WO2019150567A1 - Ventilateur à écoulement axial - Google Patents

Ventilateur à écoulement axial Download PDF

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Publication number
WO2019150567A1
WO2019150567A1 PCT/JP2018/003704 JP2018003704W WO2019150567A1 WO 2019150567 A1 WO2019150567 A1 WO 2019150567A1 JP 2018003704 W JP2018003704 W JP 2018003704W WO 2019150567 A1 WO2019150567 A1 WO 2019150567A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
curved surface
airflow
bell mouth
axial
Prior art date
Application number
PCT/JP2018/003704
Other languages
English (en)
Japanese (ja)
Inventor
新井　俊勝
菊地　仁
千景 門井
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2019568534A priority Critical patent/JP6914371B2/ja
Priority to PCT/JP2018/003704 priority patent/WO2019150567A1/fr
Priority to US16/962,594 priority patent/US20200408225A1/en
Priority to CN201880087838.5A priority patent/CN111656019B/zh
Priority to TW107119335A priority patent/TW201934888A/zh
Publication of WO2019150567A1 publication Critical patent/WO2019150567A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to an axial blower that generates an airflow that flows in the axial direction of a rotating shaft.
  • Axial fans are often installed in places close to living spaces, and noise reduction is required.
  • a bell mouth is provided around the rotor blades of the axial flow fan so that air can be smoothly sucked into the rotor blades.
  • the shape of the bell mouth affects the air blowing performance and noise characteristics of the axial blower. Therefore, as disclosed in Patent Document 1, by improving the shape of the bell mouth, the air blowing performance and quietness of the axial blower are improved.
  • the ventilation performance and noise characteristics of an axial blower are greatly affected not only by the shape of the rotor blades but also by the shape of the bell mouth.
  • the shape is designed. However, if the rotor blade and the bell mouth are individually designed, there may be cases where the ideal shape is not necessarily obtained in terms of air blowing performance and noise characteristics due to dimensional constraints.
  • the present invention has been made in view of the above, and an object of the present invention is to obtain an axial blower that improves the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
  • the present invention provides a rotating blade provided with a plurality of blades, a motor that generates airflow by rotating the rotating blade, and a direction orthogonal to the rotation axis of the rotating blade. And a frame-shaped bell mouth surrounding the rotor blade.
  • the bell mouth has a suction curved surface that becomes narrower toward the downstream side of the airflow in the axial direction of the rotation axis on the upstream side of the airflow.
  • the axial blower according to the present invention has an effect of improving the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
  • FIG. 1 The perspective view of the rotary blade of the axial blower which concerns on Embodiment 1 of this invention
  • FIG. Front view of axial blower according to Embodiment 1 Sectional drawing of the axial blower which concerns on Embodiment 1.
  • FIG. The top view which shows the shape of the blade of the axial blower which concerns on Embodiment 1.
  • the figure which shows the relationship between the ratio of the cut length of the suction curved surface of the bell mouth of the axial flow fan which concerns on Embodiment 1, and the curvature radius of the suction curved surface of the bell mouth, and the noise level of the front noise in an open point The relationship between the cut length of the bellmouth suction curved surface of the axial flow fan according to Embodiment 1 and the radius of curvature of the bellmouth suction curved surface and the noise level of the noise in the oblique 45 ° direction at the open point is shown.
  • Figure 1 which shows the relationship between the air volume and static pressure of the axial-flow fan which concerns on Embodiment 1 for every ratio of the curvature radius of the suction surface of a bellmouth, and the outer diameter of a rotary blade.
  • FIG. 1 is a perspective view of a rotor blade of an axial blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a diagram illustrating a positional relationship between the rotor blades and the bell mouth of the axial blower according to the first embodiment.
  • the rotary blade 1 according to Embodiment 1 includes a cylindrical boss 2 and three blades 1 a attached to the boss 2. In the following description, the shape of one of the three blades 1a will be mainly described, but the three blades 1a have the same shape.
  • the blade 1a has a three-dimensional shape.
  • the blades 1a are radially attached to the outer periphery of the boss 2.
  • the boss 2 is rotationally driven around the rotation axis AX by the motor 3.
  • the blade 1a rotates in the arrow S direction together with the boss 2 to generate an airflow that flows in the arrow A direction.
  • Rotating blade 1 is installed at the center of blower body 6 including bell mouth 5.
  • the blower main body 6 has a frame shape, and the outer shape in front view is a square.
  • the motor 3 is disposed on the downstream side of the airflow with respect to the bell mouth 5.
  • the motor 3 may be disposed upstream of the airflow with respect to the bell mouth 5.
  • FIG. 3 is a front view of the axial blower according to the first embodiment.
  • FIG. 4 is a cross-sectional view of the axial blower according to the first embodiment.
  • the blade 1a is shown in a meridian shape.
  • the bell mouth 5 has a suction curved surface 51, a straight portion 53, and a discharge curved surface 52.
  • the suction curved surface 51 is located on the upstream side of the airflow, and the flow path is narrower toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the discharge curved surface 52 is located on the downstream side of the airflow, and the flow path becomes wider toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the radius of curvature R1 of the suction curved surface 51 is larger than the radius of curvature R2 of the discharge curved surface 52.
  • the axial flow fan 10 is installed. Considering the characteristics and manufacturing cost, it is designed so that DR1 ⁇ L.
  • the suction curved surface 51 is formed as large as possible within the range of the length L of one side of the outer shape of the blower body 6 when viewed from the front, so that airflow is smoothly induced in the rotary blade 1.
  • Rotating blade 1 of axial blower 10 according to Embodiment 1 has an outer diameter D of 260 mm.
  • the outer peripheral trailing edge I of the rotor blade 1 is located near the boundary between the straight portion 53 of the bell mouth 5 and the discharge curved surface 52. Further, the blade leading edge portion 1 b and the blade outer edge portion 1 d of the rotor blade 1 protrude from the suction curved surface 51 of the bell mouth 5 to the upstream side of the airflow.
  • the straight part 53 prevents air from flowing backward when static pressure is applied.
  • the discharge curved surface 52 allows the flow in the centrifugal direction included in the air flow flowing out from the rotor blade 1 to smoothly flow out of the rotor blade 1. Further, the discharge curved surface 52 also serves as a diffuser that increases the static pressure.
  • the outer diameter D of the rotary blade 1 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 satisfy the relationship of R1 / D ⁇ 0.05. Further, the outer diameter DR1 ′ of the suction curved surface 51 of the bell mouth 5 when the suction curved surface 51 is extended until the tangent TL at the upstream end 51a of the suction curved surface 51 of the bell mouth 5 becomes perpendicular to the rotation axis AX, and the bell mouth When the difference from the outer diameter DR1 of the suction curved surface 51 of 5 is R1 ′, the relationship 0 ⁇ R1 ′ / R1 ⁇ 0.505 is satisfied.
  • the suction curved surface 51 of the bell mouth 5 of the axial flow fan 10 according to the first embodiment has a shape obtained by removing the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ of the outer diameter DR1 ′, and the outer diameter is DR1.
  • the axial flow fan 10 according to the first embodiment removes the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ having the outer diameter DR1 ′, so that the outer diameter of the suction curved surface 51 of the bell mouth 5 is DR1. It can be considered that.
  • the portion considered to be removed from the suction curved surface 51 ′ having the outer diameter of DR 1 ′ is referred to as a cut portion.
  • the length of the cut part is called the cut length. Therefore, in Embodiment 1, the cut length is R1 '.
  • the outer diameter DR1 of the suction curved surface 51 of the bell mouth 5 is smaller than the length L of one side of the blower body 6. .
  • the bell mouth 5 can increase the radius of curvature R1 of the suction curved surface 51 and can be smaller than the outer shape of the blower body 6 in front view. .
  • FIG. 5 is a plan view showing the shape of the blade of the axial blower according to the first embodiment.
  • FIG. 6 is a cross-sectional view of the blade of the axial blower according to the first embodiment.
  • FIG. 6 shows a blade cross section of the blade 1a in a plane along a plane passing through the rotation axis AX and the blade inner edge 1e.
  • the blade 1a has an inflection point IP between the outer peripheral side and the inner peripheral side in the blade cross section passing through the rotation axis AX and the blade inner edge 1e.
  • the blade 1a has a blade cross-section convex toward the upstream side of the airflow on the inner peripheral side closer to the boss 2 than the inflection point IP, and on the downstream side of the airflow on the outer peripheral side farther from the boss 2 than the inflection point IP. It is a convex wing cross section.
  • the curvature of the blade cross section on the inner peripheral side from the inflection point IP is R1b.
  • the curvature of the blade cross section on the outer peripheral side from the inflection point IP is R2b.
  • the curvature radii R1b and R2b of the blade 1a continuously change from the blade leading edge 1b to the blade trailing edge 1c.
  • FIG. 7 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position O-D1 in FIG.
  • FIG. 8 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD2 in FIG.
  • FIG. 9 shows a blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-sectional position O-D3 in FIG.
  • the blade 1a shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD4 in FIG.
  • the blade 1a is inclined at the blade cross-sectional position O-D1 by ⁇ (O-D1) on the upstream side of the airflow.
  • the blade 1a has an inclination angle ⁇ (O-D2) at the blade cross-section position O-D2 and the blade cross-section position.
  • the inclination angle ⁇ (O-D3) at O-D3 and the inclination angle ⁇ (O-D4) at the blade cross-sectional position O-D4 are inclined so as to incline toward the downstream side of the airflow as they approach the blade trailing edge 1c. Has changed.
  • the blade 1a has a blade cross section with the inner peripheral side away from the boss 2 near the front in the rotational direction.
  • a blade tip vortex 7 is formed due to the pressure difference between the pressure surface and the suction surface of the blade 1a.
  • the blade tip vortex 7 interferes with the suction surface of the blade 1a, another blade 1a adjacent to the blade 1a or the bell mouth 5, the noise characteristics of the axial blower 10 deteriorate. Since the blade 1a has an S-shaped blade cross section that is convex on the upstream side of the airflow on the inner peripheral side and convex on the downstream side of the airflow on the outer peripheral side, the generation of the blade vortex 7 is suppressed, It is possible to prevent leakage from the rotor 1.
  • FIG. 11 is a diagram showing the relationship between the blade cross-sectional position and the radius of curvature of the blade of the axial blower according to the first embodiment.
  • the radius of curvature R1b on the inner peripheral side of the blade 1a gradually decreases from the blade leading edge 1b toward the blade trailing edge 1c.
  • the radius of curvature R2b on the outer peripheral side of the blade 1a gradually decreases from the blade leading edge 1b to the blade cross-sectional position O-D3, and gradually increases from the blade cross-sectional position O-D3 to the blade trailing edge 1c.
  • FIG. 12 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blades and the air volume at the open point where the static pressure becomes zero. is there.
  • the air volume is normalized so that the air volume at the open point is 100%.
  • the air volume tends to increase as the ratio R1 / D between the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases.
  • FIG. 13 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade and the noise level of the front noise at the open point.
  • the noise level is normalized so that the noise level at the open point is 0 dB.
  • the ratio R1 / D of the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases, the noise level of the front noise decreases, but unlike the air volume, the noise is reduced to a certain level.
  • the noise level of the front noise hardly changes even if R1 / D increases.
  • FIG. 14 shows the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade, and the noise level of the noise in the oblique 45 ° direction at the open point.
  • the noise level is normalized so that the noise level at the open point becomes 0 dB. Similar to the noise level of the front noise, the noise level decreases as R1 / D increases. However, the noise level of the 45 ° diagonal noise at the open point is different from the noise level of the front noise in that it does not stop at a certain level.
  • FIG. 15 is a graph showing the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the air volume at the open point.
  • the airflow is normalized so that the airflow at the open point becomes 100%.
  • the ratio R1 ′ / R1 between the cut length R1 ′ of the suction curved surface 51 of the bell mouth 5 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 is 0.45 or less
  • the air volume is R1 ′. It does not depend on / R1.
  • R1 '/ R1 exceeds 0.45, the air volume rapidly decreases.
  • FIG. 16 shows the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth and the noise level of the front noise at the open point.
  • the noise level is normalized so that the noise level at the open point is 0 dB.
  • R1 '/ R1 is 0.45 or less
  • the noise level of the front noise decreases.
  • R1 '/ R1 exceeds 0.5
  • FIG. 17 shows the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the noise level of the oblique 45 ° direction noise at the open point. It is a figure which shows the relationship.
  • FIG. 18 is a diagram showing the relationship between the air volume and static pressure of the axial blower according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 19 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 20 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the oblique noise according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 21 is a diagram showing the relationship between the air volume and static pressure of the axial flow fan according to Embodiment 1 for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface.
  • FIG. 22 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface. It is.
  • FIG. 24 is a diagram showing the difference in the relationship between the air volume and the static pressure due to the difference in the curvature radius of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment.
  • FIG. 25 is a diagram illustrating a difference in the relationship between the air volume and the noise level of the front noise due to the difference in the radius of curvature of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment.
  • FIG. 26 is a diagram illustrating the difference in the relationship between the air volume and the noise level of the oblique noise due to the difference in the radius of curvature of the suction surface of the bell mouth of the axial flow fan according to the first embodiment.
  • R1 1 > R1 2 .
  • the suction of the bell mouth 5 is performed. It can suppress that the disturbance of the airflow which generate
  • the outer diameter of the suction curved surface 51 of the bell mouth 5 is equal to or less than the length of one side of the blower body 6, it is not necessary to assemble the bell mouth 5 separated from the blower body 6 with the blower body 6. An increase in man-hours can be prevented.
  • the configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

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

Abstract

L'invention concerne un ventilateur à écoulement axial (10), lequel ventilateur a : une hélice qui comporte une pluralité de pales ; un moteur (3) qui fait tourner l'hélice de façon à générer un écoulement d'air ; et une embouchure en cloche en forme de cadre qui entoure l'hélice à partir d'une direction perpendiculaire à l'arbre rotatif de l'hélice. L'embouchure en cloche a une surface incurvée d'aspiration (51) qui est disposée sur le côté amont par rapport à l'écoulement d'air, et qui, dans la direction de l'axe de l'arbre rotatif, se rétrécit vers le côté aval par rapport à l'écoulement d'air. Si le diamètre de l'hélice est D, et que le rayon de courbure de la surface incurvée d'aspiration (51) est R1, alors, la relation R1/D ≤ 0,05 est satisfaite.
PCT/JP2018/003704 2018-02-02 2018-02-02 Ventilateur à écoulement axial WO2019150567A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2019568534A JP6914371B2 (ja) 2018-02-02 2018-02-02 軸流送風機
PCT/JP2018/003704 WO2019150567A1 (fr) 2018-02-02 2018-02-02 Ventilateur à écoulement axial
US16/962,594 US20200408225A1 (en) 2018-02-02 2018-02-02 Axial blower
CN201880087838.5A CN111656019B (zh) 2018-02-02 2018-02-02 轴流送风机
TW107119335A TW201934888A (zh) 2018-02-02 2018-06-05 軸流風扇

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/003704 WO2019150567A1 (fr) 2018-02-02 2018-02-02 Ventilateur à écoulement axial

Publications (1)

Publication Number Publication Date
WO2019150567A1 true WO2019150567A1 (fr) 2019-08-08

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Application Number Title Priority Date Filing Date
PCT/JP2018/003704 WO2019150567A1 (fr) 2018-02-02 2018-02-02 Ventilateur à écoulement axial

Country Status (5)

Country Link
US (1) US20200408225A1 (fr)
JP (1) JP6914371B2 (fr)
CN (1) CN111656019B (fr)
TW (1) TW201934888A (fr)
WO (1) WO2019150567A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022191034A1 (fr) * 2021-03-12 2022-09-15 ダイキン工業株式会社 Ventilateur hélicoïdal et dispositif de réfrigération
EP4023891A4 (fr) * 2019-08-26 2022-10-19 Daikin Industries, Ltd. Dispositif de soufflage et ensemble pompe à chaleur
EP4123185A1 (fr) * 2021-07-20 2023-01-25 Sanyo Denki Co., Ltd. Ventilateur axial

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Publication number Priority date Publication date Assignee Title
WO2019214632A1 (fr) * 2018-05-09 2019-11-14 约克广州空调冷冻设备有限公司 Pale et turbine à flux axial utilisant celle-ci
CN113847275B (zh) * 2021-08-30 2023-06-16 珠海格力电器股份有限公司 翼型轴流风叶及空调外机
CN116025577A (zh) * 2023-01-05 2023-04-28 合肥华凌股份有限公司 支架组件、风机及冰箱

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JP2009275524A (ja) * 2008-05-12 2009-11-26 Mitsubishi Electric Corp 軸流送風機
JP2012233420A (ja) * 2011-04-28 2012-11-29 Mitsubishi Electric Corp 送風機
JP2017223173A (ja) * 2016-06-16 2017-12-21 三菱電機株式会社 送風機および冷凍サイクル装置の室外機

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JP4190683B2 (ja) * 1999-11-22 2008-12-03 株式会社小松製作所 ファン装置
JP6215296B2 (ja) * 2013-02-22 2017-10-18 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド プロペラファン及びこれを備えた空気調和機
JP6218862B2 (ja) * 2014-02-14 2017-10-25 三菱電機株式会社 軸流送風機
MY189574A (en) * 2016-06-16 2022-02-17 Mitsubishi Electric Corp Impeller and axial flow fan

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Publication number Priority date Publication date Assignee Title
JP2009275524A (ja) * 2008-05-12 2009-11-26 Mitsubishi Electric Corp 軸流送風機
JP2012233420A (ja) * 2011-04-28 2012-11-29 Mitsubishi Electric Corp 送風機
JP2017223173A (ja) * 2016-06-16 2017-12-21 三菱電機株式会社 送風機および冷凍サイクル装置の室外機

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4023891A4 (fr) * 2019-08-26 2022-10-19 Daikin Industries, Ltd. Dispositif de soufflage et ensemble pompe à chaleur
WO2022191034A1 (fr) * 2021-03-12 2022-09-15 ダイキン工業株式会社 Ventilateur hélicoïdal et dispositif de réfrigération
JP2022140336A (ja) * 2021-03-12 2022-09-26 ダイキン工業株式会社 プロペラファンおよび冷凍装置
EP4123185A1 (fr) * 2021-07-20 2023-01-25 Sanyo Denki Co., Ltd. Ventilateur axial
US11933315B2 (en) 2021-07-20 2024-03-19 Sanyo Denki Co., Ltd. Axial fan

Also Published As

Publication number Publication date
JP6914371B2 (ja) 2021-08-04
CN111656019A (zh) 2020-09-11
TW201934888A (zh) 2019-09-01
CN111656019B (zh) 2022-05-17
US20200408225A1 (en) 2020-12-31
JPWO2019150567A1 (ja) 2020-07-02

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