WO2012039092A1 - Axial flow blower - Google Patents
Axial flow blower Download PDFInfo
- Publication number
- WO2012039092A1 WO2012039092A1 PCT/JP2011/004497 JP2011004497W WO2012039092A1 WO 2012039092 A1 WO2012039092 A1 WO 2012039092A1 JP 2011004497 W JP2011004497 W JP 2011004497W WO 2012039092 A1 WO2012039092 A1 WO 2012039092A1
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- WIPO (PCT)
- Prior art keywords
- blade
- impeller
- axial
- radial direction
- leading edge
- Prior art date
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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
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
Definitions
- the present invention relates to an axial blower used for, for example, an air conditioner or a ventilation device.
- FIG. 8 is a front view of a conventional axial blower. It is comprised by the impeller 1 which has the boss
- the following technologies are known as techniques for reducing the noise of the axial blower so far. That is, by adding a plurality of triangular projections that form a saw-like shape in the chord direction to the entire leading edge of the blade, forming a vertical vortex by tearing the suction air, suppressing the separation of the suction air across the entire front edge, There is a method of reducing the turbulent noise by attaching an air flow to the blade, and suppressing the leakage of the blown air to the outer peripheral side, thereby improving the efficiency of the blower (for example, see Patent Document 1).
- FIG. 9 is a diagram showing a flow field in the vicinity of a leading edge of a blade of a conventional axial fan.
- the airflow flowing into the blade 3 includes an upstream turbulent vortex 4.
- This upstream turbulent vortex 4 develops as it travels downstream, induces pressure fluctuations on the blade surface, and generates noise.
- Patent Document 1 since a protrusion having a saw-shaped sharp tip is added to the entire leading edge portion, the airflow flowing into the leading edge of the wing is discontinuously cut off. There is a problem that noise is increased due to disturbance.
- the present invention has been made to solve such a problem, and an object thereof is to provide a low-noise axial fan.
- the invention according to claim 1 is an impeller having a boss rotating around an axis and a plurality of blades disposed on an outer peripheral portion of the boss, the leading edge of the blade being continuous in the radial direction. It is characterized by having a smooth wave shape having uneven portions.
- the pitch distance which is the distance between the apexes of the smooth wavy convex portions having the concave and convex portions continuously in the radial direction at the leading edge of the blade, becomes larger toward the outer peripheral side of the blade. It is characterized by being.
- the pitch distance which is the distance between the apexes of the smooth wavy convex portions having continuous irregularities in the radial direction at the leading edge of the blade, flows from the leading edge of the blade. It is characterized in that it is determined in correlation with the radial distribution of the scale of the upstream turbulent vortex generated during the process.
- the invention described in claim 4 includes a bell mouth that surrounds the impeller, wherein the height of the bell mouth is larger than the height of the impeller.
- the invention according to claim 5 includes a bell mouth that surrounds the impeller, and the height of the bell mouth is smaller than the height of the impeller.
- the axial blower according to the present invention is an impeller having a boss rotating around an axial center and a plurality of blades disposed on an outer peripheral portion of the boss, the leading edge of the blade being in the radial direction.
- Low noise can be realized by forming a smooth wave shape having continuously uneven portions.
- the pitch distance which is the distance between the vertices of the smooth wavy convex portion having continuous irregularities in the radial direction at the leading edge of the wing, increases toward the outer peripheral side of the wing, Low noise can be achieved.
- the pitch distance which is the distance between the vertices of the smooth wavy convex portion having continuous irregularities in the radial direction at the leading edge of the blade, is an upstream turbulent vortex generated when airflow flows from the leading edge of the blade.
- the noise is further reduced by being determined in correlation with the radial distribution of the scale.
- Embodiment 1 of this invention It is a perspective view of the axial-flow fan which concerns on Embodiment 1 of this invention. It is a front view of the axial-flow fan which concerns on Embodiment 1 of this invention. It is a figure which shows typically the flow field of the front edge vicinity of the blade
- FIG. 1 to 3 are diagrams for explaining an axial blower according to Embodiment 1 of the present invention.
- FIG. 1 is a perspective view of an axial blower according to Embodiment 1 of the present invention
- FIG. 2 is a front view of the axial blower according to Embodiment 1 of the present invention
- FIG. 3 is according to the present invention. It is a figure which shows typically the flow field near the front edge of the blade
- FIG. 9 is a diagram schematically showing a flow field in the vicinity of the leading edge of a blade of a conventional axial fan.
- an axial blower includes an impeller 1 having a boss 2 that rotates around an axial center and a plurality of blades 3 that are disposed on the outer periphery of the boss 2. It is comprised by.
- Each blade 3 is surrounded by a leading edge 31, a trailing edge 32, an inner peripheral end 33, and an outer peripheral end 34. Further, the leading edge 31 of the blade 3 has a smooth wave shape having uneven portions continuously in the radial direction from the inner peripheral end 33 side to the outer peripheral end 34 side.
- the airflow flowing into the blade 3 includes an upstream turbulent vortex 4.
- the air flow including the upstream turbulent vortex 4 passes through the leading edge 31 of the blade 3, the following effects are exhibited.
- the upstream turbulent vortex 4 is divided so that the length in the radial direction is shortened by the front edge 31 having a smooth wave shape having uneven portions continuously in the radial direction from the inner peripheral end 33 side to the outer peripheral end 34 side. As a result, a divided vortex 4a is formed. Thereby, the upstream turbulent vortex 4 is randomized and the development of the vortex is suppressed, so that noise can be reduced.
- the adjacent divided vortices 4a weaken each other's strength as they advance downstream. Since the interference occurs in a matching manner and a vortex weaker than the original is formed as a whole, noise can be reduced.
- FIGS. 3 and 9 show the vorticity isolines 6 on the blade surface.
- the vorticity isolines 6 are substantially line-shaped.
- the vortex is formed in the above process.
- the vorticity isolines 6 are wavy in the radial direction.
- FIG. 4 and 5 are diagrams for explaining the axial blower according to Embodiment 2 of the present invention.
- FIG. 4 is a front view of an axial blower according to Embodiment 2 of the present invention
- FIG. 5 is a schematic view of a bell mouth form and a flow field of the axial blower according to Embodiment 2 of the present invention.
- the pitch distance L is the outer circumference of the wing 3. It is configured to be larger toward the side.
- an axial-flow fan usually leaves the impeller 1 with a small clearance between the impeller 1 and the outside of the impeller 1.
- a bell mouth 5 is installed so as to surround it.
- the flow velocity of the airflow flowing into the blade 3 increases in proportion to the radius of the impeller 1, and thus increases toward the outer peripheral side. For example, as shown in FIG. 5, this is often the case when the height H2 of the bell mouth 5 is greater than the height of the impeller 1 (the maximum height in the axial direction of the blade 3) H1 (H2> H1). .
- the scale of the upstream turbulent vortex 4 also increases toward the outer peripheral side. Therefore, by being configured such that the pitch distance L increases toward the outer peripheral side of the blade 3, the upstream turbulence vortex 4 is effectively divided, and noise can be further reduced.
- FIG. 7 is a schematic view of a bell mouth form and a flow field of the axial blower according to Embodiment 3 of the present invention.
- FIG. 6 is a front view of an axial blower according to Embodiment 3 of the present invention
- FIG. 7 is a schematic view of a bell mouth form and a flow field of the axial blower according to Embodiment 3 of the present invention.
- FIG. 6 is a front view of an axial blower according to Embodiment 3 of the present invention
- the pitch distance L is the upstream turbulence vortex. It is configured to be determined in correlation with the radial distribution of the scale of 4.
- a bell mouth 5 is installed outside the impeller 1 so as to surround the impeller 1 with a minute gap between the impeller 1 and the impeller 1.
- the airflow does not sufficiently flow into the wing 3 in the vicinity of the outer peripheral edge 34, and the airflow flowing into the wing is such that the airflow becomes the largest in the vicinity of the midway in the radial direction of the wing 3, as indicated by an arrow 7 in FIG. Distribution.
- the radial distribution of the scale of the upstream turbulent vortex 4 is also a distribution in which the vortex scale becomes the largest in the vicinity of the midway in the radial direction. Can be reduced.
- further noise reduction can be realized by increasing / decreasing the pitch distance L according to the scale of the upstream turbulence vortex 4 generated when the airflow flows from the leading edge of the blade.
- the above description is an example, and even if the radial distribution of the upstream turbulent vortex 4 changes due to other conditions, the same noise reduction effect can be obtained by determining the pitch distance L in correlation with this.
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- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
また、特許文献1のような先行技術では、前縁部全体に鋸状の鋭利な先端を有する突起を付加していることにより、翼の前縁に流入する気流を不連続に切り裂くため、むしろ乱れが生じて騒音が増大するという問題がある。 The problem of the conventional axial fan will be described with reference to FIG. FIG. 9 is a diagram showing a flow field in the vicinity of a leading edge of a blade of a conventional axial fan. The airflow flowing into the
In addition, in the prior art such as
さらに、翼の前縁における半径方向に連続的に凹凸部を有する滑らかな波形状の凸部の頂点間の距離であるピッチ距離が、翼の外周側ほど大きくなっていることにより、より一層の低騒音化を実現できる。
さらに、翼の前縁における半径方向に連続的に凹凸部を有する滑らかな波形状の凸部の頂点間の距離であるピッチ距離が、翼の前縁から気流が流入する際に生じる上流乱れ渦のスケールの半径方向分布に相関して決定されていることにより、より一層の低騒音化を実現できる。 The axial blower according to the present invention is an impeller having a boss rotating around an axial center and a plurality of blades disposed on an outer peripheral portion of the boss, the leading edge of the blade being in the radial direction. Low noise can be realized by forming a smooth wave shape having continuously uneven portions.
Furthermore, since the pitch distance, which is the distance between the vertices of the smooth wavy convex portion having continuous irregularities in the radial direction at the leading edge of the wing, increases toward the outer peripheral side of the wing, Low noise can be achieved.
In addition, the pitch distance, which is the distance between the vertices of the smooth wavy convex portion having continuous irregularities in the radial direction at the leading edge of the blade, is an upstream turbulent vortex generated when airflow flows from the leading edge of the blade. The noise is further reduced by being determined in correlation with the radial distribution of the scale.
図1~図3は、本発明の実施の形態1に係る軸流送風機を説明するための図である。具体的には、図1は本発明の実施の形態1に係る軸流送風機の斜視図、図2は本発明の実施の形態1に係る軸流送風機の正面図、図3は本発明に係る軸流送風機の翼の前縁付近の流れ場を模式的に示す図である。また、図9は従来の軸流送風機の翼の前縁付近の流れ場を模式的に示す図である。
1 to 3 are diagrams for explaining an axial blower according to
より一層の騒音低減を実現するためには、以下のような構成にするのが望ましい。図4および図5は、本発明の実施の形態2に係る軸流送風機を説明するための図である。具体的には、図4は本発明の実施の形態2に係る軸流送風機の正面図、図5は本発明の実施の形態2に係る軸流送風機のベルマウスの形態および流れ場を模式的に示す図である。
In order to realize further noise reduction, the following configuration is desirable. 4 and 5 are diagrams for explaining the axial blower according to
より一層の騒音低減を実現するための別の方法として、以下のような構成にするのが望ましい。図6および図7は、本発明の実施の形態3に係る軸流送風機を説明するための図である。具体的には、図6は本発明の実施の形態3に係る軸流送風機の正面図、図7は本発明の実施の形態3に係る軸流送風機のベルマウスの形態および流れ場を模式的に示す図である。
As another method for realizing further noise reduction, the following configuration is desirable. 6 and 7 are diagrams for explaining the axial blower according to
図7に示すように、ベルマウス5の高さH2が羽根車1の高さ(翼3の軸方向の最大高さ)H1よりも小さい(H2<H1)場合には、翼3の外周端34の前縁31側では、下流側から上流側へ部分的に逆流する漏れ渦8が発生する。この場合、外周端34近傍では翼3は気流が十分には流入しなくなり、翼に流入する気流は、図7の矢印7で示すように、翼3の半径方向中腹付近で最も大きくなるような分布になる。したがって、上流乱れ渦4のスケールの半径方向分布も、半径方向中腹付近で最も渦のスケールが大きくなるような分布となるため、ピッチ距離Lをこれに相関させて決定することにより、より一層騒音を低減することができる。このようにピッチ距離Lを、翼の前縁から気流が流入する際に生じる上流乱れ渦4のスケールに合わせて増減することで、より一層の騒音低減を実現することができる。上記の説明は一例であり、その他の条件により上流乱れ渦4の半径方向分布が変化しても、ピッチ距離Lをこれに相関させて決定することにより、同様の騒音低減効果が得られる。 The effects obtained by the above configuration will be described below. The relationship between the corrugated pitch distance L and the vortex scale is the same as that described in the second embodiment, and a description thereof will be omitted.
As shown in FIG. 7, when the height H2 of the
Claims (5)
- 軸心まわりに回転するボスと、前記ボスの外周部に配設される複数枚の翼とを有する羽根車であって、
前記翼の前縁は、半径方向に連続的に凹凸部を有する滑らかな波形状を成していることを特徴とする軸流送風機。 An impeller having a boss rotating around an axis and a plurality of blades disposed on an outer periphery of the boss,
The axial flow blower according to claim 1, wherein the leading edge of the blade has a smooth wave shape having continuous uneven portions in a radial direction. - 前記翼の前縁における半径方向に連続的に凹凸部を有する滑らかな波形状の凸部の頂点間の距離であるピッチ距離が、翼の外周側ほど大きくなっていることを特徴とする請求項1記載の軸流送風機。 The pitch distance, which is the distance between the vertices of smooth wave-shaped convex portions having uneven portions continuously in the radial direction at the leading edge of the blade, is increased toward the outer peripheral side of the blade. 1. An axial blower according to 1.
- 前記翼の前縁における半径方向に連続的に凹凸部を有する滑らかな波形状の凸部の頂点間の距離であるピッチ距離が、翼の前縁から気流が流入する際に生じる上流乱れ渦のスケールの半径方向分布に相関して決定されていることを特徴とする請求項1記載の軸流送風機。 The pitch distance, which is the distance between the vertices of smooth corrugated convex portions having continuous irregularities in the radial direction at the leading edge of the blade, is the upstream turbulent vortex generated when the airflow flows from the leading edge of the blade. The axial-flow fan according to claim 1, wherein the axial-flow fan is determined in correlation with a radial distribution of the scale.
- 前記羽根車を囲繞するベルマウスを備え、前記ベルマウスの高さが前記羽根車の高さより大きいことを特徴とする請求項1または2記載の軸流送風機。 3. An axial blower according to claim 1, further comprising a bell mouth surrounding the impeller, wherein the height of the bell mouth is greater than the height of the impeller.
- 前記羽根車を囲繞するベルマウスを備え、前記ベルマウスの高さが前記羽根車の高さより小さいことを特徴とする請求項1または3記載の軸流送風機。
The axial blower according to claim 1 or 3, further comprising: a bell mouth that surrounds the impeller, wherein the height of the bell mouth is smaller than the height of the impeller.
Priority Applications (2)
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JP2012534913A JP5602237B2 (en) | 2010-09-21 | 2011-08-08 | Axial blower |
CN201180045326.0A CN103140684B (en) | 2010-09-21 | 2011-08-08 | Axial-flow blower |
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JP2010210977 | 2010-09-21 | ||
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PCT/JP2011/004497 WO2012039092A1 (en) | 2010-09-21 | 2011-08-08 | Axial flow blower |
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JP (1) | JP5602237B2 (en) |
CN (1) | CN103140684B (en) |
TW (1) | TWI473946B (en) |
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2013249763A (en) * | 2012-05-31 | 2013-12-12 | Denso Corp | Axial flow blower |
JP2013249762A (en) * | 2012-05-31 | 2013-12-12 | Denso Corp | Air blower |
JP2015063912A (en) * | 2013-09-24 | 2015-04-09 | 株式会社デンソー | Blower |
WO2017061236A1 (en) * | 2015-10-05 | 2017-04-13 | 日立マクセル株式会社 | Blower |
WO2018198300A1 (en) * | 2017-04-28 | 2018-11-01 | 三菱電機株式会社 | Propeller fan |
WO2019035153A1 (en) * | 2017-08-14 | 2019-02-21 | 三菱電機株式会社 | Impeller, fan, and air conditioning device |
WO2022201103A1 (en) * | 2021-03-25 | 2022-09-29 | Cooling_Pl Zdziech Spolka Jawna | Axial fan with serrated blade leading edges |
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JP6673702B2 (en) * | 2016-01-22 | 2020-03-25 | 日本スピンドル製造株式会社 | Cooling tower with axial blower |
TWI606776B (en) * | 2016-10-05 | 2017-11-21 | 川湖科技股份有限公司 | Slide rail assembly |
USD901669S1 (en) | 2017-09-29 | 2020-11-10 | Carrier Corporation | Contoured fan blade |
WO2019069374A1 (en) * | 2017-10-03 | 2019-04-11 | 三菱電機株式会社 | Propeller fan and axial flow blower |
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- 2011-08-08 WO PCT/JP2011/004497 patent/WO2012039092A1/en active Application Filing
- 2011-08-08 JP JP2012534913A patent/JP5602237B2/en active Active
- 2011-08-08 CN CN201180045326.0A patent/CN103140684B/en active Active
- 2011-08-25 TW TW100130455A patent/TWI473946B/en active
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JPH08189497A (en) * | 1994-11-08 | 1996-07-23 | Mitsubishi Heavy Ind Ltd | Propeller fan |
JP2000087898A (en) * | 1998-09-08 | 2000-03-28 | Matsushita Refrig Co Ltd | Axial flow blower |
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Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013249763A (en) * | 2012-05-31 | 2013-12-12 | Denso Corp | Axial flow blower |
JP2013249762A (en) * | 2012-05-31 | 2013-12-12 | Denso Corp | Air blower |
CN104364532A (en) * | 2012-05-31 | 2015-02-18 | 株式会社电装 | Air blower |
CN104364532B (en) * | 2012-05-31 | 2017-03-29 | 株式会社电装 | Aerator |
JP2015063912A (en) * | 2013-09-24 | 2015-04-09 | 株式会社デンソー | Blower |
WO2017061236A1 (en) * | 2015-10-05 | 2017-04-13 | 日立マクセル株式会社 | Blower |
WO2018198300A1 (en) * | 2017-04-28 | 2018-11-01 | 三菱電機株式会社 | Propeller fan |
JPWO2018198300A1 (en) * | 2017-04-28 | 2019-12-19 | 三菱電機株式会社 | Propeller fan |
WO2019035153A1 (en) * | 2017-08-14 | 2019-02-21 | 三菱電機株式会社 | Impeller, fan, and air conditioning device |
JPWO2019035153A1 (en) * | 2017-08-14 | 2019-12-12 | 三菱電機株式会社 | Impeller, blower, and air conditioner |
WO2022201103A1 (en) * | 2021-03-25 | 2022-09-29 | Cooling_Pl Zdziech Spolka Jawna | Axial fan with serrated blade leading edges |
Also Published As
Publication number | Publication date |
---|---|
CN103140684B (en) | 2015-09-30 |
JPWO2012039092A1 (en) | 2014-02-03 |
TW201217654A (en) | 2012-05-01 |
TWI473946B (en) | 2015-02-21 |
CN103140684A (en) | 2013-06-05 |
JP5602237B2 (en) | 2014-10-08 |
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