WO2020077802A1 - Ventilateur contrarotatif - Google Patents

Ventilateur contrarotatif Download PDF

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Publication number
WO2020077802A1
WO2020077802A1 PCT/CN2018/122355 CN2018122355W WO2020077802A1 WO 2020077802 A1 WO2020077802 A1 WO 2020077802A1 CN 2018122355 W CN2018122355 W CN 2018122355W WO 2020077802 A1 WO2020077802 A1 WO 2020077802A1
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WO
WIPO (PCT)
Prior art keywords
blade
counter
rotating fan
leading edge
line
Prior art date
Application number
PCT/CN2018/122355
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English (en)
Chinese (zh)
Inventor
胡斯特
胡小文
张辉
易榕
Original Assignee
广东美的白色家电技术创新中心有限公司
美的集团股份有限公司
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
Priority claimed from CN201821672645.XU external-priority patent/CN209180089U/zh
Priority claimed from CN201811198972.0A external-priority patent/CN111043064A/zh
Application filed by 广东美的白色家电技术创新中心有限公司, 美的集团股份有限公司 filed Critical 广东美的白色家电技术创新中心有限公司
Publication of WO2020077802A1 publication Critical patent/WO2020077802A1/fr

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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
    • F04D19/00—Axial-flow pumps
    • F04D19/007—Axial-flow pumps multistage 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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/024—Multi-stage pumps with contrarotating parts
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows

Definitions

  • the invention relates to the technical field of fans, in particular to a counter-rotating fan.
  • the counter-rotating electric fan is a new type of electric fan, which has the characteristics of low noise, long air supply distance and controllable air type.
  • Existing counter-rotating electric fans generally have the same axial width of the two-stage fan blades and rotate in opposite directions. The swirling airflow at the outlet of the first-stage fan blade can be derotated by the second-stage fan blade, thereby achieving the functions of straight wind, long-distance air supply, and accelerated air circulation.
  • the two-stage fan can do not race or even disperse the airflow, thereby achieving a wide dispersion of wind, making the human body feel very soft in the vicinity.
  • the size of the fan in home appliances is often limited by the structure.
  • the axial width of the two-stage fan blades is equal.
  • the airflow at the outlet of the first-stage blade is equivalent to providing reverse pre-rotation.
  • the two-stage fan blade load is very high, resulting in a large turning angle of the second-stage blade shape, unable to achieve axial airflow, making the outlet airflow It also has the speed component of the second-stage fan blade rotation, making the air supply distance closer.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a counter-rotating fan, which has a relatively long blowing distance.
  • a counter-rotating fan includes a first-stage impeller and a second-stage impeller having opposite rotation directions, the first-stage impeller is located on the air inlet side of the counter-rotating fan, and the second-stage impeller is located on the On the outlet side of the counter-rotating fan, the first-stage impeller includes a plurality of first blades distributed along its circumferential direction, and the second-stage impeller includes a plurality of second blades distributed along its circumferential direction, the first The axial width of one blade is larger than the axial width of the second blade.
  • the counter-rotating fan of the embodiment of the present invention since the axial width of the first blade is larger than the axial width of the second blade, it can not only ensure that the wind direction of the counter-rotating fan remains axial, but also increase the wind output from the counter-rotating fan Pressure and air volume.
  • the axial width of the first blade is A1
  • the axial width of the second blade is A2
  • A2 does not exceed twice A1.
  • the axial width A1 of the first blade ranges from 25 mm to 55 mm
  • the axial width A2 of the second blade ranges from 25 mm to 55 mm.
  • each edge of each of the first blades in the circumferential direction is respectively a first leading edge and a first trailing edge, and the first leading edge and the first trailing edge are both radially formed by Bending in the direction of rotation from the inside to the outside, and the bending protrusion of the first leading edge is directed to the first trailing edge corresponding to the first blade;
  • each of the second blades is circumferentially edged on both sides Are a second leading edge and a second trailing edge, respectively, the second leading edge and the second trailing edge are both curved toward the direction of rotation in a radial direction from inside to outside, and the bending of the second leading edge is convex
  • the outgoing point corresponds to the second trailing edge on the second blade.
  • the leading edge bending angle ⁇ le of the first blade and the second blade ranges from 15 ° to 75 °; wherein, the projection of the first leading edge on the radial cross section is A first leading edge line, the angle between the tangent line and the radial line at any point on the first leading edge line is the leading edge bending angle of the first blade; the second leading edge is in a radial section The projection is the second leading edge line, the angle between the tangent line and the radial line at any point on the second leading edge line is the leading edge bending angle of the second blade, and the radial cross section is perpendicular to the In the plane of the rotation axis of the counter-rotating fan, the radial line is a straight line passing through the rotation axis in the radial section.
  • the trailing edge bending angle ⁇ te of the first blade and the second blade ranges from 0 ° to 60 °; wherein, the projection of the first trailing edge on the radial section is A first trailing edge line, the angle between the tangent line and the radial line at any point on the first trailing edge line is the trailing edge bending angle of the first blade; The projection is the second trailing edge line, and the angle between the tangent line and the radial line at any point on the second trailing edge line is the trailing angle of the second blade; the radial section is perpendicular to the In the plane of the rotation axis of the counter-rotating fan, the radial line is a straight line passing through the rotation axis in the radial section.
  • the number of the first blades is not equal to the number of the second blades.
  • the counter-rotating fan further includes: an enclosure and two net enclosures, the net enclosure surrounds the outer peripheral sides of the first-stage impeller and the second-stage impeller, two The net cover is connected to opposite sides of the enclosure.
  • the enclosure includes: a ring rib and a plurality of horizontal ribs, the ring ribs are formed into a ring shape, a plurality of the horizontal ribs are respectively connected to the ring ribs, and two of each horizontal rib The ends are respectively connected to the two net covers.
  • the counter-rotating fan further includes: a post, the post is connected below the enclosure.
  • FIG. 1 is an overall structural diagram of a counter-rotating fan according to an embodiment of the present invention.
  • FIG. 2 is a schematic structural diagram of a first-stage impeller according to an embodiment of the present invention.
  • FIG. 3 is a schematic structural diagram of a second-stage impeller according to an embodiment of the present invention.
  • FIG. 4 is a vector diagram of airflow on the inlet side of the first-stage impeller according to an embodiment of the present invention.
  • FIG 5 is an airflow vector diagram of the first-stage impeller outlet side and the second-stage impeller inlet side of the embodiment of the present invention.
  • FIG. 6 is a vector diagram of airflow on the air outlet side of the second-stage impeller according to an embodiment of the present invention.
  • FIG. 7 is a fan relationship diagram of the ratio between the axial width A1 of the first blade and the axial width A2 of the second blade and the output of the counter-rotating fan in the embodiment of the present invention.
  • FIG. 8 is a schematic structural view of a first-stage impeller and a second-stage wheel according to an embodiment of the present invention.
  • the first stage impeller 10 the first blade 110,
  • connection should be understood in a broad sense, for example, it can be fixed connection or detachable Connected, or connected integrally; either mechanically or electrically; directly connected, or indirectly connected through an intermediary, or internally connected between two components.
  • installation should be understood in a broad sense, for example, it can be fixed connection or detachable Connected, or connected integrally; either mechanically or electrically; directly connected, or indirectly connected through an intermediary, or internally connected between two components.
  • the counter-rotating fan 1 according to an embodiment of the present invention will be described below with reference to FIGS. 1 to 7.
  • the counter-rotating fan 1 includes a first-stage impeller 10 and a second-stage impeller 20 having opposite rotation directions.
  • the first-stage impeller 10 is located on the air inlet side of the counter-rotating fan 1
  • the second-stage impeller 20 is located on the outlet side of the counter-rotating fan 1
  • the first-stage impeller 10 includes a plurality of first blades 110 distributed along its circumferential direction
  • the second-stage impeller 20 includes a plurality of first blades distributed along its circumferential direction
  • the axial width of the first blade 110 is greater than the axial width of the second blade 210.
  • the counter-rotating fan 1 of the embodiment of the present invention can be applied to electric fans, circulation fans, ventilation fans, air-conditioning fans, and other devices that need to send out air.
  • the counter-rotating fan 1 of the embodiment of the present invention is mainly used to promote air flow rather than heat exchange.
  • the rotation speed of the first blade 110 and the rotation speed of the second blade 210 can affect the entire blower distance of the counter-rotating fan 1, but the main blades discussed in this application are the first blade 110 and the second blade 210 The relationship between the axial width and the blowing distance of the counter-rotating fan 1. Therefore, the following analysis process is based on the premise that the rotation speeds of the first blade 110 and the second blade 210 are unchanged.
  • the axial width of the first blade 110 refers to the width shown in A1 in FIG. 8
  • the axial width of the second blade 210 refers to the width shown in A2 in FIG. 8.
  • U1 is the rotational linear velocity of the first-stage impeller 10
  • W1 is the airflow velocity of the first-stage impeller 10 in the rotating coordinate system
  • V1 which represents the airflow velocity of the first-stage impeller 10 felt by the human body
  • W2 is the airflow velocity of the first-stage impeller 10 in the rotating coordinate system
  • the vector synthesis result of U1 and W2 is V2
  • V2 represents the airflow velocity of the first-stage impeller 10 felt by the human body
  • W3 is the airflow velocity of the second-stage impeller 20 in the rotating coordinate system
  • U2 is the rotational linear velocity of the second-stage impeller 20.
  • V2 -V3
  • V3 represents the second Inlet airflow speed of the stage impeller 20.
  • W4 is the airflow velocity of the second-stage impeller 20 in the rotating coordinate system.
  • the vector synthesis result of U2 and W4 is V4.
  • V4 represents the airflow velocity of the second-stage impeller 20 felt by the human body.
  • V4 is synthesized by W4 and U2
  • U2 is the rotational linear velocity of the second-stage impeller 20 and U2 is a fixed value according to the foregoing description. Therefore, in order to ensure the axial direction of V4 (that is, V4 coincides with Vax as much as possible), at this time, we can think that the direction of W4 is limited.
  • the counter-rotating fan 1 needs to output a large wind pressure, so it is necessary to increase the airflow turning angle of the second blade 210 (that is, the angle difference between W3 and W4), while increasing the airflow turning angle of the second blade 210 has Two methods:
  • increasing the thickness of the second blade 210 can only guarantee one of the axial direction of the outlet air flow and the output wind pressure, that is, increasing the second blade 210 can ensure the output wind pressure of the counter-rotating fan 1, but it will cause The wind direction of the rotary fan 1 deviates from the axial direction, thereby reducing the air supply distance of the rotary fan 1; reducing the second blade 210 can certainly ensure that the wind direction of the rotary fan 1 is as close to the axial direction as possible, but it will cause the output wind pressure Lower.
  • increasing the axial width of the first blade 110 can not only ensure that the wind direction of the counter-rotating fan 1 remains axial, but also increase the wind pressure and air volume output from the counter-rotating fan 1.
  • the counter-rotating fan 1 of the embodiment of the present invention since the axial width of the first blade 110 is greater than the axial width of the second blade 210, it can not only ensure that the wind direction of the counter-rotating fan 1 remains axial, but also increase the counter-rotating The air pressure and air volume output by the fan 1.
  • the axial width of the first blade 110 is A1
  • the axial width of the second blade 210 is A2.
  • A2 does not exceed the relationship of twice A1, that is, A1 and A2 satisfy the relationship: 1 ⁇ A1 / A2 ⁇ 2. It is understandable that excessive A1 / A2 will cause the second blade 210 to extend too short, which will also cause the air flow path of the second blade 210 to be shorter, which will cause the second blade 210 to not withstand too much air flow turning, thus The wind pressure output by the counter-rotating fan 1 is low. As shown in FIG. 7, therefore, controlling the size of A1 / A2 within the range of less than 2 can ensure that the outlet direction of the counter-rotating fan 1 maintains the axial direction, and also ensures the wind pressure and air output from the counter-rotating fan 1.
  • A1 / A2 can be adjusted according to actual conditions and is not limited to the above range.
  • the axial width A1 of the first blade 110 ranges from 25 mm to 55 mm
  • the axial width A2 of the second blade 210 ranges from 25 mm to 55 mm.
  • A1 and A2 satisfy the relationship: 25mm ⁇ A1 ⁇ 55mm, 25mm ⁇ A2 ⁇ 55mm.
  • the values of A1 and A2 are better manufactured within the above range, which reduces the production cost of the counter-rotating fan 1.
  • the values of A1 and A2 can be selected according to actual needs, and are not limited to the above ranges.
  • each first blade 110 in the circumferential direction are the first leading edge Le1 and the first trailing edge Te1, and the first leading edge Le1 and the first trailing edge are respectively
  • the edges Te1 are all curved in the direction of rotation from the inside to the outside in the radial direction, and the curved protrusion of the first leading edge Le1 faces the first trailing edge Te1 on the corresponding first blade 110.
  • each second blade 210 in the circumferential direction are the second leading edge Le2 and the second trailing edge Te2, and the second leading edge Le2 and the second trailing edge Te2 rotate toward the radial direction from inside to outside
  • the direction is curved, and the curved protrusion of the second leading edge Le2 faces the second trailing edge Te2 on the corresponding second blade 210.
  • first leading edge Le1 and the first trailing edge Te1 of the first blade 110 are both curved in the radial direction from the inside to the outside toward the rotation direction
  • second leading edge Le2 of the second blade 210 is The second trailing edge Te2 is curved from the inside to the outside in the radial direction toward the rotation direction, which can effectively weaken the radial component of the surface fluid of the blades of the first blade 110 and the second blade 210, so that the energy is exhausted. It may be concentrated in the axial direction, reducing the radial loss of the first blade 110 and the second blade 210, improving the working efficiency of the counter-rotating fan 1, and increasing the output wind pressure and air volume of the counter-rotating fan 1 to a certain extent.
  • the rotation directions of the first-stage impeller 10 and the second blade 210 are opposite, and the bending direction of the first blade 110 is the same as the rotation direction of the first-stage impeller 10, and the bending direction of the second blade 210 is the same as the second-stage impeller 20
  • the rotation directions are the same, that is, the bending direction of the first blade 110 and the bending direction of the second blade 210 are opposite.
  • This structure can reduce the phenomenon that the first blade 110 and the second-stage impeller 20 periodically overlap during the rotation of the counter-rotating fan 1, so that the depleted flow field from the first blade 110 always enters away from the surface of the second blade 210. In the middle flow channel, the more uniform airflow passes over the surface of the second blade 210.
  • the rotation noise of the second blade 210 is reduced to a certain extent.
  • the leading edge bending angle ⁇ le of the first blade 110 and the second blade 210 ranges from 15 ° to 75 °. That is to say, the leading edge bending angle ⁇ le of the first blade 110 and the second blade 210 both satisfy the condition: 15 ° ⁇ le ⁇ 75 °.
  • the projection of the first leading edge Le1 on the radial section is the first leading edge Le1 line, and the angle between the tangent line and the radial line Ld at any point on the first leading edge Le1 line is the leading edge bending angle of the first blade 110
  • the projection of the second leading edge Le2 on the radial cross section is the second leading edge Le2 line, and the angle between the tangent line and the radial line Ld at any point on the second leading edge Le2 line is the leading edge bend of the second blade 210
  • the radial section is a plane perpendicular to the rotation axis of the counter-rotating fan 1
  • the radial line Ld is a straight line passing through the rotation axis in the radial section.
  • first blade 110 and the second blade 210 are curved in the circumferential direction toward their rotation direction, such a blade shape can weaken the radial motion component of the air flow when the first blade 110 and the second blade 210 rotate, Thereby, the motion component of the air flow in the axial direction is increased, that is to say, such an airfoil shape can improve the efficiency of the first blade 110 and the second blade 210.
  • ⁇ le satisfies the condition: 35 ° ⁇ le ⁇ 55 °.
  • the size of ⁇ le is not limited to the above range, and the size of ⁇ le may be specifically adjusted according to actual conditions.
  • the leading edge bend angle of the first blade 110 and the leading edge bend angle of the second blade 210 may or may not be the same.
  • the trailing edge bending angle ⁇ te of the first blade 110 and the second blade 210 ranges from 0 ° -60 °. That is, the trailing edge bending angles ⁇ te of the first blade 110 and the second blade 210 both satisfy the condition: 0 ° ⁇ te ⁇ 60 °.
  • the projection of the first trailing edge Te1 on the radial section is the first trailing edge Te1 line, and the angle between the tangent line and the radial line Ld at any point on the first trailing edge Te1 line is the trailing edge bending angle of the first blade 110
  • the projection of the second trailing edge Te2 on the radial cross section is the second trailing edge Te2 line, and the angle between the tangent line and the radial line Ld at any point on the second trailing edge Te2 line is the trailing edge bend of the second blade 210 Angle;
  • the radial section is a plane perpendicular to the rotation axis of the counter-rotating fan 1, and the radial line Ld is a straight line passing through the rotation axis in the radial section.
  • first blade 110 and the second blade 210 are curved in the circumferential direction toward their rotation direction, such a blade shape can weaken the radial motion component of the air flow when the first blade 110 and the second blade 210 rotate, Thereby increasing the axial motion component of the airflow.
  • ⁇ te satisfies the condition: 20 ° ⁇ te ⁇ 40 °.
  • the size of ⁇ te is not limited to the above range, and the size of ⁇ te may be specifically adjusted according to actual conditions.
  • the trailing edge bend angle of the first blade 110 and the trailing edge bend angle of the second blade 210 may or may not be the same.
  • the first blade 110 and the first blade 110 can be better avoided.
  • the phenomenon of periodic overlap occurs when the two blades 210 rotate, and the flow field structure can be optimized and the flow field loss can be reduced by optimizing the above-mentioned angle distribution.
  • the number of the first blade 110 and the second blade 210 are not equal. It can be understood that the number of the first blade 110 and the number of the second blade 210 are not equal, which can avoid the overlap of the wake frequency of the first blade 110 and the blade frequency multiplication of the second blade 210, thereby avoiding the superposition of noise spectrum and the The resonance of the first blade 110 and the second blade 210 is avoided. Of course, in other embodiments of the present invention, the number of the first blade 110 and the second blade 210 may also be the same.
  • the first-stage impeller 10 and the second-stage impeller 20 are driven and rotated by two motors, respectively. It can be understood that the first-stage impeller 10 and the second-stage impeller 20 are driven and rotated by two motors, respectively, which can make the first-stage impeller 10 and the second-stage impeller 20 rotate at an arbitrary speed ratio, which greatly avoids the first The resonance phenomenon occurs between the first-stage impeller 10 and the second-stage impeller 20, thereby greatly reducing the working noise of the counter-rotating fan 1. Of course, in other embodiments of the present invention, the first-stage impeller 10 and the second-stage impeller 20 are driven and rotated by the same motor.
  • the counter-rotating fan 1 further includes a shroud 30 and two mesh covers 40, the shroud 40 surrounds the outer circumferential sides of the first-stage impeller 10 and the second-stage impeller 20, two The net cover 40 is connected to opposite sides of the enclosure 30. Therefore, the safety of the counter-rotating fan 1 during operation can be improved, and the phenomenon that the rotating blade hurts people can be avoided.
  • the enclosure 30 includes ring ribs and a plurality of transverse ribs.
  • the ring ribs are formed into a ring shape.
  • the plurality of transverse ribs are respectively connected to the ring ribs.
  • Two ends of each transverse rib are respectively connected to the two mesh covers 40.
  • the structure of the enclosure 30 is relatively stable, which further ensures the safety of the counter-rotating fan 1.
  • the counter-rotating fan 1 further includes a post, which is connected below the enclosure 30.
  • the first impeller and the second impeller are at a certain distance from the ground, so as to realize the air outlet at different heights.
  • the counter-rotating fan 1 according to a specific embodiment of the present invention is described below with reference to FIGS. 1-3.
  • the counter-rotating fan 1 of this embodiment includes a first-stage impeller 10 and a second-stage impeller 20 with opposite rotation directions, a shroud 30 and two mesh covers 40.
  • the first-stage impeller 10 is located on the air inlet side of the counter-rotating fan 1
  • the second-stage impeller 20 is located on the outlet side of the counter-rotating fan 1
  • the first-stage impeller 10 includes a plurality of first blades 110 distributed along its circumferential direction
  • the second-stage impeller 20 includes a plurality of second blades distributed along its circumferential direction
  • the axial width of the first blade 110 is greater than the axial width of the second blade 210.
  • the axial width of the first blade 110 is A1, and the axial width of the second blade 210 is A2.
  • A1 and A2 satisfy the relationship: 1 ⁇ A1 / A2 ⁇ 2.
  • the edges of each first blade 110 on the two sides in the circumferential direction are the first leading edge Le1 and the first trailing edge Te1 respectively, and the edges on the two sides of each second blade 210 in the circumferential direction are the second leading edge Le2 and the second trailing edge, respectively Te2, the leading edge bending angle ⁇ le of the first blade 110 and the second blade 210 both satisfy the condition: 15 ° ⁇ le ⁇ 75 °, the trailing edge bending angle ⁇ te of the first blade 110 and the second blade 210 satisfy the condition : 0 ° ⁇ te ⁇ 60 °.
  • the first-stage impeller 10 and the second-stage impeller 20 are driven and rotated by two motors, respectively.
  • the mesh cover 40 surrounds the outer peripheral sides of the first-stage impeller 10 and the second-stage impeller 20, and the two mesh covers 40 are connected on opposite sides of the enclosure 30.

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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 contrarotatif (1) qui comporte une roue à aubes de premier étage (10) et une roue à aubes de second étage (20), ces dernières ayant des directions de rotation opposées. La roue à aubes de premier étage (10) est située sur un côté entrée d'air du ventilateur contrarotatif (1), et la roue à aubes de second étage (20) est située sur un côté sortie d'air du ventilateur contrarotatif (1). La roue à aubes de premier étage (10) comprend une pluralité de premières aubes (110) réparties dans la direction circonférentielle, et la roue à aubes de second étage (20) comprend une pluralité de secondes aubes (210) réparties dans la direction circonférentielle. La largeur axiale des premières aubes (110) est supérieure à la largeur axiale des secondes aubes (210). Le présent ventilateur contrarotatif peut non seulement garantir que la direction de sortie d'air reste axiale, mais peut également augmenter la pression et le volume du courant d'air produit.
PCT/CN2018/122355 2018-10-15 2018-12-20 Ventilateur contrarotatif WO2020077802A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201821672645.XU CN209180089U (zh) 2018-10-15 2018-10-15 对旋风扇
CN201821672645.X 2018-10-15
CN201811198972.0A CN111043064A (zh) 2018-10-15 2018-10-15 对旋风扇
CN201811198972.0 2018-10-15

Publications (1)

Publication Number Publication Date
WO2020077802A1 true WO2020077802A1 (fr) 2020-04-23

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PCT/CN2018/122355 WO2020077802A1 (fr) 2018-10-15 2018-12-20 Ventilateur contrarotatif

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WO (1) WO2020077802A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114688049A (zh) * 2020-12-25 2022-07-01 广东美的白色家电技术创新中心有限公司 风机组件和空调器

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Publication number Priority date Publication date Assignee Title
US3083893A (en) * 1960-06-02 1963-04-02 Benson Mfg Co Contra-rotating blower
CN2695689Y (zh) * 2004-04-13 2005-04-27 郑宗殷 散热风扇
CN101761493A (zh) * 2008-12-22 2010-06-30 山洋电气株式会社 轴流式鼓风机
CN102094837A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102094836A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102094838A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102734185A (zh) * 2011-04-08 2012-10-17 山洋电气株式会社 对转式轴流鼓风机
JP2013170505A (ja) * 2012-02-21 2013-09-02 Rhythm Watch Co Ltd 二重反転式送風機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3083893A (en) * 1960-06-02 1963-04-02 Benson Mfg Co Contra-rotating blower
CN2695689Y (zh) * 2004-04-13 2005-04-27 郑宗殷 散热风扇
CN101761493A (zh) * 2008-12-22 2010-06-30 山洋电气株式会社 轴流式鼓风机
CN102094837A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102094836A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102094838A (zh) * 2009-12-14 2011-06-15 国立大学法人东京大学 双重反转式轴流鼓风机
CN102734185A (zh) * 2011-04-08 2012-10-17 山洋电气株式会社 对转式轴流鼓风机
JP2013170505A (ja) * 2012-02-21 2013-09-02 Rhythm Watch Co Ltd 二重反転式送風機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114688049A (zh) * 2020-12-25 2022-07-01 广东美的白色家电技术创新中心有限公司 风机组件和空调器
CN114688049B (zh) * 2020-12-25 2024-02-20 广东美的白色家电技术创新中心有限公司 风机组件和空调器

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