WO2016066111A1 - Hélice centrifuge arrière et soufflante centrifuge - Google Patents

Hélice centrifuge arrière et soufflante centrifuge Download PDF

Info

Publication number
WO2016066111A1
WO2016066111A1 PCT/CN2015/093124 CN2015093124W WO2016066111A1 WO 2016066111 A1 WO2016066111 A1 WO 2016066111A1 CN 2015093124 W CN2015093124 W CN 2015093124W WO 2016066111 A1 WO2016066111 A1 WO 2016066111A1
Authority
WO
WIPO (PCT)
Prior art keywords
centrifugal impeller
vane
splitter
chassis
backward centrifugal
Prior art date
Application number
PCT/CN2015/093124
Other languages
English (en)
Chinese (zh)
Inventor
刘池
熊军
廖俊杰
彭勃
Original Assignee
珠海格力电器股份有限公司
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 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2016066111A1 publication Critical patent/WO2016066111A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—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
    • F04D29/26—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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps

Definitions

  • the centrifugal impeller is named as the forward, radial and backward impeller according to the angle between the exit side and the opposite direction of the peripheral speed.
  • the forward impeller exit angle is greater than 90°
  • the radial impeller exit angle is equal to 90°
  • the backward impeller exit The angle is less than 90°.
  • the full pressure of the outlet of the forward impeller is greater than that of the radial impeller.
  • the total aerodynamic noise of the impeller is proportional to the flow rate and total pressure. Therefore, the use of a backward impeller can achieve better noise performance without requiring a higher total pressure condition.
  • the degree of rearward expansion of the long blade flow channel is severe, resulting in uneven airflow velocity in the flow channel, causing turbulence and turbulence noise.
  • the main object of the present invention is to provide a backward centrifugal impeller and a centrifugal fan to solve the problem of turbulent noise which is easy to generate in the backward centrifugal impeller in the prior art.
  • a rearward centrifugal impeller comprising: a chassis; a plurality of air guiding blades, a plurality of air guiding blades are arranged along a circumference of the chassis, and each of the air guiding blades is from the chassis The central portion extends toward the outer edge of the chassis, and a flow guiding channel is formed between two adjacent air guiding vanes; the backward centrifugal impeller further includes: a splitter vane disposed in the diversion channel to reduce gas in the diversion channel Speed changes.
  • the extending direction of the splitter blade is consistent with the extending direction of the wind guide vane, and the distance from the center of the splitter blade near the center of the chassis to the center of the chassis is greater than the distance from the center of the guide vane near the center of the chassis to the center of the chassis.
  • splitter vanes are disposed on the chassis and are located in a downstream section of the flow guide channel adjacent the outer edge of the chassis.
  • the length of the splitter blade is 1/3 to 2/3 of the length of the wind guide blade.
  • the distance from the splitter blade to the suction face side of the wind guide blade is smaller than the distance from the splitter blade to the pressure face side of the wind guide blade.
  • the distance from the splitter blade to the suction face side of the wind guide blade is greater than the distance from the splitter blade to the pressure face side of the wind guide blade.
  • a splitter vane is disposed between the adjacent two air guiding vanes, and the splitter vane is located at the center of the diversion channel.
  • the width of the wind guide vanes is consistent with the width of the splitter vanes.
  • a centrifugal fan including a backward centrifugal impeller, and the backward centrifugal impeller is the above-described backward centrifugal impeller.
  • the plurality of air guiding blades are evenly arranged along the circumferential direction of the chassis, and each of the air guiding blades extends from the center of the chassis to the outer edge of the chassis, and a guiding channel is formed between the adjacent two guiding blades.
  • the flow guiding channel formed at this time is widened from the center of the chassis to the outer edge of the chassis, and when the gas flows out from the flow guiding channel, the velocity of the gas decreases with the widening of the guiding channel; the splitter blade It is disposed in the flow guiding channel, can occupy the space of the guiding channel, reduce the volume change of the guiding channel, and further reduce the velocity change of the gas in the guiding channel.
  • the invention provides a shunt blade in the flow guiding channel capable of reducing the velocity change of the gas in the flow guiding channel, so that the gas flow velocity in the guiding channel is changed little, the gas flow velocity in the guiding channel is uniform, and the disorder is not easy to occur.
  • the generation of turbulent noise can be avoided, and the performance of the backward centrifugal impeller can be improved.
  • Figure 1 is a schematic perspective view showing a first embodiment of a backward centrifugal impeller of the present invention
  • Figure 4 is a schematic plan view showing a second embodiment of the backward centrifugal impeller of the present invention.
  • Figure 5 is a schematic perspective view showing a third embodiment of the backward centrifugal impeller of the present invention.
  • a rearward centrifugal impeller in accordance with a first embodiment of the present invention, includes a chassis 10, a plurality of air guiding blades 20, and a splitter blade 30.
  • the plurality of air guiding blades 20 are evenly arranged along the circumferential direction of the chassis 10, and each of the air guiding blades 20 extends from the center of the chassis 10 toward the outer edge of the chassis 10, and a flow guiding channel 40 is formed between the two adjacent air guiding blades 20,
  • the flow guiding passage 40 formed at this time is sequentially widened from the center of the chassis 10 toward the outer edge of the chassis 10, and when the gas flows out into the flow guiding passage 40, the velocity of the gas becomes wider as the flow guiding passage 40 becomes wider.
  • the splitter blade 30 of the present embodiment is disposed in the flow guiding channel 40, can occupy the space of the flow guiding channel 40, reduce the volume change of the guiding channel 40, and thereby reduce the flow guiding channel.
  • the velocity of the gas within 40 changes.
  • the present invention provides a shunting vane 30 capable of reducing the velocity change of the gas in the flow guiding passage 40 in the flow guiding passage 40, so that the gas flow velocity in the guiding passage 40 is small, and the disorder is not likely to occur, and the guiding passage 40 is not easily generated.
  • the gas flow rate inside is uniform, which can avoid the generation of turbulent noise and improve the performance of the backward centrifugal impeller.
  • the volume of the flow guiding passage 40 is the largest, the speed of the gas changes the fastest, and the speed is the smallest, in order to effectively prevent the gas velocity from changing too fast
  • the extending direction of the splitter blade 30 in this embodiment coincides with the extending direction of the wind guide vane 20, and the distance from the center of the splitter blade 30 near the center of the chassis 10 to the center of the chassis 10 is greater than the center of the wind guide blade 20 near the chassis 10.
  • the distance from one end of the chassis 10 to the center of the disk 10 facilitates a reduction in the change in gas velocity at the wider position of the flow channel 40.
  • the splitter vane 30 of the present embodiment is disposed on the chassis 10 and located at a downstream portion of the flow guiding passage 40 near the outer edge of the chassis 10, capable of diverting gas at the widest position of the flow guiding passage 40, After the splitter vanes 30 are increased, the degree of expansion of the flow guiding passages 40 is significantly reduced, and the relative velocity of the airflow changes more uniformly.
  • the length of the splitter blade 30 is 1/3 to 2/3 of the length of the wind guide vane 20, for example, 1/2, which can effectively prevent the flow velocity of the gas from changing too fast at a wide position of the flow guide passage 40 to generate The emergence of a disordered phenomenon.
  • the splitter blade 30 of the present embodiment is disposed close to the wind guide vane 20, which can reduce the influence of the axial eddy current on the main flow, reduce the eddy current drop of the blade suction surface, reduce the eddy current noise, and improve the sound quality.
  • the distance from the side of the suction vane 30 to the suction side of the air guide vane 20 is smaller than the side of the pressure side of the splitter vane 30 to the air guide vane 20.
  • a diverting blade 30 is disposed between the adjacent two air guiding blades 20, and the distance from the side of the suction surface of the diverting blade 30 to the suction surface of the suction vane 20 is the diversion channel 40 at the position where the diverting blade 30 is located. 1/3 of the width.
  • the expansion of the flow guiding channel 40 is serious, and the air flow speed is from the inlet of the impeller to the outlet of the impeller, and the relative speed changes greatly, and a uniform transition cannot be formed, resulting in the guiding channel 40 .
  • the internal gas velocity distribution is uneven, causing flow disturbance.
  • the splitter blade 30 after the splitter blade 30 is added, the degree of expansion of the flow guiding channel 40 is significantly reduced, and the relative velocity of the airflow is uniformly changed. At this time, the axial eddy current between the splitter blade 30 and the pressure surface of the wind deflecting blade 20 is more obvious. .
  • the velocity of the airflow on the suction surface that is, the suction surface of the air guiding blade 20 is high, and it is easy to form the suction surface layer.
  • Shedding phenomenon Providing the diverting blade 30 near the suction surface of the wind guide vane 20 can effectively reduce the influence of the axial vortex, and reduce the speed difference between the suction surface and the pressure surface, that is, the pressure surface of the wind guide vane 20, thereby improving the suction surface layer.
  • the eddy current shedding phenomenon reduces the influence of the axial eddy current on the main stream, reduces the eddy current shedding of the blade suction surface, reduces the eddy current noise, and improves the sound quality.
  • the splitter blade 30 of the present invention in the present embodiment is identical to the guide vane 20 except for the length of the wind guide vane 20, specifically, the width of the wind guide vane 20 and the splitter vane
  • the width of 30 is consistent, the shunting effect is good, the structure is simple, and it is easy to implement.
  • the backward centrifugal impeller of the present embodiment further includes a fixing ring 60, and the outer ends of the air guiding blade 20 and the diverting blade 30 are fixed on the fixing ring 60, which is convenient for improving the present invention. Air intake and stability to the centrifugal impeller.
  • a backward centrifugal impeller is provided.
  • the structure of the backward centrifugal impeller of the present embodiment is substantially the same as that of the first embodiment, and is different.
  • the splitter blade 30 of the present embodiment is located at the center of the flow guiding channel 40, which can improve the airflow performance in the flow guiding channel 40, reduce the uneven flow of the airflow in the guiding channel 40, reduce the eddy current noise, and improve the sound quality.
  • a backward centrifugal impeller is provided.
  • the structure of the backward centrifugal impeller of this embodiment is substantially the same as that of the first embodiment, and the difference is
  • the distance from the side of the suction vane 30 of the present embodiment to the suction side of the wind guide vane 20 is greater than the distance from the side of the splitter vane 30 to the pressure side of the wind guide vane 20.
  • the distance from the branching vane 30 to the pressure surface side of the air guiding vane 20 is 1/3 of the width of the flow guiding passage 40 at the position where the diverting vane 30 is located, as in the first embodiment, the shunting of the present embodiment
  • the arrangement of the blade 30 can effectively reduce the influence of the axial eddy current, reduce the speed difference before the suction surface and the pressure surface, thereby improving the eddy current falling off of the suction surface of the suction surface, thereby reducing the influence of the axial eddy current on the main stream and reducing the suction of the blade.
  • the surface layer vortex shedding is removed to avoid the generation of turbulent noise and improve the performance of the backward centrifugal impeller.
  • a centrifugal fan comprising a backward centrifugal impeller, the backward centrifugal impeller being a backward centrifugal impeller in any of the above embodiments.
  • the above-mentioned embodiments of the present invention achieve the following technical effects: improving the airflow performance in the flow channel, reducing the uneven flow of the airflow in the flow channel, reducing the influence of the axial vortex on the main flow, and reducing the suction of the blade.

Abstract

L'invention porte sur une hélice centrifuge arrière et sur une soufflante centrifuge, lesquelles comprennent : un châssis (10) ; une pluralité de pales de guidage d'air (20), la pluralité de pales de guidage d'air (20) étant disposées dans une direction périphérique du châssis (10), et les pales de guidage d'air (20) s'étendant à partir du centre du châssis (10) jusqu'à un bord externe du châssis (10), et un canal de dérivation (40) étant formé entre chacune de deux pales de guidage d'air adjacentes (20) ; et une pale de division (30), disposée dans le canal de dérivation (40) de façon à réduire la variation de vitesse de gaz dans le canal de dérivation (40). L'hélice centrifuge arrière et la soufflante centrifuge sont aptes à réduire la variation d'écoulement de gaz dans le canal de dérivation, de telle sorte que la vitesse d'écoulement de gaz dans le canal de dérivation est régulière, ce qui évite la génération de bruits de turbulence et ce qui améliore les performances de l'hélice centrifuge arrière.
PCT/CN2015/093124 2014-10-29 2015-10-28 Hélice centrifuge arrière et soufflante centrifuge WO2016066111A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410597547.4 2014-10-29
CN201410597547.4A CN104314865A (zh) 2014-10-29 2014-10-29 后向离心叶轮及离心风机

Publications (1)

Publication Number Publication Date
WO2016066111A1 true WO2016066111A1 (fr) 2016-05-06

Family

ID=52370150

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/093124 WO2016066111A1 (fr) 2014-10-29 2015-10-28 Hélice centrifuge arrière et soufflante centrifuge

Country Status (2)

Country Link
CN (1) CN104314865A (fr)
WO (1) WO2016066111A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104314865A (zh) * 2014-10-29 2015-01-28 珠海格力电器股份有限公司 后向离心叶轮及离心风机
CN106321508A (zh) * 2016-10-28 2017-01-11 广东威灵电机制造有限公司 混流叶轮、混流风机及吸尘器
CN106438466A (zh) * 2016-11-03 2017-02-22 海信（山东）空调有限公司 一种离心风机及空调室内机
CN109707647B (zh) * 2017-10-26 2021-09-03 台达电子工业股份有限公司 风扇
CN108425882A (zh) * 2018-05-31 2018-08-21 陈靖 一种新型电吹风风叶
CN109139547B (zh) * 2018-09-19 2024-04-26 珠海格力电器股份有限公司 多叶型离心风叶、离心风机及空调器
CN112648232A (zh) * 2021-01-11 2021-04-13 泛仕达机电股份有限公司 一种具有错列叶片的后向离心风机叶片及后向离心风机
CN114109895B (zh) * 2021-11-25 2022-09-09 北京航空航天大学 抑制附面层分离的周向偏置高速离心叶轮

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11280695A (ja) * 1998-03-26 1999-10-15 Kubota Corp 施肥装置用の遠心ブロワ
FR2811156B1 (fr) * 2000-06-30 2006-12-15 Valeo Equip Electr Moteur Ventilateur pour machine electrique tournante, notamment pour alternateur de vehicule automobile
CN103511354A (zh) * 2012-06-25 2014-01-15 珠海格力电器股份有限公司 导流结构及具有该导流结构的轴流机组
CN203488432U (zh) * 2013-10-01 2014-03-19 湖北双剑鼓风机股份有限公司 一种高效压缩机的三元流叶轮
CN203835797U (zh) * 2014-02-24 2014-09-17 温州市天龙轻工设备有限公司 离心压缩机叶轮
CN104314865A (zh) * 2014-10-29 2015-01-28 珠海格力电器股份有限公司 后向离心叶轮及离心风机
CN204140487U (zh) * 2014-10-29 2015-02-04 珠海格力电器股份有限公司 后向离心叶轮及离心风机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2337795A (en) * 1998-05-27 1999-12-01 Ebara Corp An impeller with splitter blades
JP5308319B2 (ja) * 2009-12-02 2013-10-09 三菱重工業株式会社 遠心圧縮機の羽根車
CN102506029B (zh) * 2011-12-29 2014-04-16 中联重科股份有限公司 一种离心风机叶轮及离心风机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11280695A (ja) * 1998-03-26 1999-10-15 Kubota Corp 施肥装置用の遠心ブロワ
FR2811156B1 (fr) * 2000-06-30 2006-12-15 Valeo Equip Electr Moteur Ventilateur pour machine electrique tournante, notamment pour alternateur de vehicule automobile
CN103511354A (zh) * 2012-06-25 2014-01-15 珠海格力电器股份有限公司 导流结构及具有该导流结构的轴流机组
CN203488432U (zh) * 2013-10-01 2014-03-19 湖北双剑鼓风机股份有限公司 一种高效压缩机的三元流叶轮
CN203835797U (zh) * 2014-02-24 2014-09-17 温州市天龙轻工设备有限公司 离心压缩机叶轮
CN104314865A (zh) * 2014-10-29 2015-01-28 珠海格力电器股份有限公司 后向离心叶轮及离心风机
CN204140487U (zh) * 2014-10-29 2015-02-04 珠海格力电器股份有限公司 后向离心叶轮及离心风机

Also Published As

Publication number Publication date
CN104314865A (zh) 2015-01-28

Similar Documents

Publication Publication Date Title
WO2016066111A1 (fr) Hélice centrifuge arrière et soufflante centrifuge
US11873838B2 (en) Blower for breathing apparatus
US10502231B2 (en) Diffuser pipe with vortex generators
KR101347469B1 (ko) 원심 압축기의 임펠러
JP5502114B2 (ja) 軸流ターボ機械のための環状拡散器、軸流ターボ機械のための配列および軸流ターボ機械
US20140341727A1 (en) Centrifugal Compressor With Casing Treatment For Surge Control
JP2010203447A5 (fr)
JP2011085134A (ja) 排気ガスディフューザ
US10823195B2 (en) Diffuser pipe with non-axisymmetric end wall
CN109611356A (zh) 一种后向离心风机
JP2013529740A (ja) 最適化された効率性を備えた圧縮機およびタービンエンジン
EP3708804A1 (fr) Cavité de pointe d'hélice
CN113175443A (zh) 高效低噪无蜗壳后向离心风机三元流叶轮
CN109026830A (zh) 一种离心叶轮
JP2017203427A (ja) ターボチャージャ
CN108953223A (zh) 一种离心叶轮
CN110219829B (zh) 一种离心蜗壳出口结构
JP2016050486A (ja) 流体機械、及び流体機械の羽根車
WO2016066113A1 (fr) Soufflante centrifuge et conditionneur d'air la possédant
JP6362980B2 (ja) ターボ機械
JPWO2016181463A1 (ja) 軸流送風機
CN108953222B (zh) 一种离心叶轮
CN109931290B (zh) 一种后向离心叶轮
CN204140487U (zh) 后向离心叶轮及离心风机
CN104314867B (zh) 轨道车辆冷却系统用带分流叶片的离心风机叶轮

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15855774

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15855774

Country of ref document: EP

Kind code of ref document: A1