US20120009059A1 - Multiblade fan - Google Patents

Multiblade fan Download PDF

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Publication number
US20120009059A1
US20120009059A1 US13/201,006 US200913201006A US2012009059A1 US 20120009059 A1 US20120009059 A1 US 20120009059A1 US 200913201006 A US200913201006 A US 200913201006A US 2012009059 A1 US2012009059 A1 US 2012009059A1
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US
United States
Prior art keywords
impeller
inlet
casing
rotation axis
blades
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.)
Abandoned
Application number
US13/201,006
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English (en)
Inventor
Kazuki Okamoto
Kenichi Sakoda
Hitoshi Kikuchi
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KIKUCHI, HITOSHI, OKAMOTO, KAZUKI, SAKODA, KENICHI
Publication of US20120009059A1 publication Critical patent/US20120009059A1/en
Abandoned 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/40—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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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 capable of improving noise characteristics or blowing performance.
  • a typical multiblade fan includes a scroll type casing having a bell-mouthed inlet and an impeller housed in the casing.
  • the impeller is a multiblade impeller (sirocco fan) that includes a plurality of annularly arranged blades and that is housed in the casing with a rotation axis of the impeller oriented toward the inlet of the casing.
  • the multiblade fan When the multiblade fan is constructed in this manner, air is incident on a blade at an acute (sharp) incident angle when the air flows into the impeller to pass through between the blades. Because this causes the impeller to function insufficiently, it is possible that the multiblade fan provides its blowing performance insufficiently.
  • Another conventional multiblade fan has adopted a configuration of causing a space between an impeller and a bell-mouthed inlet to vary in a rotation direction (see Patent Document 3).
  • This configuration makes velocity distribution of air inside the impeller uniform, thereby improving performance of the blower.
  • these configurations are disadvantageous in that because the shape of a casing is complicated or it is difficult to release the casing from a die, cost of production increases.
  • the multiblade fan uses a scroll type casing that is expanded by a predetermined degree to recover a static pressure. Accordingly, when a position where air is sucked is changed, velocity of airflow inside the impeller is changed, thereby changing the deflection of the airflow that is deflected toward the main plate. Hence, changing the shape of the blades of the impeller is disadvantageous in being insufficiently effective. This is because the changing the shape of the blades is effective for a target airflow; however, there are produced losses in air flows other than the target airflow. It is also necessary to determine the shape of the blades while taking its influences over an all-around rotation of the impeller into consideration.
  • a multiblade fan includes a scroll type casing that includes a bell-mouthed inlet and an impeller that includes a plurality of annularly arranged blades and a rotation axis oriented toward the inlet and that is housed in the casing.
  • a center axis of the inlet and the rotation axis of the impeller are arranged to make a tilt angle and in either one of a mutually intersecting positional relationship and a mutually skewed positional relationship, so that a space between the inlet and the impeller is increased from the rotation axis of the impeller toward an outlet of the casing.
  • a space between an inlet and an impeller increases from a rotation axis of the impeller toward an outlet of a casing.
  • This configuration permits air that has flown into the impeller through the inlet to flow in a gentle curve inside the impeller to pass through between blades.
  • This causes velocity distribution (deflection of airflow) of intake air inside the impeller and an incident angle of the intake air on a blade to relatively change, thereby making the velocity distribution of air having passed through between the blades uniform in the axial direction of the rotation axis of the impeller.
  • FIG. 1 is a schematic cross-sectional plan view depicting a multiblade fan according to an embodiment of the present invention.
  • FIG. 2 is a schematic cross-sectional view taken along line A-A of the multiblade fan depicted in FIG. 1 .
  • FIG. 3 is a schematic explanatory diagram illustrating how the multiblade fan depicted in FIG. 1 works.
  • FIG. 4 is a schematic explanatory diagram illustrating how the multiblade fan depicted in FIG. 1 works.
  • FIG. 5 is a graph illustrating noise characteristics for different spaces between an inlet and an impeller.
  • FIG. 6 is a graph illustrating results of performance tests of multiblade fans.
  • FIG. 7 is a graph illustrating results of performance tests of multiblade fans.
  • FIG. 8 is a schematic explanatory diagram of the configuration of the multiblade fan depicted in FIG. 1 .
  • FIG. 9 is a schematic explanatory diagram of a modification of the multiblade fan depicted in FIG. 1 .
  • FIG. 10 is a schematic explanatory diagram of another modification of the multiblade fan depicted in FIG. 1 .
  • FIG. 11 is a schematic configuration diagram of a conventional multiblade fan.
  • FIG. 12 is a schematic explanatory diagram illustrating how the multiblade fan depicted in FIG. 11 works.
  • a multiblade fan 1 is a blower that includes a multibladed wheel (sirocco fan).
  • the multiblade fan 1 is applied to, for example, an air conditioning system, a duct fan, and a ventilating fan.
  • the multiblade fan 1 can be of a single inlet type or a double inlet type. In the present embodiment, the multiblade fan 1 of a single inlet type will be described as an example.
  • the multiblade fan 1 includes a casing 2 , an impeller 3 , and a drive motor 4 (see FIG. 1 and FIG. 2 ).
  • the casing 2 is, for example, a scroll type casing.
  • the casing 2 includes a main body 21 , an inlet 22 , and an outlet 23 .
  • the main body 21 assumes a scroll-like shape in plan view.
  • the inlet 22 is a bell-mouthed inlet defined in a side surface (axially upper surface of the scroll-like shape) of the main body 21 , at a center of the scroll-like shape.
  • the outlet 23 is defined in a circumferential surface (coiled surface of the scroll-like shape) of the main body 21 .
  • the casing 2 is made of, for example, resin and formed by die molding.
  • the impeller 3 is a multibladed wheel (sirocco fan) that includes a plurality of blades 31 that are annularly arranged.
  • the impeller 3 includes a rotary shaft m that is oriented toward the inlet 22 of the casing 2 and a circumferential surface that is oriented along the circumference of the casing 2 .
  • the impeller 3 is constructed by annularly arranging the blades 31 along the rim of a substantially disc-shaped main plate 32 at predetermined intervals and fixing the blades 31 to the main plate 32 . In this manner, a bladed wheel made of the blades 31 is formed on the main plate 32 .
  • An annular member 33 serving as reinforcement is fit in end portions (end portions on the side opposite from the main plate 32 ) of the blades 31 .
  • the impeller 3 is housed in the casing 2 with the end portions of the blades 31 oriented toward the inlet 22 and with a circumferential surface of the bladed wheel oriented along the circumference of the casing 2 .
  • the drive motor 4 is a motor that drives the impeller 3 to rotate.
  • the drive motor 4 is inserted into the casing 2 through the bottom surface of the casing 2 to be coupled to the main plate 32 of the impeller 3 .
  • On/off control of the drive motor 4 is performed by using, for example, an external switch.
  • This configuration also causes (2) air to be incident on a blade at an acute (sharp) incident angle ⁇ when the air flows into the impeller to pass through between blades (see FIG. 12 ). Because this causes the impeller to function insufficiently, it is possible that the multiblade fan fails to provide its blowing performance sufficiently.
  • the center axis l of the inlet 22 of the casing 2 and the rotation axis m of the impeller 3 are arranged in (a) an intersecting positional relationship where they intersect with each other at a tilt angle ⁇ or in (b) a skew-lines positional relationship where they are skewed relative to each other (see FIG. 2 ).
  • the positional relationship between the inlet 22 and the impeller 3 are set such that the center axis l of the inlet 22 and the rotation axis m of the impeller 3 are not coaxial with each other (not on a single axis).
  • the center axis l of the inlet 22 is a center axis of the bell-mouthed inlet of the inlet 22 .
  • a space L between the inlet 22 and the blades 31 of the impeller 3 increases toward the outlet 23 of the casing 2 due to the positional relationship between the inlet 22 and the impeller 3 (see FIG. 1 and FIG. 2 ).
  • the space L between an opening surface of the inlet 22 and an end (an end of one of the blades 31 near the inlet 22 ) of the one of the blades 31 of the impeller 3 increases from the rotation axis m of the impeller 3 toward the outlet 23 of the casing 2 .
  • the space L can be arbitrarily set according to specifications for the multiblade fan 1 or the like.
  • This configuration also causes air to flow into the blades 31 at a less acute incident angle ⁇ inside the impeller 3 (see FIG. 4 ). Accordingly, the velocity distribution of air that passes through between the blades 31 , 31 is more uniform as compared with that of the configuration in which air flows into the blades at the acute (sharp) angle ⁇ (see FIG. 12 ). Hence, the impeller 3 can provide its function sufficiently, thereby improving blowing performance of the multiblade fan 1 .
  • an opening area of an air passage in the main body 21 is maximized near the outlet 23 (see FIG. 1 ).
  • This causes air near the outlet 23 to flow at a relatively high airflow rate, thereby increasing an airflow rate of air that passes through between the blades 31 of the impeller 3 , which increases the magnitude of the inertia force.
  • the velocity distribution of the air that passes through between the blades 31 , 31 is further deflected toward the main plate.
  • the velocity distribution of intake air inside the impeller 3 and the incident angle ⁇ on one of the blades 31 are changed by a large extent. This makes the velocity distribution, which can otherwise be largely deflected toward the main plate, of the air passing through between the blades 31 , 31 effectively uniform. Accordingly, noise characteristics are efficiently improved.
  • an arc angle ⁇ [°] that indicates a rotation angle of the impeller 3 about the rotation axis m of the impeller 3 relative to a reference direction, which is parallel to the axial direction of the outlet 23 of the casing 2 in plan view of the impeller 3 , can be defined (see FIG. 1 ).
  • the arc angle ⁇ can be set so that favorable noise characteristics are obtained with the configuration depicted in FIG.
  • FIG. 5 depicts a relationship between the arc angle ⁇ and the noise characteristics.
  • the noise characteristics are given as a difference in noise level relative to a reference noise level (0 [dB]), which is a noise level of the conventional example.
  • This position corresponds to the position near the outlet 23 of the casing 2 . Accordingly, it is revealed that by setting the space L between the inlet 22 and the impeller 3 to be maximized near the outlet 23 of the casing 2 , the noise characteristics of the multiblade fan 1 are efficiently improved.
  • FIG. 6 and FIG. 7 are graphs illustrating results of performance tests of the multiblade fans. Performance tests for (1) blowing performance (performance measured by static pressure) and (2) noise characteristics have been performed on the present embodiment.
  • the multiblade fan 1 of the present embodiment is improved in blowing performance and noise characteristics as compared with the multiblade fan of the conventional example.
  • the multiblade fan 1 of the present embodiment is increased in static pressure by approximately 10 [Pa] and decreased in noise level by approximately 1 [dB] under the same airflow rate.
  • this multiblade fan 1 is constructed such that (1) the space L between the inlet 22 and the impeller 3 increases from the rotation axis m of the impeller 3 toward the outlet 23 of the casing 2 (see FIG. 1 and FIG. 2 ). This configuration permits air that has flown into the impeller 3 through the inlet 22 to flow in a gentle curve inside the impeller 3 to pass through between the blades 31 , 31 (see FIG. 3 ).
  • the space L between the inlet 22 and the impeller 3 is adjusted because (2) the center axis l of the inlet 22 and the rotation axis m of the impeller 3 are arranged at the tilt angle ⁇ to each other and in any one of the intersecting positional relationship and the skew-lines positional relationship. Put another way, the space L is adjusted by adjusting the positional relationship between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 .
  • This space L causes the velocity distribution of intake air inside the impeller 3 and the incident angle ⁇ on one of the blades 31 to be relatively changed, making the velocity distribution of air passing through between the blades 31 , 31 uniform.
  • the multiblade fan 1 can employ any one of the following configurations (see FIG. 8 to FIG. 10 ) to adjust the positional relationship between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 (they are arranged at the tilt angle ⁇ to each other and in any one of the intersecting positional relationship and the positional relationship).
  • FIG. 8 depicts a configuration in which both the center axis l of the inlet 22 and the rotation axis m of the impeller 3 are tilted relative to the main body 21 , thereby adjusting the positional relationship (tilt angle ⁇ ) between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 .
  • This configuration is advantageous in that the tilt angle ⁇ can be attained more easily in terms of design as compared with a configuration in which only any one of the center axis l of the inlet 22 and the rotation axis m of the impeller 3 are tilted relative to the main body 21 .
  • a mating portion of an outer periphery of the bell-mouthed inlet of the inlet 22 and a wall surface of the main body 21 includes a stepped portion so that the bell-mouthed inlet of the inlet 22 is tilted relative to the wall surface of the main body 21 (see FIG. 2 ).
  • the drive motor 4 is attached to the main body 21 such that the rotation axis of the drive motor 4 is tilted relative to the wall surface of the main body 21 .
  • the impeller 3 is attached to the drive motor 4 .
  • both the center axis l of the inlet 22 and the rotation axis m of the impeller 3 are tilted relative to the main body 21 .
  • the configuration is not limited thereto.
  • the positional relationship between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 can be adjusted by arranging only any one of the center axis l of the inlet 22 and the rotation axis m of the impeller 3 to be tilted relative to the main body 21 (see FIG. 9 and FIG. 10 ).
  • FIG. 9 depicts a configuration in which only the center axis l of the inlet 22 is tilted relative to the main body 21 .
  • a component that is formed by simple die molding can be used to form the inlet 22 of the main body 21 . Accordingly, this configuration is advantageous in that the positional relationship between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 can be adjusted in a simple and less expensive manner.
  • FIG. 10 depicts another exemplary configuration in which only the rotation axis m of the impeller 3 (the rotation axis of the drive motor 4 ) is tilted relative to the main body 21 .
  • This configuration is advantageous in that the positional relationship between the center axis l of the inlet 22 and the rotation axis m of the impeller 3 can be adjusted in a simple and less expensive manner without changing an outer dimension of the main body 21 .
  • a multiblade fan according to the present invention is useful in enabling an improvement in noise characteristics or blowing performance.
  • 1 multiblade fan 2 casing, 21 main body, 22 inlet, 23 outlet, 3 impeller, 31 blade, 32 main plate, 33 annular member, 4 drive motor

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US13/201,006 2009-05-27 2009-05-27 Multiblade fan Abandoned US20120009059A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/059710 WO2010137140A1 (ja) 2009-05-27 2009-05-27 多翼送風機

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US20120009059A1 true US20120009059A1 (en) 2012-01-12

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US13/201,006 Abandoned US20120009059A1 (en) 2009-05-27 2009-05-27 Multiblade fan

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US (1) US20120009059A1 (ja)
JP (1) JP5230805B2 (ja)
KR (1) KR20110113660A (ja)
CN (1) CN102317633B (ja)
TW (1) TWI388730B (ja)
WO (1) WO2010137140A1 (ja)

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EP2738394A1 (de) * 2012-11-29 2014-06-04 BSH Bosch und Siemens Hausgeräte GmbH Gehäuse für ein Radialgebläse und Radialgebläse
US20160369819A1 (en) * 2014-07-31 2016-12-22 Gentherm Incorporated Air mover inlet interface and cover
US20180156222A1 (en) * 2016-12-05 2018-06-07 Asia Vital Components Co., Ltd. Series fan inclination structure
US20190353183A1 (en) * 2016-12-20 2019-11-21 Mitsubishi Electric Corporation Multiblade fan
USD938571S1 (en) * 2019-02-04 2021-12-14 Mitsubishi Electric Corporation Casing for blower
USD938570S1 (en) * 2019-02-04 2021-12-14 Mitsubishi Electric Corporation Casing for blower
USD944966S1 (en) * 2019-02-04 2022-03-01 Mitsubishi Electric Corporation Casing for blower
USD963153S1 (en) * 2020-07-31 2022-09-06 Mitsubishi Electric Corporation Casing for blower
US11486645B2 (en) 2018-05-30 2022-11-01 Nidec Motor Corporation Mounting system for pressure switch providing both mechanical support and integrated pressure communication
US11566635B2 (en) 2017-10-27 2023-01-31 Mitsubishi Electric Corporation Centrifugal blower, air-blowing apparatus, air-conditioning apparatus, and refrigeration cycle apparatus

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JP6142285B2 (ja) * 2013-03-21 2017-06-07 パナソニックＩｐマネジメント株式会社 片吸込み型遠心送風機
JP6528112B2 (ja) * 2014-09-26 2019-06-12 パナソニックＩｐマネジメント株式会社 遠心送風機
JP6332546B2 (ja) * 2015-02-19 2018-05-30 株式会社Ｓｏｋｅｎ 遠心送風機
JP6486459B2 (ja) * 2015-04-20 2019-03-20 三菱電機株式会社 遠心送風機
DE102019210077A1 (de) * 2019-07-09 2021-01-14 Ziehl-Abegg Se Ventilator mit Spiralgehäuse und Spiralgehäuse für einen Ventilator
CN112228359A (zh) * 2020-09-29 2021-01-15 曹云标 一种涡轮压缩机
KR102621165B1 (ko) * 2021-11-08 2024-01-05 국방과학연구소 벨마우스

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US5352089A (en) * 1992-02-19 1994-10-04 Nippondenso Co., Ltd. Multi-blades fan device
US5842828A (en) * 1995-06-29 1998-12-01 Aisin Seiki Kabushiki Kaisha Liquid pump

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JP4302960B2 (ja) * 2002-10-23 2009-07-29 カルソニックカンセイ株式会社 遠心式の多翼送風機
CN1784547B (zh) * 2003-05-01 2011-07-20 大金工业株式会社 多叶片离心式送风机
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Publication number Priority date Publication date Assignee Title
US2773453A (en) * 1952-09-12 1956-12-11 Gemeinhardt William Rotary pumps
US5352089A (en) * 1992-02-19 1994-10-04 Nippondenso Co., Ltd. Multi-blades fan device
US5842828A (en) * 1995-06-29 1998-12-01 Aisin Seiki Kabushiki Kaisha Liquid pump

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2738394A1 (de) * 2012-11-29 2014-06-04 BSH Bosch und Siemens Hausgeräte GmbH Gehäuse für ein Radialgebläse und Radialgebläse
US20160369819A1 (en) * 2014-07-31 2016-12-22 Gentherm Incorporated Air mover inlet interface and cover
US20180156222A1 (en) * 2016-12-05 2018-06-07 Asia Vital Components Co., Ltd. Series fan inclination structure
US10184477B2 (en) * 2016-12-05 2019-01-22 Asia Vital Components Co., Ltd. Series fan inclination structure
US20190353183A1 (en) * 2016-12-20 2019-11-21 Mitsubishi Electric Corporation Multiblade fan
US10907655B2 (en) * 2016-12-20 2021-02-02 Mitsubishi Electric Corporation Multiblade fan
US20230400036A1 (en) * 2017-10-27 2023-12-14 Mitsubishi Electric Corporation Centrifugal blower, air-blowing apparatus, air-conditioning apparatus, and refrigeration cycle apparatus
US11566635B2 (en) 2017-10-27 2023-01-31 Mitsubishi Electric Corporation Centrifugal blower, air-blowing apparatus, air-conditioning apparatus, and refrigeration cycle apparatus
US11486645B2 (en) 2018-05-30 2022-11-01 Nidec Motor Corporation Mounting system for pressure switch providing both mechanical support and integrated pressure communication
USD938571S1 (en) * 2019-02-04 2021-12-14 Mitsubishi Electric Corporation Casing for blower
USD962418S1 (en) * 2019-02-04 2022-08-30 Mitsubishi Electric Corporation Casing for blower
USD961756S1 (en) * 2019-02-04 2022-08-23 Mitsubishi Electric Corporation Casing for blower
USD944966S1 (en) * 2019-02-04 2022-03-01 Mitsubishi Electric Corporation Casing for blower
USD938570S1 (en) * 2019-02-04 2021-12-14 Mitsubishi Electric Corporation Casing for blower
USD963153S1 (en) * 2020-07-31 2022-09-06 Mitsubishi Electric Corporation Casing for blower

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CN102317633B (zh) 2014-03-05
WO2010137140A1 (ja) 2010-12-02
CN102317633A (zh) 2012-01-11
TW201042154A (en) 2010-12-01
JP5230805B2 (ja) 2013-07-10
TWI388730B (zh) 2013-03-11
JPWO2010137140A1 (ja) 2012-11-12
KR20110113660A (ko) 2011-10-17

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