WO2020110167A1 - Impulseur et ventilateur à flux axial - Google Patents

Impulseur et ventilateur à flux axial Download PDF

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Publication number
WO2020110167A1
WO2020110167A1 PCT/JP2018/043355 JP2018043355W WO2020110167A1 WO 2020110167 A1 WO2020110167 A1 WO 2020110167A1 JP 2018043355 W JP2018043355 W JP 2018043355W WO 2020110167 A1 WO2020110167 A1 WO 2020110167A1
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WO
WIPO (PCT)
Prior art keywords
impeller
blade
angle
traveling direction
tangent line
Prior art date
Application number
PCT/JP2018/043355
Other languages
English (en)
Japanese (ja)
Inventor
新井　俊勝
青木　普道
樹司 村上
侑也 向坂
一樹 蓮池
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 CN201880099511.XA priority Critical patent/CN113039366B/zh
Priority to PCT/JP2018/043355 priority patent/WO2020110167A1/fr
Priority to JP2020557411A priority patent/JPWO2020110167A1/ja
Priority to TW108114283A priority patent/TWI742364B/zh
Publication of WO2020110167A1 publication Critical patent/WO2020110167A1/fr
Priority to JP2022044255A priority patent/JP2022075846A/ja

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    • 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

Definitions

  • the present invention relates to an impeller and an axial-flow blower that generate an air flow that flows in the direction of a rotation axis.
  • Patent Document 1 discloses an impeller in which the planar shape of the blade when the blade is projected on a plane perpendicular to the rotation axis is such that the chord centerline is advanced in the traveling direction of the blade due to the rotation of the impeller. It is disclosed.
  • the chord center line is a line connecting the centers of the chord lines. To move the chord centerline forward in the traveling direction means that the chord centerline is curved forward in the traveling direction as it moves away from the rotation axis.
  • the present invention has been made in view of the above, and an object thereof is to obtain an impeller that can reduce noise and stress concentration.
  • an impeller according to the present invention includes a boss portion rotatable about a rotation axis and a blade extending radially from the boss portion.
  • the blade leading edge of the outer edge of the blade which is directed toward the traveling direction of the blade due to the rotation of the boss, is opposite to the traveling direction.
  • Has a third bending portion which is provided on the opposite side and bends in the traveling direction.
  • the impeller according to the present invention has an effect of reducing noise and stress concentration.
  • the figure which shows the plane shape of the impeller shown in FIG. The figure which shows the plane shape of a wing and a boss part among the impellers shown in FIG.
  • the figure explaining the state of the air flow around the wing shown in FIG. The figure explaining the relationship between the shape of the wing shown in FIG. 3, and the strength of the wing.
  • the top view which shows the suction side of the impeller shown in FIG. The top view which shows the pressure side of the impeller shown in FIG.
  • FIG. 1 is a diagram showing a schematic configuration of an axial blower 10 having an impeller 11 according to a first embodiment of the present invention.
  • the axial blower 10 is used for cooling a fan, a ventilation fan, an air conditioner, or equipment.
  • the axial blower 10 has an impeller 11 that can generate an airflow by rotation, and a motor 12 that rotationally drives the impeller 11.
  • the axial blower 10 also has a housing that houses the impeller 11 in a rotatable manner.
  • the motor 12 is held in the housing.
  • the housing has an opening through which the airflow generated by the rotation of the impeller 11 passes. At the edge of the opening, a bell mouth is provided whose diameter is expanded toward the upstream side of the air flow. In FIG. 1, the illustration of the housing and the bell mouth is omitted.
  • the impeller 11 has a spider 5 that is molded from one plate material, and three curved plates 3 that are joined to the spider 5.
  • the spider 5 has a boss portion 2 that is a main plate portion located at the center of the spider 5, and three mounting portions 4 provided around the boss portion 2.
  • the boss portion 2 is connected to the motor 12, and when the motor 12 is driven, the boss portion 2 rotates in the rotation direction C about the rotation shaft 6.
  • Each of the curved plates 3 constitutes the wing 1.
  • the curved plate 3 is formed by pressing a sheet metal.
  • the curved plate 3 is attached to each of the mounting portions 4, and is joined to the end portion of the mounting portion 4 on the side opposite to the rotating shaft 6.
  • the mounting portion 4 corresponds to a root portion of the wing 1 on the boss portion 2 side.
  • the curved plate 3 is joined to the mounting portion 4 by welding or using rivets.
  • the impeller 11 has the boss portion 2 rotatable about the rotation axis 6 and the three blades 1 radially extending from the boss portion 2.
  • Each wing 1 includes a curved plate 3 and a mounting portion 4.
  • the blade 1 has a curved surface shape in which the portion on the side opposite to the rotating shaft 6 is inclined toward the upstream side of the air flow.
  • the rotation of the impeller 11 in the rotation direction C causes the axial blower 10 to generate an airflow flowing in the direction of arrow A, which is a direction parallel to the rotation axis 6.
  • the impeller 11 is not limited to the one composed of the spider 5 and the curved plate 3, and may have the cylindrical boss portion 2 and the wing 1 attached to the boss portion 2.
  • the number of blades 1 provided in the impeller 11 is not limited to three and may be arbitrary.
  • Each of the blades 1 provided on the impeller 11 has a similar three-dimensional solid shape. The description of the blade 1 described below is common to each of the blades 1 provided in the impeller 11.
  • FIG. 2 is a diagram showing a planar shape of the impeller 11 shown in FIG.
  • FIG. 2 shows a plan view of the impeller 11 when the impeller 11 is projected on a plane perpendicular to the rotation axis 6.
  • FIG. 3 is a view showing a plane shape of the blade 1 and the boss portion 2 of the impeller 11 shown in FIG. 2 and 3, the X axis and the Y axis are axes perpendicular to each other.
  • the origin O of the X axis and the Y axis is the position of the rotary shaft 6.
  • the outer edge of the blade 1 in the plane shape is a blade leading edge portion 13 that is a portion that is directed in the traveling direction of the blade 1 due to the rotation of the boss portion 2, and a portion that is directed to the side opposite to the traveling direction of the blade 1. It has a certain blade trailing edge portion 14, a blade outer peripheral portion 15 which is a portion directed to the side opposite to the rotary shaft 6, and a blade inner peripheral portion 16 which is a portion directed to the rotary shaft 6. In plan view, the blade inner peripheral portion 16 forms an arc along the outer edge of the boss portion 2.
  • the blade 1 has a tip portion 20 protruding in the traveling direction of the blade 1.
  • the blade outer peripheral portion 15 forms an arc centered on the rotating shaft 6.
  • the blade outer peripheral portion 15 may be a curve other than a circular arc.
  • the blade outer peripheral portion 15 is bent toward the upstream side of the air flow.
  • the impeller 11 suppresses the generation of blade tip vortices due to the leakage of the air flow from the pressure surface side of the blade 1 to the suction surface side of the blade 1 in the blade outer peripheral portion 15.
  • the impeller 11 can reduce noise caused by the tip vortex generated on the blade 1 interfering with the pressure surface, the other blade 1, or the bell mouth.
  • the blade leading edge portion 13 is provided on the first bending portion 17 that bends in a direction opposite to the traveling direction of the blade 1 and on the rotary shaft 6 side with respect to the first bending portion 17. It has the 2nd bending part 18 which curves in the advancing direction, and the 3rd bending part 19 which is provided in the opposite side to the rotating shaft 6 rather than the 1st bending part 17, and bends in the advancing direction.
  • the blade leading edge portion 13 is curved between the first bending portion 17 and the second bending portion 18 and between the first bending portion 17 and the third bending portion 19, respectively.
  • the shape of the curve is changing.
  • the third curved portion 19 constitutes the tip portion 20 together with the blade outer peripheral portion 15.
  • the traveling direction of the blade 1 may be referred to as the front, and the direction opposite to the traveling direction of the blade 1 may be referred to as the rear.
  • the combination of the first bending portion 17, the second bending portion 18, and the third bending portion 19 may be referred to as unevenness.
  • the line segment 21 represents the first tangent line that is the tangent line at the position 25 included in the tip portion 20 of the blade outer peripheral portion 15.
  • the position 25 is a position behind the apex 24 between the blade outer peripheral portion 15 and the blade leading edge portion 13.
  • the line segment 22 represents the second tangent line that is the tangent line at the position 26 included in the distal end portion 20 of the third bending portion 19.
  • the position 26 is a position closer to the rotary shaft 6 than the apex 24.
  • the line segment 23 represents the third tangent line that is the tangent line at the position 27 at the end of the first bending portion 17 on the side of the second bending portion 18.
  • the chord centerline 30 of the wing 1 is curved forward as it moves away from the rotation axis 6.
  • the tip portion 20 has a shape that is tapered toward the front and protrudes toward the front.
  • the first angle ⁇ 1 is an angle formed by the line segment 21 and the line segment 22 and is an angle in a range including the tip portion 20.
  • the angle ⁇ 2, which is the second angle, is an angle formed by the line segment 22 and the line segment 23 and is an angle in a range including the first bending portion 17.
  • the angle ⁇ 1 is smaller than the angle ⁇ 2.
  • FIG. 4 is a diagram for explaining the state of the airflow around the blade 1 shown in FIG.
  • FIG. 4 shows a cross section taken along line IV-IV shown in FIG.
  • a blade tip vortex 28 is generated in the blade 1 near the blade outer peripheral portion 15.
  • the blade tip vortex 28 is formed by the pressure difference between the pressure surface 31 and the suction surface 32 of the blade 1 when the impeller 11 is rotating. Since the airflow from the front and the airflow sucked from the side where the bell mouth is provided flow into the blade leading edge portion 13, a separation vortex 29 is formed near the blade leading edge portion 13. ..
  • the blade tip vortex 28 and the separation vortex 29 generated on the blade 1 may generate noise by hitting another blade 1, a bell mouth, or a housing adjacent to the blade 1.
  • An air flow 33 in the turbulent boundary layer is generated on the suction surface 32 side of the blade 1.
  • the noise characteristics are deteriorated as the separation vortex 29 and the wake vortex 34 are increased and the turbulence of the air flow 33 is increased.
  • the longitudinal vortex that wraps around from the blade leading edge portion 13 to the suction surface 32 side is attached to the suction surface 32, and the blade leading edge portion 13 is formed.
  • the separation vortex 29 generated at 1 becomes a stable vertical vortex.
  • FIG. 5 is a diagram for explaining the relationship between the shape of the blade 1 and the strength of the blade 1 shown in FIG.
  • FIG. 5 shows the planar shape of the blade 1 when the shape of the blade 1 is changed so that the curvature of the chord centerline 30 becomes large.
  • the forward projection of the tip portion 20 increases. Note that, in FIG. 5, the shape of the blade 1 is shown in a simplified manner, and illustrations of configurations unnecessary for the description are omitted.
  • the line segment 35 is a straight line connecting a position 36 on an arbitrary radius R of the blade leading edge portion 13 and a position 37 on the blade outer peripheral portion 15.
  • the line segment 35 is assumed to be perpendicular to the tangent line of the blade outer peripheral portion 15 at the position 37.
  • the angle ⁇ 1 becomes smaller as the protrusion of the tip portion 20 toward the front becomes larger.
  • the stress concentration in the vicinity of the blade leading edge portion 13 becomes more remarkable, so that the blade 1 is more likely to be deformed.
  • unevenness is not provided on the blade leading edge portion 13, if the angle ⁇ 1 is reduced by increasing the forward curve of the chord centerline 30, the separation vortex 29 is stabilized as described above. While noise characteristics can be improved, deformation of the blade 1 is likely to occur due to stress concentration. In the first embodiment, unevenness is provided on the blade leading edge portion 13 to reduce stress concentration on the blade 1.
  • FIG. 6 is a plan view showing the suction surface 32 side of the impeller 11 shown in FIG.
  • FIG. 7 is a plan view showing the pressure surface 31 side of the impeller 11 shown in FIG.
  • the stress generated by the rotation of the impeller 11 is concentrated in the portion 40 of each blade 1 surrounded by the broken line.
  • the portion 40 is a portion near the blade leading edge portion 13 and near a position where the curved plate 3 is joined to the mounting portion 4. Since the blade 1 is deformed with the position of the curved plate 3 joined to the mounting portion 4 serving as a fulcrum, stress concentrates on the portion 40 of each blade 1.
  • the stress is measured in the case of the blade 1 having the tip portion 20 of the same angle ⁇ 1 and in the case where the blade leading edge portion 13 is not provided with unevenness and in the case of the first embodiment in which the blade leading edge portion 13 is provided with unevenness.
  • Examples of the stress described here are a steel material in which the rotational speed of the impeller 11 is 1800 min ⁇ 1 , the thickness of the curved plate 3 is 1 mm, the thickness of the spider 5 is 3 mm, and the materials of the curved plate 3 and the spider 5 are general.
  • the stress when When the blade leading edge portion 13 is not provided with irregularities, the maximum stress that the blade 1 receives is 57.2 MPa.
  • the maximum stress received by the blade 1 is 48.2 MPa.
  • the maximum stress received by the blade 1 is reduced by about 15.7% as compared with the case where the unevenness is not provided by providing the blade leading edge portion 13 with the unevenness.
  • the impeller 11 the first curved portion 17, the second curved portion 18, and the third curved portion 19 are provided in the blade leading edge portion 13, so that stress concentration in the blade 1 is relaxed. be able to.
  • the impeller 11 can suppress the deformation of the blade 1 by relaxing the stress concentration on the blade 1.
  • the impeller 11 can be made lighter in weight and can be manufactured at a lower cost as compared with the case where the thickness of the blade 1 is increased to improve the strength of the blade 1. Further, the impeller 11 can reduce the material cost as compared with the case of using a high-strength and expensive material for the material of the blade 1 in order to improve the strength of the blade 1.
  • FIG. 8 is a diagram illustrating noise characteristics of the impeller 11 according to the first embodiment.
  • FIG. 9 is a diagram illustrating the air flow-static pressure characteristics of the impeller 11 according to the first embodiment.
  • FIG. 10 is a diagram showing an example of the angles ⁇ 1 and ⁇ 2 shown in FIG. 2 for the impeller 11 according to the first embodiment.
  • the graph shown in FIG. 8 represents an example of the relationship between the air volume and the level of specific noise.
  • the graph shown in FIG. 9 represents an example of the relationship between the air volume and the static pressure.
  • the “impeller A1” is the impeller 11 according to the first embodiment, and the angle ⁇ 1 is 42.1 degrees and the angle ⁇ 2 is 130.0 degrees.
  • the “impeller A2” is the impeller 11 according to the first embodiment, and the angle ⁇ 1 is 29.4 degrees and the angle ⁇ 2 is 111.6 degrees.
  • the “impeller A3” is the impeller 11 according to the first embodiment, and the angle ⁇ 1 is 20.2 degrees and the angle ⁇ 2 is 90.0 degrees.
  • the “impeller B1” is an impeller according to a comparative example, and does not have the above-mentioned unevenness. In the “impeller B1”, the angle ⁇ 1 is 67.6 degrees.
  • the "impeller A1", “impeller A2”, “impeller A3” and “impeller B1” have a diameter of 260 mm.
  • the angle ⁇ 1 is included in the range of 20.2 degrees to 42.1 degrees.
  • the blade 1 has an angle ⁇ 2 of 90 degrees or more, so that the first bending portion 17, the second bending portion 18, and the third bending portion 19 are smoothly connected.
  • the impeller 11 can reduce the influence of the unevenness on the blade leading edge portion 13 on the inflow of the airflow at the blade leading edge portion 13.
  • the vertical axis represents the specific noise K T (dB) based on the total pressure
  • the horizontal axis represents the air volume Q (m 3 /min).
  • the vertical axis represents the static pressure P S (Pa)
  • the horizontal axis represents the air volume Q (m 3 /min).
  • SPL A represents the noise level corrected by the A characteristic
  • P T represents total pressure
  • K T SPL A ⁇ 10 ⁇ log(Q ⁇ P T 2.5 ) (1)
  • the airflow-static pressure characteristics of "impeller A1", “impeller A2” and “impeller A3” can be regarded as the same as the airflow-static pressure characteristics of "impeller B1".
  • the noise characteristic relationship between "impeller A1", “impeller A2”, and “impeller A3” is such that noise is reduced by about 2 dB at the maximum as compared with the case of "impeller B1". Has been improved.
  • FIG. 11 is a diagram showing an example of the relationship between the angle ⁇ 1 of the impeller 11 and the air volume Q according to the first embodiment.
  • the graph shown in FIG. 11 represents an example of the relationship between the angle ⁇ and the air volume ratio ⁇ Q at the open point where the static pressure is zero.
  • the air volume ratio ⁇ Q represents the ratio of the air volume Q of each impeller 11 to the air volume Q of the “impeller B1” whose angle ⁇ 1 is 67.6 degrees.
  • the vertical axis represents the air volume ratio ⁇ Q (%)
  • the horizontal axis represents the angle ⁇ 1 (degrees).
  • 11 represents the relationship between the angle ⁇ 1 and the air volume ratio ⁇ Q for “impeller A1”, “impeller A2”, “impeller A3”, and “impeller B1”.
  • the curve representing the relationship between the angle ⁇ and the air volume ratio ⁇ Q is obtained by interpolating the relationship between the angle ⁇ and the air volume ratio ⁇ Q between the plots.
  • the air volume ratio ⁇ Q tends to decrease as the angle ⁇ 1 decreases.
  • the angle ⁇ 1 is changed in the angle range of 67.6 degrees to 20.2 degrees, the reduction width of the air volume ratio ⁇ Q is suppressed to 0.6% at the maximum.
  • the impeller 11 according to the first embodiment has a limited decrease in the air volume by reducing the angle ⁇ 1.
  • FIG. 12 is a diagram showing an example of the relationship between the angle ⁇ 1 of the impeller 11 and the minimum specific noise K Tmin according to the first embodiment.
  • the vertical axis represents the minimum specific noise difference ⁇ K Tmin (dB)
  • the horizontal axis represents the angle ⁇ 1 (degrees).
  • Minimum specific noise difference [Delta] K Tmin the angle ⁇ 1 represents the difference between the minimum ratio noise K Tmin and minimum specific noise K Tmin of each wheel 11 of the "wheel B1" is 67.6 degrees.
  • the plot in the graph of FIG. 12 represents the relationship between the angle ⁇ 1 and the minimum specific noise difference ⁇ K Tmin for “impeller A1”, “impeller A2”, “impeller A3” and “impeller B1”. Curve representing the relationship between the angle ⁇ 1 and the minimum ratio noise difference [Delta] K Tmin is determined by interpolating the relation between the angle ⁇ 1 and the minimum ratio noise difference [Delta] K Tmin between plots.
  • the noise characteristic of the impeller 11 is improved so that the minimum specific noise difference ⁇ K Tmin becomes 0.5 dB or more lower.
  • the noise characteristic of the impeller 11 is improved so that the minimum specific noise difference ⁇ K Tmin becomes 2 dB lower.
  • FIG. 13 is a diagram showing an example of the relationship between the angle ⁇ 1 of the impeller 11 and the maximum stress ⁇ max according to the first embodiment.
  • the vertical axis represents the maximum stress ratio ⁇ max (%)
  • the horizontal axis represents the angle ⁇ 1 (degrees).
  • the maximum stress ratio ⁇ max represents the ratio of the maximum stress ⁇ max of each impeller 11 to the maximum stress ⁇ max of the “impeller B1” having the angle ⁇ 1 of 67.6 degrees.
  • the plot in the graph of FIG. 13 represents the relationship between the angle ⁇ 1 and the maximum stress ratio ⁇ max for “impeller A1”, “impeller A2”, “impeller A3”, and “impeller B1”.
  • the curve representing the relationship between the angle ⁇ 1 and the maximum stress ratio ⁇ max is obtained by interpolating the relationship between the angle ⁇ 1 and the maximum stress ratio ⁇ max between the plots.
  • the impeller 11 when the angle ⁇ 1 is included in the range of 20.2 degrees to 55 degrees, the maximum stress ⁇ max decreases from 4% to 9%.
  • the impeller 11 can reduce noise and alleviate stress concentration.
  • the angle ⁇ 2 is set to 90 degrees or more, so that the relationship of ⁇ 2 ⁇ 1 is established. As described above, the impeller 11 can reduce noise and alleviate stress concentration when the angle ⁇ 1 is smaller than the angle ⁇ 2.
  • the impeller 11 is provided with the first curved portion 17, the second curved portion 18, and the third curved portion 19 at the blade leading edge portion 13 of each blade 1.
  • the impeller 11 can reduce noise and stress concentration by making the plane shape of the blade 1 a shape having an angle ⁇ 1 smaller than the angle ⁇ 2. As a result, the impeller 11 has an effect of reducing noise and stress concentration.

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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 impulseur (11) comprenant : un bossage (2) qui peut tourner autour d'un axe de rotation (6) ; et des pales (1) qui sont rayonnées à partir du bossage (2). Depuis une forme plane de chaque lame (1) lorsque la lame (1) est projetée sur un plan orthogonal à l'axe de rotation (6), une section de bord d'attaque de pale (13) du bord extérieur de la pale (1), qui fait face à la direction de déplacement de la pale (1) qui est provoquée par la rotation du bossage (2), comporte : une première section de courbe (17) qui est incurvée vers une direction opposée à la direction de déplacement ; une deuxième section de courbe (18) qui est disposée plus vers l'axe de rotation (6) que la première section de courbe (17) et est incurvée vers la direction de déplacement ; et une troisième section de courbe (19) qui est disposée sur le côté opposé de la première section de courbe (17) à partir de l'axe de rotation (6) et est incurvée vers la direction de déplacement.
PCT/JP2018/043355 2018-11-26 2018-11-26 Impulseur et ventilateur à flux axial WO2020110167A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201880099511.XA CN113039366B (zh) 2018-11-26 2018-11-26 叶轮以及轴流送风机
PCT/JP2018/043355 WO2020110167A1 (fr) 2018-11-26 2018-11-26 Impulseur et ventilateur à flux axial
JP2020557411A JPWO2020110167A1 (ja) 2018-11-26 2018-11-26 翼車および軸流送風機
TW108114283A TWI742364B (zh) 2018-11-26 2019-04-24 葉輪及軸流風扇
JP2022044255A JP2022075846A (ja) 2018-11-26 2022-03-18 翼車および軸流送風機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/043355 WO2020110167A1 (fr) 2018-11-26 2018-11-26 Impulseur et ventilateur à flux axial

Publications (1)

Publication Number Publication Date
WO2020110167A1 true WO2020110167A1 (fr) 2020-06-04

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PCT/JP2018/043355 WO2020110167A1 (fr) 2018-11-26 2018-11-26 Impulseur et ventilateur à flux axial

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JP (2) JPWO2020110167A1 (fr)
CN (1) CN113039366B (fr)
TW (1) TWI742364B (fr)
WO (1) WO2020110167A1 (fr)

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JPS5990798A (ja) * 1982-11-15 1984-05-25 Toshiba Corp 羽根車
JPH06264897A (ja) * 1993-03-11 1994-09-20 Yamaha Motor Co Ltd 軸流ファン
JP2004346775A (ja) * 2003-05-20 2004-12-09 Hitachi Constr Mach Co Ltd プロペラファン並びにエンジン冷却装置及び建設機械
JP2010101223A (ja) * 2008-10-22 2010-05-06 Sharp Corp プロペラファン、流体送り装置および成型金型
JP2015031249A (ja) * 2013-08-06 2015-02-16 三菱電機株式会社 プロペラファン
JP2015190332A (ja) * 2014-03-27 2015-11-02 三菱電機株式会社 軸流送風機、換気装置及び冷凍サイクル装置
WO2016021555A1 (fr) * 2014-08-07 2016-02-11 三菱電機株式会社 Ventilateur à écoulement axial et climatiseur ayant ledit ventilateur à écoulement axial
WO2017077575A1 (fr) * 2015-11-02 2017-05-11 三菱電機株式会社 Soufflante, unité extérieure, et appareil à cycle de réfrigération

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JPS5222811B2 (fr) * 1973-08-11 1977-06-20
JPS6088100U (ja) * 1983-11-25 1985-06-17 株式会社東芝 羽根車
JP5990798B2 (ja) 2012-09-18 2016-09-14 アクアフェアリー株式会社 発電装置
JP5980180B2 (ja) * 2013-08-08 2016-08-31 三菱電機株式会社 軸流ファン、及び、その軸流ファンを有する空気調和機
CN205136124U (zh) * 2015-11-12 2016-04-06 珠海格力电器股份有限公司 轴流风机及其轴流风叶
WO2017216937A1 (fr) * 2016-06-16 2017-12-21 三菱電機株式会社 Turbine et soufflante axiale

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5039241B1 (fr) * 1970-02-06 1975-12-16
JPS5990798A (ja) * 1982-11-15 1984-05-25 Toshiba Corp 羽根車
JPH06264897A (ja) * 1993-03-11 1994-09-20 Yamaha Motor Co Ltd 軸流ファン
JP2004346775A (ja) * 2003-05-20 2004-12-09 Hitachi Constr Mach Co Ltd プロペラファン並びにエンジン冷却装置及び建設機械
JP2010101223A (ja) * 2008-10-22 2010-05-06 Sharp Corp プロペラファン、流体送り装置および成型金型
JP2015031249A (ja) * 2013-08-06 2015-02-16 三菱電機株式会社 プロペラファン
JP2015190332A (ja) * 2014-03-27 2015-11-02 三菱電機株式会社 軸流送風機、換気装置及び冷凍サイクル装置
WO2016021555A1 (fr) * 2014-08-07 2016-02-11 三菱電機株式会社 Ventilateur à écoulement axial et climatiseur ayant ledit ventilateur à écoulement axial
WO2017077575A1 (fr) * 2015-11-02 2017-05-11 三菱電機株式会社 Soufflante, unité extérieure, et appareil à cycle de réfrigération

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Publication number Publication date
CN113039366B (zh) 2023-06-02
TW202020314A (zh) 2020-06-01
CN113039366A (zh) 2021-06-25
JP2022075846A (ja) 2022-05-18
JPWO2020110167A1 (ja) 2021-05-13
TWI742364B (zh) 2021-10-11

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