US20020004008A1 - Centrifugal fan - Google Patents
Centrifugal fan Download PDFInfo
- Publication number
- US20020004008A1 US20020004008A1 US09/897,284 US89728401A US2002004008A1 US 20020004008 A1 US20020004008 A1 US 20020004008A1 US 89728401 A US89728401 A US 89728401A US 2002004008 A1 US2002004008 A1 US 2002004008A1
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- US
- United States
- Prior art keywords
- air
- impeller
- fan
- centrifugal
- casing
- 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
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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
- F04D29/40—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
- F04D29/444—Bladed diffusers
Definitions
- the present invention relates to a centrifugal fan which sucks air in the axial direction of a rotary shaft and blows it out in the radial direction.
- This centrifugal fan is effectively applied to an air purifier for vehicle use or an air-conditioner recessed in a ceiling.
- a centrifugal fan which will be referred to as a fan in this specification hereinafter, which is described in Japanese Unexamined Utility Model Publication No. 61-29222, is composed as follows. Outside a centrifugal multi-blade impeller, which will be referred to as an impeller in this specification hereinafter, there are provided two air passages which are formed into a spiral. Due to the above structure, air streams can be simultaneously blown out from a plurality of outlets.
- the length of the air passage (the winding angle of the air passage) is shorter than that of a fan having one outlet. Therefore, the following problems may be encountered.
- the air stream in the fan is unstable, and turbulence tends to occur in the air stream. For the above reasons, noise tends to be generated, and further the total pressure of the fan can not be sufficiently increased.
- the present invention has been achieved to solve the above problems. It is an object of the present invention to decrease the occurrence of noise and increase the total pressure of a fan having a plurality of outlets.
- the present invention provides a centrifugal fan comprising: a centrifugal impeller ( 111 ) having a number of blades ( 112 ) around a rotary shaft, the centrifugal impeller ( 111 ) sucking air in the axial direction of the rotary shaft and blowing it out in the radial direction; a casing ( 113 ) for accommodating the centrifugal impeller ( 111 ), the casing ( 113 ) having a plurality of outlets ( 114 ) for blowing out air; and stator blades ( 115 ) arranged in the casing ( 113 ), extending from the outer diameter side of the centrifugal impeller ( 111 ) to the downstream side of an air current.
- stator blades ( 115 ) are arranged all over the circumference on the outer diameter side of the centrifugal impeller ( 111 ).
- centrifugal impeller ( 111 ) has blades ( 112 ) arranged backward, the impeller delivery angle ( ⁇ ) of which is larger than 90°.
- the entrance angle ( ⁇ ) of the stator blade ( 115 ) is not more than 20°.
- the cross-section of the stator blade ( 115 ) is an airfoil shape.
- FIG. 1 is a perspective view showing the inside of a passenger compartment of a vehicle into which an air purifier using a fan of an embodiment of the present invention is incorporated;
- FIG. 2 is a front view showing an air purifier in which a fan of an embodiment of the present invention is used;
- FIG. 3 is a front cross-sectional view of a fan of an embodiment of the present invention.
- FIG. 4 is a cross-sectional view taken on line A-A in FIG. 3;
- FIG. 5 is an enlarged view of an impeller and diffuser of a fan of an embodiment of the present invention
- FIG. 6 is a graph showing a relation between the total pressure ⁇ P and the volume of blown air and also showing a relation between the specific noise Ks and the volume of the blown air;
- FIG. 7 is a schematic illustration showing a model of a fan of the prior art.
- FIG. 8 is a schematic illustration showing a model of a fan in which diffusers have been removed.
- FIG. 1 is a perspective view of the inside of a passenger compartment of a vehicle showing a state in which the air purifier 100 is incorporated onto the rear package tray 200 of the vehicle.
- FIG. 2 is a front view showing an air purifier 100 for vehicle use.
- the air purifier 100 is set in motion or stopped by an output signal of a smoke sensor (not shown), which detects the degree of fouling of the air in the compartment, or by a manual switch operated by a driver.
- a smoke sensor not shown
- a manual switch operated by a driver When this purifier 100 is operating, air is introduced into the inlet 101 arranged at a substantial center of the air purifier 100 as shown in FIG. 1, and air, which has been cleaned, is blown out from the outlet 102 .
- FIG. 3 is a front cross-sectional view, which is taken on line B-B in FIG. 4, of the fan 110 of this embodiment.
- FIG. 4 is a cross-sectional view taken on line A-A in FIG. 3.
- Reference numeral 111 is a centrifugal impeller, which will be referred to as an impeller hereinafter, having a number of blades 112 around the rotary shaft 111 a , for blowing out air, which has been sucked in the axial direction of the rotary shaft 111 a , in the radial direction.
- an impeller (turbo-impeller) is adopted, the blades of which are arranged backward, the delivery angle ⁇ of each blade 112 of which is larger than 90°.
- the delivery angle ⁇ of each blade 112 is an angle formed between the blade 112 and the outer diameter edge L 1 of the impeller 111 as shown in FIG. 5. This delivery angle ⁇ is measured from the proceeding side of the rotary direction of the impeller 111 .
- the impeller 111 is accommodated in the casing 113 made of resin (polypropylene in this embodiment).
- the casing 113 made of resin (polypropylene in this embodiment).
- this casing 113 there are provided a plurality (two in this embodiment) of outlets 114 from which air is blown out.
- each outlet 114 formed in the casing 113 there is provided a filter 103 for cleaning air which has been blown out from the impeller 111 .
- the entrance angle ⁇ of the diffuser 115 is set at not more than 20°. In this figure, the entrance angle ⁇ of the diffuser 115 is set at 20°. In this connection, as shown in FIG.
- the entrance angle ⁇ of the diffuser 115 is defined as an angle of the inner diameter edge (the circular locus connecting the side end portions of the diffusers 115 of the impeller 111 ) L 2 of the diffuser 115 with the diffusers 115 , wherein the entrance angle ⁇ of the diffuser 115 is measured from the proceeding side of the rotary direction of the impeller 111 .
- reference numeral 116 is a suction port for introducing air, which has been introduced from the inlet 101 , into the casing 113 .
- a bell-mouth 117 for introducing air, which has been sucked from the suction port, onto the inner diameter side of the impeller 111 .
- This bell-mouth 117 is molded and integrated with the casing 113 .
- Reference numeral 118 is an electric motor (drive means) for driving the impeller 111 .
- this electric motor 118 is controlled by being turned on, the air purifier 100 is operated.
- diffusers 115 which extend from portions close to the outer diameter side of the impeller 111 to the downstream side of the air current. Accordingly, while a current of air, which has been blown out from the impeller 111 , is being straightened, its dynamic pressure is converted into static pressure.
- FIG. 6 is a graph showing the results of experiments on the total pressure ⁇ P and the specific noise Ks with respect to the conventional fan shown in FIG. 7 (having a scroll casing, the air passage length of which is small (the winding angle of the air passage of which is small)), also with respect to the fan in which the diffusers 115 are abolished from the fan of this embodiment shown in FIG. 8, and also with respect to the fan of this embodiment.
- the present invention it is possible to sufficiently increase the total pressure of the fan 110 and suppress the generation of noise.
- the entrance angle ⁇ of the diffuser 115 is set at a value not more than 20° from the viewpoint of practical use, it is possible to guide the air, which has been blown out from the impeller 111 , into the outlet 114 side while the dynamic pressure of the air is effectively converted into static pressure.
- an impeller (turbo-impeller), the blades of which are arranged backward, the delivery angle ⁇ of each blade 112 of which is larger than 90°, is adopted. Therefore, it is possible to increase the static pressure of the air itself which is blown out from the impeller 111 . Accordingly, the total pressure ⁇ P can be increased.
- the number of the outlets 114 of the fan 110 is two, however, it should be noted that the present invention is not limited to the above specific embodiment. It is possible to apply the present invention to a fan having not less than three outlets 114 .
- the fan of the present invention is applied to an air purifier for vehicle use, however, it should be noted that the present invention is not limited to the above specific embodiment.
- the fan of the present invention can be applied to an air-conditioner recessed in a ceiling or to another apparatus.
- the impeller is used, the blades of which are arranged backward and the impeller delivery angle ⁇ of which is not less than 90°.
- the impeller it possible to use an impeller, the blades of which are arranged forward and the impeller delivery angle ⁇ of which is not more than 90°.
- the diffusers 115 are arranged around the circumference on the outer diameter side of the impeller 111 , however, the diffusers 115 may be arranged only in a portion of the circumference on the outer diameter side of the impeller 111 .
- each diffuser 115 is plate-shaped and the thickness is constant.
- the cross section of each diffuser 115 may be an airfoil shape, the impeller 111 side of which is a side of the chord of blade, or a streamline shape.
Abstract
According to the present invention, there are provided diffusers 115 which extend from portions close to the outer diameter of the centrifugal impeller 111 to the downstream side of a current of air, on the outer diameter side of the centrifugal impeller 111 and around the circumference. Due to the foregoing, while a current of air blown out from the impeller 111 is being straightened by the diffusers 115, the dynamic pressure of the current of air is converted into static pressure. Consequently, it is possible to make the current of air flow stably into the outlet 114 side without disturbing it. Therefore, while the generation of noise is being suppressed, the total pressure of the fan 110 can be sufficiently increased.
Description
- 1. Field of the Invention
- The present invention relates to a centrifugal fan which sucks air in the axial direction of a rotary shaft and blows it out in the radial direction. This centrifugal fan is effectively applied to an air purifier for vehicle use or an air-conditioner recessed in a ceiling.
- 2. Description of the Related Art
- A centrifugal fan, which will be referred to as a fan in this specification hereinafter, which is described in Japanese Unexamined Utility Model Publication No. 61-29222, is composed as follows. Outside a centrifugal multi-blade impeller, which will be referred to as an impeller in this specification hereinafter, there are provided two air passages which are formed into a spiral. Due to the above structure, air streams can be simultaneously blown out from a plurality of outlets.
- However, in the case of the above fan having a plurality of outlets, the length of the air passage (the winding angle of the air passage) is shorter than that of a fan having one outlet. Therefore, the following problems may be encountered. The air stream in the fan is unstable, and turbulence tends to occur in the air stream. For the above reasons, noise tends to be generated, and further the total pressure of the fan can not be sufficiently increased.
- The present invention has been achieved to solve the above problems. It is an object of the present invention to decrease the occurrence of noise and increase the total pressure of a fan having a plurality of outlets.
- In order to accomplish the above object, the present invention provides a centrifugal fan comprising: a centrifugal impeller (111) having a number of blades (112) around a rotary shaft, the centrifugal impeller (111) sucking air in the axial direction of the rotary shaft and blowing it out in the radial direction; a casing (113) for accommodating the centrifugal impeller (111), the casing (113) having a plurality of outlets (114) for blowing out air; and stator blades (115) arranged in the casing (113), extending from the outer diameter side of the centrifugal impeller (111) to the downstream side of an air current.
- Due to the above structure, while a stream of air blown out from the centrifugal impeller (111) is being straightened by the stator blades (115), dynamic pressure of the stream of air is converted into static pressure. Accordingly, it is possible to make the stream of air flow stably onto the outlet (114) side without disturbing the stream of air. Therefore, it is possible to sufficiently increase the total pressure of the centrifugal fan and suppress the generation of noise.
- In this connection, it is preferable that the stator blades (115) are arranged all over the circumference on the outer diameter side of the centrifugal impeller (111).
- It is also preferable that the centrifugal impeller (111) has blades (112) arranged backward, the impeller delivery angle (β) of which is larger than 90°.
- It is also preferable that the entrance angle (α) of the stator blade (115) is not more than 20°.
- Further, it is preferable that the cross-section of the stator blade (115) is an airfoil shape.
- In this connection, reference numerals in parentheses in each means described above show the correspondence to the specific means described in the embodiments which will be stated later.
- The present invention may be more fully understood from the description of preferred embodiments of the invention set forth below, together with the accompanying drawings.
- In the drawings:
- FIG. 1 is a perspective view showing the inside of a passenger compartment of a vehicle into which an air purifier using a fan of an embodiment of the present invention is incorporated;
- FIG. 2 is a front view showing an air purifier in which a fan of an embodiment of the present invention is used;
- FIG. 3 is a front cross-sectional view of a fan of an embodiment of the present invention;
- FIG. 4 is a cross-sectional view taken on line A-A in FIG. 3;
- FIG. 5 is an enlarged view of an impeller and diffuser of a fan of an embodiment of the present invention;
- FIG. 6 is a graph showing a relation between the total pressure ΔP and the volume of blown air and also showing a relation between the specific noise Ks and the volume of the blown air;
- FIG. 7 is a schematic illustration showing a model of a fan of the prior art; and
- FIG. 8 is a schematic illustration showing a model of a fan in which diffusers have been removed.
- In this embodiment, a fan of the present invention is applied to an air purifier, for vehicle use, by which air in a passenger compartment of a vehicle is cleaned. FIG. 1 is a perspective view of the inside of a passenger compartment of a vehicle showing a state in which the
air purifier 100 is incorporated onto the rear package tray 200 of the vehicle. FIG. 2 is a front view showing anair purifier 100 for vehicle use. - In this embodiment, the
air purifier 100 is set in motion or stopped by an output signal of a smoke sensor (not shown), which detects the degree of fouling of the air in the compartment, or by a manual switch operated by a driver. When thispurifier 100 is operating, air is introduced into theinlet 101 arranged at a substantial center of theair purifier 100 as shown in FIG. 1, and air, which has been cleaned, is blown out from theoutlet 102. - Next, the
fan 110 of this embodiment will be explained below. - FIG. 3 is a front cross-sectional view, which is taken on line B-B in FIG. 4, of the
fan 110 of this embodiment. FIG. 4 is a cross-sectional view taken on line A-A in FIG. 3.Reference numeral 111 is a centrifugal impeller, which will be referred to as an impeller hereinafter, having a number ofblades 112 around therotary shaft 111 a, for blowing out air, which has been sucked in the axial direction of therotary shaft 111 a, in the radial direction. In this embodiment, an impeller (turbo-impeller) is adopted, the blades of which are arranged backward, the delivery angle β of eachblade 112 of which is larger than 90°. - In this connection, the delivery angle β of each
blade 112 is an angle formed between theblade 112 and the outer diameter edge L1 of theimpeller 111 as shown in FIG. 5. This delivery angle β is measured from the proceeding side of the rotary direction of theimpeller 111. - As shown in FIG. 3, the
impeller 111 is accommodated in thecasing 113 made of resin (polypropylene in this embodiment). In thiscasing 113, there are provided a plurality (two in this embodiment) ofoutlets 114 from which air is blown out. - In each
outlet 114 formed in thecasing 113, there is provided afilter 103 for cleaning air which has been blown out from theimpeller 111. - In the
casing 113, on the outer diameter side of theimpeller 111, there are provided stationary blades (diffusers) 115 extending from portions close to the outer diameter of theimpeller 111 toward the downstream side of the air current, wherein thesediffusers 115 are arranged around the circumference on the outer diameter side of theimpeller 111. In this embodiment, the entrance angle α of thediffuser 115 is set at not more than 20°. In this figure, the entrance angle α of thediffuser 115 is set at 20°. In this connection, as shown in FIG. 5, the entrance angle α of thediffuser 115 is defined as an angle of the inner diameter edge (the circular locus connecting the side end portions of thediffusers 115 of the impeller 111) L2 of thediffuser 115 with thediffusers 115, wherein the entrance angle α of thediffuser 115 is measured from the proceeding side of the rotary direction of theimpeller 111. - In this connection, reference numeral116 is a suction port for introducing air, which has been introduced from the
inlet 101, into thecasing 113. At the inner diameter edge of this suction port 116, there is provided a bell-mouth 117 for introducing air, which has been sucked from the suction port, onto the inner diameter side of theimpeller 111. This bell-mouth 117 is molded and integrated with thecasing 113. -
Reference numeral 118 is an electric motor (drive means) for driving theimpeller 111. When thiselectric motor 118 is controlled by being turned on, theair purifier 100 is operated. - Next, the characteristic of this embodiment will be described below.
- Immediately after air has been blown out from the
impeller 111 into thecasing 113, its flow velocity is greatly changed, and further the thus blown air collides with the side (the inner wall of thecasing 113 located on the outer diameter side of the impeller 111) of thecasing 113. Since a current of air on the upper face side (the suction port 116 side) of thecasing 113 and a current of air on the lower face side (theelectric motor 118 side) are reverse to each other, noise tends to be generated, and further it is impossible to sufficiently increase the total pressure of the fan. - On the other hand, in this embodiment, on the outer diameter side of the
impeller 111, there are provideddiffusers 115 which extend from portions close to the outer diameter side of theimpeller 111 to the downstream side of the air current. Accordingly, while a current of air, which has been blown out from theimpeller 111, is being straightened, its dynamic pressure is converted into static pressure. - Consequently, it is possible to make the current of air flow stably into the
outlet 114 side without disturbing it. Therefore, the generation of noise can be suppressed and the total pressure of thefan 110 can be sufficiently increased. - After the current of air has been straightened by the
diffusers 115 so that the distribution of air velocity can be made uniform, the current of air flows into thefilter 103. Therefore, it is possible to prevent the occurrence of a problem in which the clogging of the filter occurs in one portion of thefilter 103 compared with the other portion. Accordingly, the life of thefilter 103 can be extended. - In this connection, FIG. 6 is a graph showing the results of experiments on the total pressure ΔP and the specific noise Ks with respect to the conventional fan shown in FIG. 7 (having a scroll casing, the air passage length of which is small (the winding angle of the air passage of which is small)), also with respect to the fan in which the
diffusers 115 are abolished from the fan of this embodiment shown in FIG. 8, and also with respect to the fan of this embodiment. As can be seen from this graph, according to the present invention, it is possible to sufficiently increase the total pressure of thefan 110 and suppress the generation of noise. - In this connection, the definition of terminology of total pressure ΔP and specific noise Ks is based on JIS B 0132, and the above method of the experiment is based on JIS B 8340.
- In this connection, as shown in FIG. 6, the smaller the entrance angle α of the
diffuser 115 is made, the more the level of the specific noise Ks can be decreased (by about 2 dB). However, as can be seen in this embodiment, when the entrance angle α of thediffuser 115 is set at a value not more than 20° from the viewpoint of practical use, it is possible to guide the air, which has been blown out from theimpeller 111, into theoutlet 114 side while the dynamic pressure of the air is effectively converted into static pressure. - In this embodiment, an impeller (turbo-impeller), the blades of which are arranged backward, the delivery angle β of each
blade 112 of which is larger than 90°, is adopted. Therefore, it is possible to increase the static pressure of the air itself which is blown out from theimpeller 111. Accordingly, the total pressure ΔP can be increased. - Another embodiment will be explained below. In the embodiment described above, the number of the
outlets 114 of thefan 110 is two, however, it should be noted that the present invention is not limited to the above specific embodiment. It is possible to apply the present invention to a fan having not less than threeoutlets 114. - In the above embodiment, the fan of the present invention is applied to an air purifier for vehicle use, however, it should be noted that the present invention is not limited to the above specific embodiment. The fan of the present invention can be applied to an air-conditioner recessed in a ceiling or to another apparatus.
- In the above embodiment, the impeller is used, the blades of which are arranged backward and the impeller delivery angle β of which is not less than 90°. However, it possible to use an impeller, the blades of which are arranged forward and the impeller delivery angle β of which is not more than 90°.
- In the above embodiment, the
diffusers 115 are arranged around the circumference on the outer diameter side of theimpeller 111, however, thediffusers 115 may be arranged only in a portion of the circumference on the outer diameter side of theimpeller 111. - In the above embodiment, the each
diffuser 115 is plate-shaped and the thickness is constant. However, it should be noted that the present invention is not limited to the above specific embodiment. The cross section of eachdiffuser 115 may be an airfoil shape, theimpeller 111 side of which is a side of the chord of blade, or a streamline shape. - While the invention has been described by reference to specific embodiments chosen for purposes of illustration, it should be apparent that numerous modifications could be made thereto by those skilled in the art without departing from the basic concept and scope of the invention.
Claims (5)
1. A centrifugal fan comprising: a centrifugal impeller having a number of blades around a rotary shaft, the centrifugal impeller sucking air in the axial direction of the rotary shaft and blowing it out in the radial direction; a casing for accommodating the centrifugal impeller, the casing having a plurality of outlets for blowing out air; and stator blades arranged in the casing, extending from the outer diameter side of the centrifugal impeller to the downstream side of an air current.
2. A centrifugal fan according to claim 1 , wherein the stator blades are arranged around the circumference on the outer diameter side of the centrifugal impeller.
3. A centrifugal fan according to claim 1 , wherein the centrifugal impeller has blades arranged backward, the impeller outlet angle of which is larger than 90°.
4. A centrifugal fan according to claim 1 , wherein the entrance angle of the stator blade is not more than 20°.
5. A centrifugal fan according to claim 1 , wherein the cross-section of the stator blade is an airfoil shape.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000-205529 | 2000-07-06 | ||
JP2000205529A JP2002021790A (en) | 2000-07-06 | 2000-07-06 | Centrifugal type blower |
Publications (1)
Publication Number | Publication Date |
---|---|
US20020004008A1 true US20020004008A1 (en) | 2002-01-10 |
Family
ID=18702600
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/897,284 Abandoned US20020004008A1 (en) | 2000-07-06 | 2001-07-02 | Centrifugal fan |
Country Status (2)
Country | Link |
---|---|
US (1) | US20020004008A1 (en) |
JP (1) | JP2002021790A (en) |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080279681A1 (en) * | 2005-03-31 | 2008-11-13 | Mitsubishi Heavy Industries, Ltd. | Centrifugal Blower |
US20100247351A1 (en) * | 2009-03-31 | 2010-09-30 | Kleber Andreas | Axial flow fan, in particular for a motor vehicle |
US20100329857A1 (en) * | 2008-02-19 | 2010-12-30 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Compact Fan |
US20120121399A1 (en) * | 2009-07-31 | 2012-05-17 | Rem Enterprises Inc. | air vacuum pump for a particulate loader and transfer apparatus |
WO2015089752A1 (en) * | 2013-12-18 | 2015-06-25 | 赵兵 | Air purifier and fan thereof |
US20160152752A1 (en) * | 2013-08-12 | 2016-06-02 | Henkel IP & Holding GmbH | Alkoxysilane-functionalized polyacrylate compositions and method of preparation thereof |
EP3019718A4 (en) * | 2013-07-12 | 2017-03-08 | Volvo Truck Corporation | Heat exchanger system for a vehicle |
US20180023587A1 (en) * | 2016-07-19 | 2018-01-25 | Minebea Mitsumi Inc. | Centrifugal Fan |
US20190376523A1 (en) * | 2015-10-23 | 2019-12-12 | Minebea Mitsumi Inc. | Centrifugal fan |
CN111070996A (en) * | 2018-10-18 | 2020-04-28 | 电装国际美国公司 | Vehicle HVAC airflow system |
US10913324B2 (en) * | 2014-02-03 | 2021-02-09 | Denso Corporation | Blower |
US11719483B2 (en) * | 2020-04-09 | 2023-08-08 | Electrolux Home Products, Inc. | Ice maker for a refrigerator and method for synchronizing an implementation of an ice making cycle and an implementation of a defrost cycle of an evaporator in a refrigerator |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4185654B2 (en) * | 2000-08-04 | 2008-11-26 | カルソニックカンセイ株式会社 | Centrifugal multi-blade blower |
JP5304879B2 (en) * | 2011-12-27 | 2013-10-02 | ダイキン工業株式会社 | Air conditioner |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4371310A (en) * | 1974-07-23 | 1983-02-01 | The United States Of America As Represented By The Secretary Of The Navy | Centrifugal pump recirculation diffuser |
US4798518A (en) * | 1982-03-09 | 1989-01-17 | Wilhelm Gebhardt Gmbh | Fan unit for use with duct systems |
US5803721A (en) * | 1996-10-29 | 1998-09-08 | Enviroflex, Inc. | Clean room fan unit |
US6203275B1 (en) * | 1996-03-06 | 2001-03-20 | Hitachi, Ltd | Centrifugal compressor and diffuser for centrifugal compressor |
-
2000
- 2000-07-06 JP JP2000205529A patent/JP2002021790A/en not_active Withdrawn
-
2001
- 2001-07-02 US US09/897,284 patent/US20020004008A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4371310A (en) * | 1974-07-23 | 1983-02-01 | The United States Of America As Represented By The Secretary Of The Navy | Centrifugal pump recirculation diffuser |
US4798518A (en) * | 1982-03-09 | 1989-01-17 | Wilhelm Gebhardt Gmbh | Fan unit for use with duct systems |
US6203275B1 (en) * | 1996-03-06 | 2001-03-20 | Hitachi, Ltd | Centrifugal compressor and diffuser for centrifugal compressor |
US5803721A (en) * | 1996-10-29 | 1998-09-08 | Enviroflex, Inc. | Clean room fan unit |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080279681A1 (en) * | 2005-03-31 | 2008-11-13 | Mitsubishi Heavy Industries, Ltd. | Centrifugal Blower |
US7883312B2 (en) * | 2005-03-31 | 2011-02-08 | Mitsubishi Heavy Industries, Ltd. | Centrifugal blower |
US20100329857A1 (en) * | 2008-02-19 | 2010-12-30 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Compact Fan |
US8992175B2 (en) * | 2008-02-19 | 2015-03-31 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Compact fan |
US20100247351A1 (en) * | 2009-03-31 | 2010-09-30 | Kleber Andreas | Axial flow fan, in particular for a motor vehicle |
US8459967B2 (en) * | 2009-03-31 | 2013-06-11 | Behr Gmbh & Co. Kg | Axial flow fan, in particular for a motor vehicle |
US20120121399A1 (en) * | 2009-07-31 | 2012-05-17 | Rem Enterprises Inc. | air vacuum pump for a particulate loader and transfer apparatus |
US10072557B2 (en) | 2013-07-12 | 2018-09-11 | Volvo Truck Corporation | Heat exchanger system for a vehicle |
EP3019718A4 (en) * | 2013-07-12 | 2017-03-08 | Volvo Truck Corporation | Heat exchanger system for a vehicle |
AU2013393876B2 (en) * | 2013-07-12 | 2017-12-14 | Volvo Truck Corporation | Heat exchanger system for a vehicle |
US20160152752A1 (en) * | 2013-08-12 | 2016-06-02 | Henkel IP & Holding GmbH | Alkoxysilane-functionalized polyacrylate compositions and method of preparation thereof |
WO2015089752A1 (en) * | 2013-12-18 | 2015-06-25 | 赵兵 | Air purifier and fan thereof |
US10913324B2 (en) * | 2014-02-03 | 2021-02-09 | Denso Corporation | Blower |
US20190376523A1 (en) * | 2015-10-23 | 2019-12-12 | Minebea Mitsumi Inc. | Centrifugal fan |
US20180023587A1 (en) * | 2016-07-19 | 2018-01-25 | Minebea Mitsumi Inc. | Centrifugal Fan |
CN111070996A (en) * | 2018-10-18 | 2020-04-28 | 电装国际美国公司 | Vehicle HVAC airflow system |
US11719483B2 (en) * | 2020-04-09 | 2023-08-08 | Electrolux Home Products, Inc. | Ice maker for a refrigerator and method for synchronizing an implementation of an ice making cycle and an implementation of a defrost cycle of an evaporator in a refrigerator |
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