expected to improve.
  • the bearing portion (60) is interposed between the outer shaft portion (86) and the impeller (51) or the rotor (45), the bearing portion (60) is provided in the stator (43).
  • the size of the bearing portion (60) can be designed in accordance with the durability required for the bearing part (60) without being restricted by the stator (43). Can be improved.
  • the bearing part (60) is fixed to the first wheel part (61) fixed to the outer shaft part (86) and the impeller (51),
  • the form which has the 2nd ring part (62) rotatable with respect to the 1st ring part (61) can be illustrated.
  • the impeller (51) is fixed to the second wheel portion (62), and is inclined toward the stator (43) in the axial direction toward the radially outer side.
  • a mixed flow type impeller (51) having a hub (53) having a surface (53K) and a plurality of blades (55) fixed to the hub (53) and arranged in the circumferential direction. preferable.
  • the impeller (51) is a mixed flow type, and the hub (53) of the impeller (51) has an inclined surface (53K) inclined toward the stator (43) in the axial direction toward the radially outer side. )have. That is, in the mixed flow type impeller (51), the surface of the hub (53) is inclined as described above in order to create a flow in a direction inclined with respect to the axial direction. Therefore, in the mixed flow type impeller (51), even if the bearing portion (60) is provided on the outer shaft portion (86) located on the outer side in the axial direction of the stator (43), A relatively large air flow path can be secured. Therefore, the air flow is less likely to be inhibited in the impeller (51), and the air blowing performance can be further improved.
  • the bearing portion (60) includes a plurality of bearings arranged in the axial direction.
  • the durability of the bearing portion (60) is improved as compared with a bearing portion having a single bearing.
  • the plurality of bearings are arranged adjacent to each other.
  • the durability of the bearing portion (60) can be improved as described in (4) above, and the impeller (51) can be improved.
  • the size (axial size) of the hub (53) can be made as small as possible. That is, since the plurality of bearings are arranged adjacent to each other, the size of the outer shaft portion (86) to which the plurality of bearings are attached can be minimized. Therefore, the size of the hub (53) of the impeller (51) arranged around the outer shaft portion (86) can be reduced as much as possible. This makes it difficult for the air flow to be inhibited inside the impeller (51).
  • the air conditioner includes the blower (13) and a case (20) that houses the blower (13).
  • the blower (13) has an axial direction of the non-rotating shaft (80). It arrange
  • Air conditioner indoor unit 13 Blower 20 cases 43 Stator 45 rotor 49 Motor 51 impeller 51G Impeller center of gravity 53 Hub 54 Shroud 55 feathers 60 Bearing part 601 1st bearing 602 2nd bearing 61 Inner ring 62 Outer ring 80 Non-rotating shaft 86 Outer shaft 87 Inner shaft A axis

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

Un ventilateur (13) comporte : un moteur du type à rotor externe (49) comprenant un stator (43), un rotor (45) et un arbre non rotatif (80) ; une turbine à flux centrifuge ou diagonal (51) fixée au rotor (45) ; et une partie palier (60) qui supporte la turbine (51) ou le rotor (45) de sorte que la turbine (51) puisse entrer en rotation autour de l'arbre non rotatif (80). L'arbre non rotatif (80) comprend une partie arbre extérieur (86) située plus loin vers l'extérieur que le stator (43) dans la direction axiale. La partie palier (60) est interposée entre la partie arbre extérieur (86) et la turbine (51) ou le rotor (45). Le centre de gravité (51G) de la turbine (51) est situé à l'intérieur de la plage (60S) de la partie palier (60).
PCT/JP2012/003706 2011-06-09 2012-06-06 Ventilateur et climatiseur WO2012169183A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011129385 2011-06-09
JP2011-129385 2011-06-09
JP2012121053A JP5267703B2 (ja) 2011-06-09 2012-05-28 送風機及び空気調和機
JP2012-121053 2012-05-28

Publications (1)

Publication Number Publication Date
WO2012169183A1 true WO2012169183A1 (fr) 2012-12-13

Family

ID=47295768

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/003706 WO2012169183A1 (fr) 2011-06-09 2012-06-06 Ventilateur et climatiseur

Country Status (2)

Country Link
JP (1) JP5267703B2 (fr)
WO (1) WO2012169183A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110013716A (zh) * 2019-05-21 2019-07-16 陶业光 一种水洗装置及其空气净化器
US11608832B2 (en) * 2017-10-23 2023-03-21 Lg Electronics Inc. Rotary drive for an impeller and motor assembly with gas and rolling bearings arranged in housing structure

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5862095B2 (ja) * 2011-08-01 2016-02-16 ダイキン工業株式会社 空気調和装置の室外機
WO2021255917A1 (fr) * 2020-06-19 2021-12-23 三菱電機株式会社 Unité intérieure de climatiseur

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5877189U (ja) * 1981-11-20 1983-05-25 西部電機工業株式会社 ランナ−ハブ部にモ−タ−を内蔵する斜流フアン
JP2005256705A (ja) * 2004-03-11 2005-09-22 Nippon Densan Corp 細長遠心ファン
JP2006188966A (ja) * 2004-12-28 2006-07-20 Nippon Densan Corp 小型遠心ファン
JP2009281215A (ja) * 2008-05-21 2009-12-03 Daikin Ind Ltd 空気調和機用室内機

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3426151B2 (ja) * 1998-03-16 2003-07-14 アスモ株式会社 ブラシレスモータ
JP2002106493A (ja) * 2000-09-29 2002-04-10 Toshiba Corp 送風機
JP2007154775A (ja) * 2005-12-06 2007-06-21 Nidec Copal Electronics Corp 送風機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5877189U (ja) * 1981-11-20 1983-05-25 西部電機工業株式会社 ランナ−ハブ部にモ−タ−を内蔵する斜流フアン
JP2005256705A (ja) * 2004-03-11 2005-09-22 Nippon Densan Corp 細長遠心ファン
JP2006188966A (ja) * 2004-12-28 2006-07-20 Nippon Densan Corp 小型遠心ファン
JP2009281215A (ja) * 2008-05-21 2009-12-03 Daikin Ind Ltd 空気調和機用室内機

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11608832B2 (en) * 2017-10-23 2023-03-21 Lg Electronics Inc. Rotary drive for an impeller and motor assembly with gas and rolling bearings arranged in housing structure
CN110013716A (zh) * 2019-05-21 2019-07-16 陶业光 一种水洗装置及其空气净化器
CN110013716B (zh) * 2019-05-21 2024-04-19 陶业光 一种水洗装置及其空气净化器

Also Published As

Publication number Publication date
JP5267703B2 (ja) 2013-08-21
JP2013015135A (ja) 2013-01-24

Similar Documents

Publication Publication Date Title
US9254742B2 (en) Grille shutter
JP4432474B2 (ja) 遠心送風機の羽根車及びそれを備えた遠心送風機
JP4337669B2 (ja) 車両用電動送風ファン装置
JP5267703B2 (ja) 送風機及び空気調和機
JP2014058966A (ja) 熱交換器のためのファンモジュール
JP2012510245A5 (fr)
JP6292241B2 (ja) 遠心ファン
JP6620427B2 (ja) 送風機
US20150337855A1 (en) Installation structure for drive motor of double suction blower
US20090175745A1 (en) Blower Unit for Vehicle
WO2014132526A1 (fr) Machine à fluide de type à spirale
US9045037B2 (en) Ventilation assembly
JP6840243B2 (ja) 電動送風機、電気掃除機、及び手乾燥装置
JP2005127311A (ja) 遠心送風機及びこれを用いた空気調和機
JP6697803B2 (ja) 流体式ファンクラッチ
JP4423919B2 (ja) 遠心送風機及びこれを用いた空気調和機
JP2006188991A (ja) 送風機
JP4176943B2 (ja) 自動車用送風装置
JP6687050B2 (ja) 遠心送風機
JP6181908B2 (ja) ブロワ
JP2007303286A (ja) 車両用二重反転式送風機
JP6793803B1 (ja) 遠心送風機
JP2009191760A (ja) 車両用送風装置
US20240175389A1 (en) Cooling module for an electric or hybrid motor vehicle, having a tangential-flow turbomachine
JP5724380B2 (ja) 軸流ファン

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12796412

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12796412

Country of ref document: EP

Kind code of ref document: A1