EP2503157A1 - Lüfter mit mehreren blättern für ein zentrifugalgebläse - Google Patents

Lüfter mit mehreren blättern für ein zentrifugalgebläse Download PDF

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Publication number
EP2503157A1
EP2503157A1 EP10831457A EP10831457A EP2503157A1 EP 2503157 A1 EP2503157 A1 EP 2503157A1 EP 10831457 A EP10831457 A EP 10831457A EP 10831457 A EP10831457 A EP 10831457A EP 2503157 A1 EP2503157 A1 EP 2503157A1
Authority
EP
European Patent Office
Prior art keywords
blade
blades
angle
fan
circle
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.)
Withdrawn
Application number
EP10831457A
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English (en)
French (fr)
Inventor
Masatoshi Kawasaki
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP2503157A1 publication Critical patent/EP2503157A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • 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
    • F04D29/422—Discharge tongues
    • 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
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a multi-blade fan, which has a plurality of annularly-disposed blades, for centrifugal blowers, and specifically relates to a technology to enable to design the multi-blade fan optimally as achieving high fan efficiency and low noise generation.
  • a centrifugal blower having a large number of blades disposed annularly is suitably used as a blower in an automotive air conditioning system. Such a centrifugal blower is desired to achieve low noise generation, as well as high fan efficiency.
  • an object of the present invention is to find out what kind of design factors (parameters) would work particularly for eliminating noise generation and then optimum ranges of the factors which are found would be combined to enable the design of a reasonably optimum multi-blade fan of centrifugal blowers.
  • a multi-blade fan for a centrifugal blower is a multi-blade fan for a centrifugal blower having a plurality of annularly-disposed blades, characterized in that at least, number of blades Z, an inner/outer diameter ratio defined as a ratio D1/D2 of a diameter D1 of an inscribed circle of the blades to a diameter D2 of a circumscribed circle of the blades, an angle of inclination ⁇ (deg) of each blade defined as an angle between a line which connects a position of the blade on the inscribed circle to a position thereof on the circumscribed circle, and a line extending radially from a center of the inscribed circle and passing through the position on the inscribed circle, and a tongue clearance ratio defined as a ratio S/D2 between the tongue clearance S and the diameter D2 of the circumscribed circle are all within following ranges.
  • the number of blades is preferably within 33 ⁇ Z ⁇ 50, and is more preferably within 35 ⁇ Z ⁇ 45.
  • the inner/outer diameter ratio D1/D2 is preferably within 0.76 ⁇ D1/D2 ⁇ 0.85, and is more preferably within 0.8 ⁇ D1/D2 ⁇ 0.84.
  • the angle of inclination ⁇ (deg) of the blade is preferably within 20 ⁇ ⁇ ⁇ 42, and is more preferably within 25 ⁇ ⁇ ⁇ 35.
  • the number of blades Z, the inner/outer diameter ratio D1/D2, the angle of inclination ⁇ of the blade, and the tongue clearance ratio S/D2 are set within the above-described ranges, so that the flow rate of the airflow between the blades can be controlled within the optimum range and the shear flow fluctuation of the airflow can be suppressed, and therefore the noise generation can be reduced actually.
  • desirable low noise generation can be achieved as maintaining high fan efficiency, and therefore the optimum design of the multi-blade fan is enabled.
  • an exit angle ⁇ 2 (deg) of the blade which is defined as an angle between a tangent line of the circumscribed circle and a tangent line of the blade at a position of each blade on the circumscribed circle, is within 148 ⁇ ⁇ 2 ⁇ 175. It is more preferably within 152 ⁇ ⁇ 2 ⁇ 170, and is further preferably within 155 ⁇ ⁇ 2 ⁇ 165.
  • the exit angle ⁇ 2 of the blade is optimized, the flow rate of the airflow between the blades can be surely controlled within the optimum range and the shear flow fluctuation of the airflow can be suppressed, and therefore the noise generation can be reduced more surely.
  • an entrance angle ⁇ 1 (deg) of the blade which is defined as an angle between a tangent line of the inscribed circle and a tangent line of the blade at a position of each blade on the inscribed circle, is within a range of 50 ⁇ 1 ⁇ 90. It is more preferably within 55 ⁇ ⁇ 1 ⁇ 85, and is further preferably within 60 ⁇ ⁇ 1 ⁇ 80.
  • a condition of the airflow flowed between blades can be more surely controlled optimally, so as to achieve desirable low noise generation surely.
  • a thickness of each blade is within a range of 0.6 - I mm, though the multi-blade fan for a centrifugal blower according to the present invention is not limited thereto.
  • the structure of the multi-blade fan for a centrifugal blower according to the present invention is basically applicable to every multi-blade fan, and is suitable to be applied to a blower of an automotive air conditioning system, which is required to have a small size, a low noise and a high efficiency.
  • the multi-blade fan for a centrifugal blower makes it possible that a multi-blade fan is designed optimally, that the high fan efficiency is maintained and that desirable low noise generation is achieved, because the number of blades Z, an inner/outer diameter ratio D1/D2, an angle of inclination ⁇ (deg) of the blade and a tongue clearance ratio S/D2 are all set within predetermined ranges, and preferably, an exit angle ⁇ 2 and an entrance angle ⁇ 1 of the blade as well as a thickness of each blade may be set within predetermined ranges.
  • FIG. 1 shows a multi-blade fan of a centrifugal blower according to an embodiment of the present invention, where (A) is a schematic front view showing blades and (B) is a schematic front view showing a casing which houses blades.
  • Multi-blade fan 1 comprises a plurality of (many) blades 2 disposed annularly, and is housed in casing 11.
  • symbol D1 shows a diameter of inscribed circle 3 many blades 2
  • symbol D2 shows a diameter of circumscribed circle 4 of many blades 2.
  • symbol S shows a clearance between circumscribed circle 4 of tongue 12 and casing 11.
  • the Inner/Outer Diameter Ratio is defined as D1/D2, which is a ratio of diameter D1 (mm) of inscribed circle 3 to diameter D2 (mm) of circumscribed circle 4 of blades 2.
  • Angle of Inclination ⁇ (deg) of the blade is defined as an angle between line 5, which is drawn from one end of each blade 2 at inscribed circle 3 side to the other end at circumscribed circle 4 side, and line 6, which is drawn radially from the other end at inscribed circle 3 side as extending to the center of the inscribed circle.
  • Exit Angle ⁇ 2 (deg) of blade 2 is defined as an angle between tangent line 7 of circumscribed circle 4 and tangent line 8 of blade 2, at circumscribed circle 4 side of each blade 2.
  • Entrance Angle ⁇ 1 (deg) of blade 2 is defined as an angle between tangent line 9 of inscribed circle 3 and tangent line 10 of blade 2, at inscribed circle 3 side of each blade 2. As described above, it is preferable that the thickness of blade 2 is set within 0.6-1mm though the thickness of each blade 2 is not limited thereto.
  • Number of Blades Z of blades 2 is set within an appropriate range of 30-55 concerning Specific Noise. It is more preferable to set it within 33 ⁇ Z ⁇ 50, and is further preferable to set it within 35 ⁇ Z ⁇ 45.
  • Number of Blades Z of blade 2 is less than the above-described appropriate range, the airflow between blades cannot reattach, so that the shear flow is greatly fluctuated as increasing noises as shown in Fig. 4(A) .
  • Number of Blades Z of blade 2 is more than the above-described appropriate range, the narrow gap makes the outflow higher so as to generate high noise even though the airflow between blades can reattach as shown in Fig. 4(C) .
  • Inner/Outer Diameter Ratio which is defined by D1/D2, is set within the appropriate range of 0.72-0.86 as shown in Fig. 5 . It is more preferable to set it within the range of 0.76 ⁇ D1/D2 ⁇ 0.85, and is further preferable to set it within the range of 0.8 ⁇ D1/D2 ⁇ 0.84. Further, the Inner/Outer Diameter Ratio D1/D2 is set within the above-described appropriate range of 0.72-0.86 as considering the fan efficiency.
  • Inner/Outer Diameter Ratio D1/D2 When Inner/Outer Diameter Ratio D1/D2 is set within the above-described appropriate range, the airflow between blades can reattach, so that appropriate suppression of flow rate between blades makes it possible to achieve the low noise generation as shown in Fig. 6(B) . In addition, the fan efficiency becomes within a desirable range. Those phenomena are shown in Table 2.
  • Angle of Inclination ⁇ (deg) of the blade is set within the appropriate range of 15-48 deg, where the ⁇ is defined as an angle between a line, which is drawn from one end of each blade at the inscribed circle side to the other end at the circumscribed circle side, and another line, which is drawn radially from the other end at the inscribed circle side. It is more preferable to set it within the range of 20 ⁇ ⁇ ⁇ 42, and is further preferable to set it within the range of 25 ⁇ ⁇ ⁇ 35.
  • Tongue Clearance Ratio defined as a ratio S/D2, where S is a clearance between circumscribed circle 4 of tongue 12 and casing 11 and where D2 is a diameter of circumscribed circle 4, is set within the appropriate range of 0.09-0.15.
  • Tongue Clearance Ratio is smaller than the above-described appropriate range, dissonant NZ-Noise, which is generated when the outflow from the blade interferes at the tongue, significantly increases.
  • Tongue Clearance is greater than the above-described appropriate range, the size of the casing outline becomes excessive like casing 11a shown in Fig. 10 .
  • Tongue Clearance is set within the above-described appropriate range, a casing with an appropriate size can suppress the NZ-Noise generation, so as to achieve a low noise condition.
  • parameters such as Number of Blades Z, Inner/Outer Diameter Ratio D1/D2, Angle of Inclination ⁇ (deg) of the blade and Tongue Clearance Ratio S/D2, are set within the above-described appropriate range, so that the low noise is surely achieved with a casing having an appropriate size, as maintaining the high fan efficiency.
  • Exit Angle ⁇ 2 (deg) of the blade is preferably set within the range of 148 ⁇ ⁇ 2 ⁇ 175, and is more preferably set within the range of 152 ⁇ ⁇ 2 ⁇ 170, and is further preferably set within the range of 155 ⁇ ⁇ 2 ⁇ 165.
  • Exit Angle ⁇ 2 is greater than the above-described appropriate range, the narrow gap of the blades makes the outflow higher so as to generate high noise even though the airflow between blades can reattach as shown in Fig. 12(A) .
  • Exit Angle ⁇ 2 is smaller than the above-described appropriate range, the airflow between blades cannot reattach, so that the shear flow is greatly fluctuated as shown in Fig. 12(C) .
  • Exit Angle ⁇ 2 is set within the above-described appropriate range, the airflow between blades can reattach, so that appropriate suppression of flow rate between blades makes it possible to achieve the low noise generation as shown in Fig. 12(B) .
  • the fan efficiency becomes desirable. Those phenomena are shown in Table 4.
  • Entrance Angle ⁇ 1 (deg) of the blade is preferably set within the range of 50 ⁇ ⁇ 1 ⁇ 90, and is more preferably set within the range of 55 ⁇ ⁇ 1 ⁇ 85, and is further preferably set within the range of 60 ⁇ ⁇ 1 ⁇ 80.
  • Entrance Angle ⁇ 1 is greater than the above-described appropriate range, the great difference between the inflow angle and the entrance angle increases an anterior burble, so as to generate higher noise as shown in Fig. 14(A) .
  • Entrance Angle ⁇ 1 is smaller than the above-described appropriate range, too much turning from the inflow into the blades to the outflow from them causes higher noise as shown in Fig.
  • the structure of the multi-blade fan for a centrifugal blower according to the present invention is suitable for a blower used in an air conditioning system for vehicles, which strongly demands low noise generation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP10831457A 2009-11-19 2010-11-04 Lüfter mit mehreren blättern für ein zentrifugalgebläse Withdrawn EP2503157A1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2009264094 2009-11-19
JP2010196893A JP2011127586A (ja) 2009-11-19 2010-09-02 遠心式送風機の多翼ファン
PCT/JP2010/069575 WO2011062062A1 (ja) 2009-11-19 2010-11-04 遠心式送風機の多翼ファン

Publications (1)

Publication Number Publication Date
EP2503157A1 true EP2503157A1 (de) 2012-09-26

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EP10831457A Withdrawn EP2503157A1 (de) 2009-11-19 2010-11-04 Lüfter mit mehreren blättern für ein zentrifugalgebläse

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EP (1) EP2503157A1 (de)
JP (1) JP2011127586A (de)
CN (1) CN102667173A (de)
WO (1) WO2011062062A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150184663A1 (en) * 2013-12-30 2015-07-02 Dongbu Daewoo Electronics Corporation Centrifugal fan for devices including refrigerators
WO2019025710A1 (fr) * 2017-08-02 2019-02-07 Valeo Systemes Thermiques Roue de type centrifuge pour groupe moto-ventilateur
FR3069896A1 (fr) * 2017-08-02 2019-02-08 Valeo Systemes Thermiques Roue de type centrifuge pour groupe moto-ventilateur
FR3074237A1 (fr) * 2017-11-24 2019-05-31 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile
FR3074236A1 (fr) * 2017-11-24 2019-05-31 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile
EP2991206B1 (de) * 2013-04-25 2020-04-29 Changzhou Leili Motor Science & Technology Co., Ltd. Bürstenloser motor für abflusspumpe und abflusspumpe
US10718351B2 (en) 2015-08-06 2020-07-21 Mitsubishi Electric Corporation Centrifugal blower, air conditioning apparatus, and refrigerating cycle apparatus

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KR101448942B1 (ko) 2012-12-31 2014-10-14 갑을오토텍(주) 블로어
GB201310773D0 (en) * 2013-06-17 2013-07-31 Northwick Park Inst For Medcal Res Ltd Implant and method of producing an implant
CN105782076A (zh) * 2016-04-29 2016-07-20 浙江苏泊尔家电制造有限公司 离心风机和抽油烟机
CN208587316U (zh) * 2018-07-27 2019-03-08 深圳市大疆创新科技有限公司 离心风扇及电子设备
CN110382876B (zh) * 2018-07-27 2022-02-22 深圳市大疆创新科技有限公司 离心风扇及电子设备
WO2020019294A1 (zh) * 2018-07-27 2020-01-30 深圳市大疆创新科技有限公司 离心风扇及电子设备
CN110319054B (zh) * 2019-05-30 2020-09-18 宁波方太厨具有限公司 一种用于前向离心风机的叶轮
CN110878768A (zh) * 2019-12-20 2020-03-13 中国北方发动机研究所(天津) 一种具有变进口叶片角型导流叶片的有叶扩压器结构
CN111997936B (zh) * 2020-08-27 2021-04-06 华中科技大学 一种可调节蜗舌装置及贯流风机
KR102617365B1 (ko) * 2021-09-29 2023-12-21 대륜산업 주식회사 환기팬 임펠러

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JPH07260315A (ja) * 1994-03-28 1995-10-13 Hitachi Ltd 冷凍冷蔵庫
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JP5151331B2 (ja) * 2007-09-10 2013-02-27 パナソニック株式会社 多翼羽根車および多翼送風機

Non-Patent Citations (1)

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See references of WO2011062062A1 *

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2991206B1 (de) * 2013-04-25 2020-04-29 Changzhou Leili Motor Science & Technology Co., Ltd. Bürstenloser motor für abflusspumpe und abflusspumpe
US20150184663A1 (en) * 2013-12-30 2015-07-02 Dongbu Daewoo Electronics Corporation Centrifugal fan for devices including refrigerators
US9885361B2 (en) * 2013-12-30 2018-02-06 Dongbu Daewoo Electronics Corporation Centrifugal fan for devices including refrigerators
US10718351B2 (en) 2015-08-06 2020-07-21 Mitsubishi Electric Corporation Centrifugal blower, air conditioning apparatus, and refrigerating cycle apparatus
WO2019025710A1 (fr) * 2017-08-02 2019-02-07 Valeo Systemes Thermiques Roue de type centrifuge pour groupe moto-ventilateur
FR3069896A1 (fr) * 2017-08-02 2019-02-08 Valeo Systemes Thermiques Roue de type centrifuge pour groupe moto-ventilateur
FR3069895A1 (fr) * 2017-08-02 2019-02-08 Valeo Systemes Thermiques Roue de type centrifuge pour groupe moto-ventilateur
FR3074237A1 (fr) * 2017-11-24 2019-05-31 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile
WO2019102101A1 (fr) * 2017-11-24 2019-05-31 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile
FR3074236A1 (fr) * 2017-11-24 2019-05-31 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile

Also Published As

Publication number Publication date
CN102667173A (zh) 2012-09-12
JP2011127586A (ja) 2011-06-30
WO2011062062A1 (ja) 2011-05-26

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