WO2010137140A1 - Multi-blade fan - Google Patents
Multi-blade fan Download PDFInfo
- Publication number
- WO2010137140A1 WO2010137140A1 PCT/JP2009/059710 JP2009059710W WO2010137140A1 WO 2010137140 A1 WO2010137140 A1 WO 2010137140A1 JP 2009059710 W JP2009059710 W JP 2009059710W WO 2010137140 A1 WO2010137140 A1 WO 2010137140A1
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- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- casing
- suction port
- blade
- air
- Prior art date
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Classifications
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00457—Ventilation unit, e.g. combined with a radiator
- B60H1/00471—The ventilator being of the radial type, i.e. with radial expulsion of the air
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
- F04D29/054—Arrangements for joining or assembling shafts
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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
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
- F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
-
- 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
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- 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
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/51—Inlet
Definitions
- the present invention relates to a multiblade fan, and more particularly to a multiblade fan that can improve noise performance or air blowing performance.
- a general multi-blade fan includes a scroll casing having a bell mouth-shaped suction port and an impeller accommodated in the casing.
- the impeller is a multi-blade impeller (sirocco fan) formed by arranging a plurality of blades in an annular shape, and is housed in the casing with its rotating shaft directed toward the suction port of the casing.
- the conventional multi-blade blower adopts a configuration in which the suction port is deformed in accordance with the suction flow velocity (see Patent Document 1), a configuration in which a taper is provided on the end of the blade (see Patent Document 2), and the like. Yes.
- Patent Document 1 a configuration in which the suction port is deformed in accordance with the suction flow velocity
- Patent Document 2 a configuration in which a taper is provided on the end of the blade
- the multiblade fan performs static pressure recovery using a scroll-type casing having a predetermined expansion. For this reason, when the air intake position changes, the speed of the air flow in the impeller changes, and the deviation of the air flow toward the main plate changes. For this reason, in the structure which changes the shape of the blade
- An object of the present invention is to provide a multiblade fan that can improve noise performance or air blowing performance.
- a multiblade blower comprises a scroll-type casing having a bell mouth-like suction port, a plurality of blades arranged in an annular shape, and a rotating shaft directed toward the suction port.
- a multi-blade blower comprising an impeller housed in the casing, wherein the central axis of the suction port and the rotational axis of the impeller intersect with each other while having an inclination angle, or are mutually twisted Due to the positional relationship, the gap between the suction port and the impeller is enlarged from the rotating shaft of the impeller toward the vicinity of the outlet of the casing.
- the gap between the suction port and the impeller is enlarged from the rotating shaft of the impeller toward the vicinity of the outlet of the casing.
- the air flowing into the impeller from the suction port can gently curve in the impeller and pass between the blades.
- the velocity distribution of the intake air in the impeller (air flow bias) and the inflow angle to the blades change relatively, and the velocity distribution of the air passing between the blades is made uniform in the direction of the rotation axis of the impeller.
- FIG. 1 is a plan sectional view showing a multiblade blower according to this embodiment.
- 2 is a cross-sectional view taken along line AA showing the multiblade fan shown in FIG.
- FIG. 3 is an explanatory view showing the operation of the multiblade fan shown in FIG. 1.
- FIG. 4 is an explanatory diagram showing the operation of the multiblade fan shown in FIG. 1.
- FIG. 5 is a graph showing noise characteristics with respect to the position of the gap between the suction port and the impeller.
- FIG. 6 is a graph showing the results of the performance test of the multiblade fan.
- FIG. 7 is a graph showing the results of the performance test of the multiblade fan.
- FIG. 8 is an explanatory diagram showing a configuration of the multiblade fan shown in FIG. 1.
- FIG. 1 is a plan sectional view showing a multiblade blower according to this embodiment.
- 2 is a cross-sectional view taken along line AA showing the multiblade fan shown in FIG.
- FIG. 9 is an explanatory view showing a modification of the multiblade blower described in FIG. 1.
- FIG. 10 is an explanatory view showing a modification of the multiblade blower described in FIG. 1.
- FIG. 11 is a block diagram showing a conventional multiblade fan.
- FIG. 12 is an explanatory view showing the operation of the multiblade fan shown in FIG. 11.
- the multi-blade fan 1 is a blower having a multi-blade impeller (sirocco fan), and is applied to, for example, air conditioning equipment, duct fans, ventilation fans, and the like. Moreover, this multiblade fan 1 may employ
- the multiblade blower 1 includes a casing 2, an impeller 3, and a drive motor 4 (see FIGS. 1 and 2).
- the casing 2 is, for example, a scroll-type casing, and includes a casing body 21, a suction port 22, and an air outlet 23.
- the casing body 21 has a scroll shape in plan view.
- the suction port 22 is a bell mouth-shaped suction port, and is formed on one side of the casing body 21 (upper surface in the axial direction of the scroll shape) and at the center of the scroll shape.
- the air outlet 23 is formed on the peripheral surface of the casing body 21 (a scroll-shaped surface in the turning direction).
- the casing 2 is made of, for example, resin and is formed by die cutting.
- the impeller 3 is a multi-blade impeller (sirocco fan) formed by arranging a plurality of blades 31 in a ring shape.
- the impeller 3 is arranged with its rotation axis m facing the suction port 22 side of the casing 2 and its circumferential surface facing the circumferential direction of the casing 2.
- the impeller 3 is configured by arranging and fixing a plurality of blades 31 in a ring shape with a predetermined interval along the peripheral edge of the substantially disc-shaped main plate 32. Thereby, a blade ring by a plurality of blades 31 is formed on the main plate 32.
- a reinforcing annular member 33 is fitted into the end portions (end portions on the side opposite to the main plate 32) of the blades 31.
- the impeller 3 is accommodated in the casing 2 with the end of the blade 31 facing the suction port 22 of the casing 2 and the peripheral surface of the blade ring facing the circumferential direction of the casing 2.
- the drive motor 4 is a motor that drives the impeller 3 to rotate.
- the drive motor 4 is arranged to be connected to the main plate 32 of the impeller 3 from the lower surface side of the casing 2.
- the drive motor 4 is ON / OFF controlled by an external switch, for example.
- the central axis l of the suction port 22 is the bell-mouth shaped central axis of the suction port 22.
- the gap L from the suction port 22 to the blade 31 of the impeller 3 is enlarged near the air outlet 23 of the casing 2 (FIGS. 1 and 1). 2).
- the gap L from the opening surface of the suction port 22 to the end of the blade 31 of the impeller 3 is the rotational axis m of the impeller 3. It is enlarged as it goes to the blower outlet 23 vicinity of the casing 2 from.
- size of the clearance gap L between the suction inlet 22 and the impeller 3 can be suitably selected according to the specification etc. of the multiblade fan 1.
- the gap L between the suction port 22 and the impeller 3 is enlarged from the rotation shaft m of the impeller 3 toward the vicinity of the air outlet 23 of the casing 2.
- the inflowing air can gently curve in the impeller 3 (see FIG. 3).
- the speed of the air passing between the blades 31 and 31 as compared with the configuration in which the air flows biased toward the main plate (see FIG. 11).
- the distribution is made uniform in the axial direction of the impeller 3. Thereby, the noise performance and ventilation performance of the multiblade fan 1 are improved.
- the air passage in the casing body 21 is expanded most in the vicinity of the air outlet 23 (see FIG. 1).
- the air easily flows, the inertial force is increased by increasing the flow velocity of the air passing through the blade 31 of the impeller 3, and the velocity distribution of the air passing between the blades 31, 31 is increased.
- the bias toward the main plate side is further increased. Therefore, at this position, the gap L between the suction port 22 and the impeller 3 is enlarged in the vicinity of the air outlet 23 (see FIG. 2), so that the velocity distribution of the intake air in the impeller 3 and the blade 31 are increased. Is greatly changed, and a large deviation of the velocity distribution of the air passing between the blades 31, 31 toward the main plate is effectively made uniform. Thereby, a noise characteristic improves efficiently.
- the position where the gap L between the suction port 22 and the impeller 3 is maximized is appropriately selected based on the scroll shape of the casing 2 and the like.
- a circumferential angle ⁇ [[ ⁇ [] applied to the rotational direction of the impeller 3 with reference to a direction parallel to the axial direction of the outlet 23 of the casing 2 through the rotational axis m of the impeller 3. °] is defined (see FIG. 1).
- the central axis l of the suction port 22 of the casing 2 and the rotational axis m of the impeller 3 are in a positional relationship in which they intersect with each other while having an inclination angle ⁇ , or in a positional relationship of twists.
- a circumferential angle ⁇ having suitable noise characteristics may be selected.
- FIG. 5 shows the relationship between the circumferential angle ⁇ and the noise characteristics.
- the noise characteristic is shown by a noise difference with the conventional example as a reference (0 [dB]).
- [performance test] 6 and 7 are graphs showing the results of the performance test of the multiblade fan. In this embodiment, performance tests on (1) blowing performance (static pressure performance) and (2) noise performance were performed.
- the multi-blade fan 1 of the example has improved air blowing characteristics and noise characteristics as compared to the conventional multi-blade fan.
- the static pressure is increased by about 10 [Pa]
- the noise is reduced by about 1 [dB].
- the inertial force is increased by increasing the flow velocity of the air passing between the blades 31 and 31 of the impeller 3, and the velocity distribution of the air passing between the blades 31 and 31 toward the main plate is increased.
- the bias is further increased. Therefore, by setting a large gap L between the suction port 22 and the impeller 3 at this position, the velocity distribution of the intake air in the impeller 3 and the inflow angle ⁇ to the blade 31 are greatly changed, and the blade The large deviation of the velocity distribution of the air passing between 31 and 31 toward the main plate is effectively made uniform. Thereby, there exists an advantage which can improve a noise characteristic effectively.
- the suction axis 22 and the rotation axis m of the impeller 3 have a tilt angle ⁇ and intersect each other, or are in a twisted relationship with each other.
- the gap L between the mouth 22 and the impeller 3 is adjusted. That is, the gap L between the suction port 22 and the impeller 3 is adjusted by adjusting the positional relationship between the central axis l of the suction port 22 and the rotation axis m of the impeller 3. Due to this gap L, the velocity distribution of the intake air in the impeller 3 and the inflow angle ⁇ to the blade 31 change relatively, and the velocity distribution of the air passing between the blades 31, 31 is made uniform. . Therefore, there is an advantage that the velocity distribution of the air passing between the blades 31 and 31 can be made uniform with a simple configuration as compared with the configuration in which the dimensions and shapes of the impeller and the bell mouth are changed in a complicated manner.
- both the central axis l of the suction port 22 and the rotation axis m of the impeller 3 are arranged to be inclined with respect to the casing body 21, so that the central axis l of the suction port 22 and The positional relationship (inclination angle ⁇ ) with the rotation axis m of the impeller 3 is adjusted.
- the inclination angle ⁇ can be formed without difficulty in design as compared with a configuration in which only one of the central axis l of the suction port 22 and the rotation axis m of the impeller 3 is inclined with respect to the casing body 21.
- a step is provided in a part of the connection portion between the outer periphery of the bell mouth shape of the suction port 22 and the wall surface of the casing main body 21, and the bell mouth shape of the suction port 22 is formed in the casing by this step. It is comprised so that it may incline with respect to the wall surface of the main body 21 (refer FIG. 2). Further, the drive motor 4 is attached to the casing body 21 while its rotating shaft is inclined with respect to the wall surface of the casing body 21. An impeller 3 is attached to the drive motor 4. Thus, both the central axis l of the suction port 22 and the rotation axis m of the impeller 3 are arranged to be inclined with respect to the casing body 21.
- the present invention is not limited to this, and only the central axis l of the suction port 22 or only the rotation axis m of the impeller 3 is arranged to be inclined with respect to the casing body 21, thereby The positional relationship with the rotation axis m of the impeller 3 may be adjusted (see FIGS. 9 and 10).
- the multiblade blower according to the present invention is useful in that noise performance or air blowing performance can be improved.
- 1 multiblade blower 2 casing, 21 casing body, 22 inlet, 23 outlet, 3 impeller, 31 blade, 32 main plate, 33 annular member, 4 drive motor
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Abstract
Description
この多翼送風機1は、多翼羽根車(シロッコファン)を有する送風機であり、例えば、空調設備、ダクト扇、換気扇などに適用される。また、この多翼送風機1は、片側吸込式を採用しても良いし、両側吸込式を採用しても良い。この実施の形態では、一例として、片側吸込式を採用する多翼送風機1について説明する。 [Multi-blade blower]
The
一般に、(1)吸込口の中心軸lと羽根車の回転軸mとが同軸上にある構成では、吸込口から羽根車に流入した空気に慣性力が作用する(図11参照)。このため、羽根車内では、空気が主板寄りに偏って流れる傾向がある。すると、羽根車の翼間(翼と翼の隙間)を通過する空気の速度分布(翼間から吹き出す空気の速度分布)が、羽根車の軸方向にて不均一となる。すると、流速変動が生じ易くなるため、空気の圧力変動や乱れが大きくなり、騒音悪化や送風性能の低下などが生じるおそれがある。また、かかる構成では、(2)羽根車内にて、翼に対して急な(鋭い)角度δにて流入して翼間を通過する(図12参照)。すると、羽根車が十分に機能しないため、送風性能が十分に発揮されないおそれがある。 [Relationship between inlet and impeller]
In general, (1) In the configuration in which the central axis l of the suction port and the rotation shaft m of the impeller are coaxial, inertial force acts on the air flowing into the impeller from the suction port (see FIG. 11). For this reason, in an impeller, there exists a tendency for air to flow biased toward the main plate. Then, the velocity distribution of air passing between the blades of the impeller (the gap between the blades) (the velocity distribution of the air blown from between the blades) becomes non-uniform in the axial direction of the impeller. As a result, fluctuations in the flow velocity are likely to occur, resulting in large fluctuations in air pressure and turbulence, which may cause noise deterioration and deterioration in blowing performance. In such a configuration, (2) in the impeller, it flows at a steep (sharp) angle δ with respect to the blades and passes between the blades (see FIG. 12). Then, since an impeller does not fully function, there exists a possibility that ventilation performance may not fully be exhibited.
図6および図7は、多翼送風機の性能試験の結果を示すグラフである。この実施の形態では、(1)送風性能(静圧性能)および(2)騒音性能に関する性能試験が行われた。 [performance test]
6 and 7 are graphs showing the results of the performance test of the multiblade fan. In this embodiment, performance tests on (1) blowing performance (static pressure performance) and (2) noise performance were performed.
以上説明したように、この多翼送風機1では、(1)吸込口22と羽根車3との隙間Lが羽根車3の回転軸mからケーシング2の吹出口23近傍に向かうに連れて拡大される(図1および図2参照)。かかる構成では、吸込口22から羽根車3に流入した空気が羽根車3内にて緩やかにカーブして翼31、31間を通過できる(図3参照)。すると、羽根車3内における吸入空気の速度分布(空気流れの偏り)や翼31への流入角度δが相対的に変化して、翼31、31間を通過した空気の速度分布が羽根車3の回転軸方向に均一化される。これにより、多翼送風機1の騒音性能や送風性能が向上する利点がある。 [effect]
As described above, in this
なお、この多翼送風機1では、吸込口22の中心軸lと羽根車3の回転軸mとの位置関係(傾斜角φを有しつつ相互に交差する位置関係あるいは相互にねじれの位置関係)の調整にあたり、以下の構成が採用され得る(図8~図10参照)。 [Modification]
In this
Claims (3)
- ベルマウス状の吸込口を有するスクロール型のケーシングと、複数の翼を環状に配列して成ると共に回転軸を前記吸込口に向けて前記ケーシングに収容される羽根車とを備える多翼送風機であって、
前記吸込口の中心軸と前記羽根車の回転軸とが傾斜角を有しつつ相互に交差する位置関係あるいは相互にねじれの位置関係にあることにより、前記吸込口と前記羽根車との隙間が前記羽根車の回転軸から前記ケーシングの吹出口近傍に向かうに連れて拡大されることを特徴とする多翼送風機。 A multi-blade blower comprising a scroll-type casing having a bell mouth-shaped suction port, and a plurality of blades arranged in an annular shape and an impeller accommodated in the casing with a rotating shaft directed toward the suction port. And
Since the central axis of the suction port and the rotation shaft of the impeller have a tilt angle and are in a positional relationship crossing each other or in a positional relationship of twisting, a clearance between the suction port and the impeller is reduced. A multi-blade blower that is enlarged from the rotating shaft of the impeller toward the vicinity of the air outlet of the casing. - 前記ケーシングのケーシング本体に対して前記吸込口の中心軸が傾斜して配置されることにより、前記吸込口の中心軸と前記羽根車の回転軸との位置関係が調整される請求項1に記載の多翼送風機。 The positional relationship between the central axis of the suction port and the rotation shaft of the impeller is adjusted by arranging the central axis of the suction port to be inclined with respect to the casing body of the casing. Multi-wing blower.
- 前記ケーシングのケーシング本体に対して前記羽根車の回転軸が傾斜して配置されることにより、前記吸込口の中心軸と前記羽根車の回転軸との位置関係が調整される請求項1または2に記載の多翼送風機。 The positional relationship between the center axis of the suction port and the rotation axis of the impeller is adjusted by arranging the rotation axis of the impeller to be inclined with respect to the casing body of the casing. The multiblade blower described in 1.
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
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US13/201,006 US20120009059A1 (en) | 2009-05-27 | 2009-05-27 | Multiblade fan |
PCT/JP2009/059710 WO2010137140A1 (en) | 2009-05-27 | 2009-05-27 | Multi-blade fan |
KR1020117020925A KR20110113660A (en) | 2009-05-27 | 2009-05-27 | Multi-blade fan |
CN200980156448.XA CN102317633B (en) | 2009-05-27 | 2009-05-27 | Multi-blade fan |
JP2011515796A JP5230805B2 (en) | 2009-05-27 | 2009-05-27 | Multi-blade blower |
TW098130902A TWI388730B (en) | 2009-05-27 | 2009-09-14 | Multi-wing blower |
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PCT/JP2009/059710 WO2010137140A1 (en) | 2009-05-27 | 2009-05-27 | Multi-blade fan |
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WO2010137140A1 true WO2010137140A1 (en) | 2010-12-02 |
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PCT/JP2009/059710 WO2010137140A1 (en) | 2009-05-27 | 2009-05-27 | Multi-blade fan |
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US (1) | US20120009059A1 (en) |
JP (1) | JP5230805B2 (en) |
KR (1) | KR20110113660A (en) |
CN (1) | CN102317633B (en) |
TW (1) | TWI388730B (en) |
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WO2016133014A1 (en) * | 2015-02-19 | 2016-08-25 | 株式会社日本自動車部品総合研究所 | Centrifugal blower |
WO2016170580A1 (en) * | 2015-04-20 | 2016-10-27 | 三菱電機株式会社 | Centrifugal blower |
JPWO2019082949A1 (en) * | 2017-10-27 | 2020-11-12 | 三菱電機株式会社 | Centrifugal blower, blower, air conditioner and refrigeration cycle device |
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DE102012221916A1 (en) * | 2012-11-29 | 2014-06-05 | BSH Bosch und Siemens Hausgeräte GmbH | Housing for a radial fan and radial fan |
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- 2009-05-27 WO PCT/JP2009/059710 patent/WO2010137140A1/en active Application Filing
- 2009-05-27 CN CN200980156448.XA patent/CN102317633B/en not_active Expired - Fee Related
- 2009-05-27 US US13/201,006 patent/US20120009059A1/en not_active Abandoned
- 2009-05-27 KR KR1020117020925A patent/KR20110113660A/en active IP Right Grant
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WO2016133014A1 (en) * | 2015-02-19 | 2016-08-25 | 株式会社日本自動車部品総合研究所 | Centrifugal blower |
JPWO2016133014A1 (en) * | 2015-02-19 | 2017-07-20 | 株式会社Soken | Centrifugal blower |
WO2016170580A1 (en) * | 2015-04-20 | 2016-10-27 | 三菱電機株式会社 | Centrifugal blower |
JPWO2019082949A1 (en) * | 2017-10-27 | 2020-11-12 | 三菱電機株式会社 | Centrifugal blower, blower, air conditioner and refrigeration cycle device |
TWI731570B (en) * | 2017-10-27 | 2021-06-21 | 日商三菱電機股份有限公司 | Centrifugal blower, blower, air conditioner and refrigeration cycle device |
US11566635B2 (en) | 2017-10-27 | 2023-01-31 | Mitsubishi Electric Corporation | Centrifugal blower, air-blowing apparatus, air-conditioning apparatus, and refrigeration cycle apparatus |
US12044250B2 (en) | 2017-10-27 | 2024-07-23 | Mitsubishi Electric Corporation | Centrifugal blower, air-blowing apparatus, air-conditioning apparatus, and refrigeration cycle apparatus |
Also Published As
Publication number | Publication date |
---|---|
KR20110113660A (en) | 2011-10-17 |
US20120009059A1 (en) | 2012-01-12 |
CN102317633B (en) | 2014-03-05 |
TWI388730B (en) | 2013-03-11 |
CN102317633A (en) | 2012-01-11 |
JPWO2010137140A1 (en) | 2012-11-12 |
JP5230805B2 (en) | 2013-07-10 |
TW201042154A (en) | 2010-12-01 |
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