EP3739218A1 - Pale de ventilateur axial, ensemble pale de ventilateur axial et ensemble conduit de ventilateur axial - Google Patents

Pale de ventilateur axial, ensemble pale de ventilateur axial et ensemble conduit de ventilateur axial Download PDF

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Publication number
EP3739218A1
EP3739218A1 EP18900229.8A EP18900229A EP3739218A1 EP 3739218 A1 EP3739218 A1 EP 3739218A1 EP 18900229 A EP18900229 A EP 18900229A EP 3739218 A1 EP3739218 A1 EP 3739218A1
Authority
EP
European Patent Office
Prior art keywords
axial flow
flow fan
blade
air
air guide
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
EP18900229.8A
Other languages
German (de)
English (en)
Other versions
EP3739218A4 (fr
Inventor
Xintao JIA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Midea Group Co Ltd
GD Midea Environment Appliances Manufacturing Co Ltd
Original Assignee
Midea Group Co Ltd
GD Midea Environment Appliances Manufacturing Co Ltd
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 Midea Group Co Ltd, GD Midea Environment Appliances Manufacturing Co Ltd filed Critical Midea Group Co Ltd
Publication of EP3739218A1 publication Critical patent/EP3739218A1/fr
Publication of EP3739218A4 publication Critical patent/EP3739218A4/fr
Pending legal-status Critical Current

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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
    • F04D29/26—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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • dB (A) refers to A-weighted sound level, which simulates frequency characteristics of human ear to low-intensity noise below 55dB.
  • the present application is intended to solve at least one of technical problems existing in the prior art or related technologies.
  • the air guide section has a zigzag shape.
  • the number of the axial flow fan blades is odd.
  • the number of the axial flow fan blades is three or five.
  • the axial flow fan blade and a mounting surface of the hub intersects at a first curve, and an included angle between a tangent line at any point on the first curve and a vertical surface of the hub is 30 ⁇ 5°.
  • the present application also provides an air duct assembly for axial flow fan, which includes the above-mentioned blade assembly for axial flow fan, and also includes a guide duct, the axial flow fan blades of the blade assembly for axial flow fan being located within the guide duct.
  • the duct assembly for axial flow fan also includes an air outflow shroud, on which an end of the guide duct is fixed.
  • the air guide section of the axial flow fan blade in the present application can divide an airflow into small airflows at the source of the airflow so as to make the air guide grooves on the windward edge achieve the best noise reduction effect.
  • each of the air guide grooves has the gradually decreased depth toward the rotation center, that is, farther away from the airflow source, smaller the depth of the air guide grooves, which ensures a uniform air speed and making air experienced by users more natural.
  • the axial flow fan blade of the present application can provide users with good comprehensive experience without compromising air speed and air volume for reducing noise.
  • orientation or position relationship indicated by the terms “center”, “longitudinal”, “lateral”, “upper”, “lower”, “front”, “rear”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inner”, “outer”, etc. is based on the orientation or position relationship shown in the drawings, and is intended only to facilitate the description of the application and simplify the description, but not to indicate or imply that the referred device or element must have a particular orientation, being constructed and operated in a particular orientation, and thus cannot be understood as a limitation of the present application.
  • the terms “first”, “second”, “third” are used only for descriptive purposes, and cannot be understood as indicating or implying relative importance.
  • a air guide section formed on an end of an windward edge of a blade proximal to a blade tip, and a plurality of air guide grooves 2 are disposed on the air guide section; a distance between the closest point of the air guide section and a rotation center of the axial flow fan blade 1 is r 1 , a distance between the farthest point of the air guide section and the rotation center of the axial flow fan blade 1 is r 2 , a distance between the farthest point on the windward edge and the rotation center of the axial flow fan blade 1 is r, and the ratio of (r 2 -r 1 ) to r is between 1/3 and 1/2.
  • a depth of the air guide grooves 2 is gradually reduced along a direction running towards the rotation center.
  • the blade tip refers to a portion of the axial flow fan blade 1 far away from the rotation center O, while a blade root is a portion of the axial flow fan blade 1 close to the rotation center O.
  • the air guide section is only provided at the end of the axial flow fan blade 1 proximal to the blade tip, which can not only achieve almost the same noise reduction effect as when the air guide section is formed on the entire windward edge, but also avoid the problem that the strength of the axial flow fan blade 1 is reduced when the air guide section is formed at an end of the blade root.
  • the depth of the air guide groove 2 gradually decreases toward the rotation center, and thus the current axial flow fan blade 1 can be processed to obtain the above air guide section without any impact on the strength of the axial flow fan blades 1 and thus it eliminates the need for additionally separate design of the axial flow fan blades 1.
  • the air guide section is provided at the end of the axial flow fan blade 1 proximal to the blade tip, the air resistance to the axial flow fan blade 1 can also be reduced, thereby effectively reducing the motor load so as to increase the air speed at the same power.
  • this embodiment provides a blade assembly for axial flow fan including the above-mentioned axial flow fan blades 1 and a hub 3 for mounting the axial flow fan blades 1.
  • the number of the axial flow fan blades 1 is preferably odd to reduce the noise generated by resonance. Moreover, it is preferred but not necessary that the number of the axial flow fan blades 1 is three or five, so as to ensure the performance of the blade assembly for axial flow fan.
  • a distance between the farthest point on the fan blade and the rotation center of the axial flow fan blade 1 is r 4 .
  • the ratio of r 3 to r 4 is between 0.2 and 0.3, larger air volume can be obtained under the premise of ensuring the mounting strength of the hub 3 and the axial flow fan blades 1.
  • each of the axial flow fan blades 1 has a thickness of 2.0 mm, r 4 of 185 mm, and r 3 of 42 mm.
  • air speed of 0.5m/s are still possible at two meters away from the air outlet under the condition that the noise is less than 50dB (A).
  • the guide duct 4 has gradually decreased cross-sectional area along an air outflow direction, so that the airflow is accelerated within the guide duct 4, and higher air speed is obtained at the air outflow shroud 5 to meet user requirements.
  • a grille 7 of the air outflow shroud includes a plurality of grid bars, and all of the grid bars are distributed along the circumference.
  • Fig. 3 does not constitute a limitation to the air outflow shroud of this application.
  • the grid bars of the air outflow shroud in this application can also be arranged in cross.
  • the inclination directions of an inner section and the outer section of the grid bar in Fig. 3 are different in the direction away from the center of the circumference, the main purpose of which is to obtain a better appearance of the grille 7.
  • the entire grid bars can be designed such that the grid bars gradually incline toward the rotation direction of the fan blade in the direction away from the center of the circumference.
  • the guide duct is projected on the grille 7 along its own axis to obtain a first projection line 8 (referring to Fig. 3 ).
  • the first projection line 8 and the grid bar intersect at a first point, and an included angle between a first tangent line of the grid bar at the first point and a second tangent line of the first projection line 8 at this point is 100°-115°.
  • the resistance of the grille 7 to the airflow can be further reduced to obtain a greater air speed and air volume.
  • each of the grid bars of the air outflow shroud 5 has the gradually increased cross section along the air outflow direction, so that the air outlet area between adjacent grid bars of the grille 7 gradually decreases along the air outflow direction.
  • an acceleration pressure is formed on the grille 7 and higher air speed is formed at the air outlet, so that the user can obtain a better experience.
  • the ratio of the area of the air inlet surface of the air inlet shroud 6 to the area of the air outlet surface of the air outflow shroud 5 is 1.1-1.35. In this case, a greater air speed can be obtained on the air outlet surface while ensuring the appearance of the product. It is found through experiments that when the ratio of the area of the air inlet surface of the air inlet shroud 6 to the area of the air outlet surface of the air outflow shroud 5 in this embodiment is 1.25, the user can get the best experience in terms of performance and appearance.
  • the air inlet shroud 6 includes a first air inlet surface 601, a second air inlet surface 602 and a third air inlet surface 603 which are mutually angled each other. Therefore, the area of the air inlet surface of the air inlet shroud 6 is the sum of the areas of the first air inlet surface 601, the second air inlet surface 602, and the third air inlet surface 603.
  • a plurality of mutually angled air inlet surfaces are provided such that the air inlet area of the air inlet shroud 6 can be increased, thereby increasing the ratio of the area of the air inlet surface of the air inlet shroud 6 to the area of the air outlet surface of the air outflow shroud 5 while ensuring the appearance of the product.
  • the number of air inlet surfaces on the air inlet shroud 6 is not limited by the drawings, for example, there may be any other air inlet surfaces, or there may be one.
  • the angle between the multiple air inlet surfaces is not limited by the drawings.
  • any field requiring the application of axial flow fans can employ the above-mentioned axial flow fan blade 1, the blade assembly for axial flow fan and the air duct assembly for axial flow fan.
  • the above-mentioned axial flow fan blade 1, the blade assembly for axial flow fan and the air duct assembly for axial flow fan can be applied to heaters, coolers, ordinary fans and other products.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP18900229.8A 2018-01-13 2018-06-28 Pale de ventilateur axial, ensemble pale de ventilateur axial et ensemble conduit de ventilateur axial Pending EP3739218A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201820054204.7U CN207795681U (zh) 2018-01-13 2018-01-13 轴流扇叶、轴流风机扇叶组件、轴流风机风道组件
PCT/CN2018/093266 WO2019136939A1 (fr) 2018-01-13 2018-06-28 Pale de ventilateur axial, ensemble pale de ventilateur axial et ensemble conduit de ventilateur axial

Publications (2)

Publication Number Publication Date
EP3739218A1 true EP3739218A1 (fr) 2020-11-18
EP3739218A4 EP3739218A4 (fr) 2021-03-17

Family

ID=63271797

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18900229.8A Pending EP3739218A4 (fr) 2018-01-13 2018-06-28 Pale de ventilateur axial, ensemble pale de ventilateur axial et ensemble conduit de ventilateur axial

Country Status (4)

Country Link
US (1) USD884874S1 (fr)
EP (1) EP3739218A4 (fr)
CN (1) CN207795681U (fr)
WO (1) WO2019136939A1 (fr)

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CN114526252A (zh) * 2022-02-22 2022-05-24 宁波公牛生活电器有限公司 扇叶、风扇和隐形风扇灯

Also Published As

Publication number Publication date
EP3739218A4 (fr) 2021-03-17
WO2019136939A1 (fr) 2019-07-18
USD884874S1 (en) 2020-05-19
CN207795681U (zh) 2018-08-31

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