EP0955469B1 - Impeller of fan - Google Patents
Impeller of fan Download PDFInfo
- Publication number
- EP0955469B1 EP0955469B1 EP99106357A EP99106357A EP0955469B1 EP 0955469 B1 EP0955469 B1 EP 0955469B1 EP 99106357 A EP99106357 A EP 99106357A EP 99106357 A EP99106357 A EP 99106357A EP 0955469 B1 EP0955469 B1 EP 0955469B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- blade
- impeller
- fan
- shows
- view
- 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.)
- Expired - Lifetime
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
Definitions
- An air conditioner adjusts temperature and humidity of the air, and generally comprises an air-cooler, an air-heater, a humidifier, a fan and an air-filter.
- the present invention addresses the problems discussed above and aims to provide a fan's impeller having less noise and greater static pressure.
- the impeller of the present invention is less noisy by 2 dB than the conventional impeller. Further, the impeller of the present invention remains less noisy up to point Q2 where 68% of open-air volume is blown. Regarding the static pressure, the impeller of the present invention gains 32% increase compared with the conventional impeller at point Q3 where 60% of open-air volume is blown.
- Passage centerline B-B is drawn between the midpoints of the leading and trailing edges of blade 12 on a revolution locus.
- the cross sectional view of blade 12 in the radial direction shows a valley in the upper half and shows a peak in the lower half, with regard to windward.
- the upper half is defined as a portion between around the centerline B-B and tip 14, and the lower half is defined as a portion between around the centerline B-B and hub 13.
Description
- The present invention relates to an impeller of a fan employed in air conditioners and the like, and more particularly to the shape of the impeller.
- An air conditioner adjusts temperature and humidity of the air, and generally comprises an air-cooler, an air-heater, a humidifier, a fan and an air-filter.
- Fig. 8 shows a conventional impeller of a mixed-flow-fan employed in the air conditioner. In the mixed-flow-fan, gas flows slantingly with regard to a rotary shaft.
- In Fig. 8,
impeller 21 of the mixed-flow-fan is equipped with a plurality ofthin blades 22 radially mounted onhub 23 which substantially shapes as a taper stand. - Fig. 9 is a cross sectional view taken on line D-D of Fig. 8. The cross sectional view of
blade 22 in the radial direction shows a substantial direct line or a curve bent toward only one direction.Impeller 21 is housed in the [same casing and driven by the rotary shaft fitted inhub 23 that is coupled to a motor.Impeller 21 is thus rotated by the motor, thereby blowing air. - However, the conventional construction discussed above cannot control blade-tip-vortex generated around outer edge portion of
blade 22 on a satisfactory level during the blowing, because the cross sectional view of theblade 22 shapes as a substantial direct line or a curve bent toward only one direction. - Further,
blades 22 are not equipped with any countermeasures against airflow drawn in radial direction, the airflow is generated whenimpeller 21 is driven by a high load. - It would thus be desirable to improve a conventional impeller as shown in Fig. 8 such as
impeller 21 by requiring it to have less noise by controlling the blade-tip-vortex and to have a greater static pressure by smoothening the drawn airflow. - Reference may be made to EP-A-0 887 558 relative to which the present invention is characterised.
- The present invention addresses the problems discussed above and aims to provide a fan's impeller having less noise and greater static pressure.
- The present invention thus has as object an impeller according to
claim 1. - The impeller of the present invention draws a revolution locus at its leading edge. The both shapes of the locus and blade are the features of the present invention. The locus of upper half of the blade shows a valley and that of lower half of the blade shows a peak, with regard to windward. The upper half of the blade is defined as a portion between around the blade center and the outer end, while the lower half of the blade is defined as a portion between around the blade center and the hub. The cross section of the upper half of the blade in a radial direction shows a valley and that of the lower half shows a peak, with regard to windward.
- The shapes discussed above allow the impeller to restrain airflow from breaking away off the blades. The blade-tip-vortex on a suction surface near the outer end of a blade is generated by the airflow that turns over from a pressure surface toward a suction surface. A valley-curved portion of the blade thus promotes the production of the vortex, thereby restraining the airflow from breaking away off the blade. As a result, the fan having less noise can be achieved. At the same time, a peak-curved portion of the blade smoothens the airflow drawn in the radial direction during high load operation, thereby increasing the static pressure.
-
- Fig. 1 is a plan view of an impeller of a fan in accordance with a first exemplary embodiment of the present invention.
- Fig. 2 is a partial view of a revolution locus of a blade of the impeller of the fan in accordance with the first exemplary embodiment of the present invention.
- Fig. 3 is a cross section taken on line A-A in Fig. 1.
- Fig. 4 shows the impeller in an operation in accordance with the first exemplary embodiment of the present invention.
- Fig. 5 is a characteristics-comparison-chart of the impeller in accordance with the first exemplary embodiment of the present invention and a conventional impeller.
- Fig. 6 is a cross section of the blade viewed at a centerline of a passage in accordance with a second exemplary embodiment of the present invention.
- Fig. 7 is a cross section of the blade of the impeller viewed in the radial direction and at the maximum thickness portion of the blade in accordance with the second exemplary embodiment of the present invention.
- Fig. 8 is a plan view of a conventional impeller of a fan.
- Fig. 9 is a cross section of the conventional impeller taken on line D-D of Fig. 8.
-
- Exemplary embodiments of the present invention are described with reference to the accompanying drawings.
- The first exemplary embodiment of the present invention is described hereinafter with reference to Fig. 1 through Fig. 5.
- Fig. 1 is a plan view of an impeller of a mixed flow fan. Fig. 4 shows the active impeller.
- In Fig. 1,
impeller 1 of mixed-flow-fan is mounted onhub 3 substantially shaping as a taper stand and has threethin blades 2 in the radial direction on the taper stand rim. An arrow mark indicates a rotational direction. As shown in Fig. 4,hub 3 mounted withblades 2 is fixed to a rotary shaft ofmotor 4, andimpeller 1 is housed incasing 5.Impeller 1 blows air by drivingmotor 4 in a direction indicated by an arrow mark. At this time, as shown in Fig. 1, most of the airflow flows into leadingedge 6 ofblade 2 and flows out fromtrailing edge 7. Impeller 1 blows air in this manner. - Fig. 2 is a partial view of a revolution locus of
blade 2 ofimpeller 1. In Fig. 2, the revolution locus drawn by leadingedge 6 ofblade 2 shows a valley in an upper half thereof and a peak in a lower half, with regard to windward. The upper half of theblade 2 is defined as a portion between around the blade center and the outer end 8 (hereinafter referred to as "tip 8"), while the lower half of theblade 2 is defined as a portion between around the blade center and thehub 3. Line B-B is drawn by connecting respective midpoints of leadingedge 6 andtrailing edge 7 ofblade 2. Line B-B shows a center of passage through which the airflow flows in the direction indicated by the arrow mark. Line C-C shows a hub center i.e. a rotation center ofimpeller 1. - Fig. 3 is a cross section taken on line A-A in Fig. 1. As shown in Fig. 3, the cross section of
blade 2 in radial direction shows a valley in an upper half of the blade and shows a peak in a lower half thereof, with regard to windward. The upper half of the cross sectional view ofblade 2 is defined as a portion between around the line B-B andtip 8, while the lower half thereof is defined as a portion between around the line B-B and thehub 3. This structure allowstip 8 to produce airflow aroundtip 8 itself, and the airflow turns over frompressure surface 10 ofblade 2 towardsuction surface 9 thereof. The airflow produces blade-tip-vortex aroundtip 8 onsuction side 9, and a valley-curved portion ofblade 2 promotes the production so that the airflow is restrained from breaking away off the blade. As a result,impeller 1 having less noise can be achieved. At the same time, a peak-curved portion ofblade 2 smoothens the airflow increasingly drawn in the radial direction during high load operation, i.e. the airflow flowed in fromtip 8 side, thereby increasing the static pressure. - As such, the present invention can reduce noises, and increase static pressure during a high load operation of the impeller.
- Specific advantages of the first exemplary embodiment are described hereinafter.
- Fig. 5 is a characteristics-comparison-chart of the impeller of the present invention and a conventional impeller. The impeller of which blade measures 400 mm across is used in the experiment. Characteristics of static pressure and noise with regard to air volume are shown in the chart.
- As this experiment tells, at an open air volume point Q1, the impeller of the present invention is less noisy by 2 dB than the conventional impeller. Further, the impeller of the present invention remains less noisy up to point Q2 where 68% of open-air volume is blown. Regarding the static pressure, the impeller of the present invention gains 32% increase compared with the conventional impeller at point Q3 where 60% of open-air volume is blown.
- The second exemplary embodiment of the present invention is described with reference to Fig. 6 and Fig. 7.
- Fig. 6 is a cross section of the blade shown in Fig. 7 and taken on line B-B that is a centerline of a passage. Fig. 7 is a cross section of the blade of the impeller viewed in the radial direction and at the maximum thickness portion of the blade. As shown in Fig. 6, the impeller of the fan in accordance with the second exemplary embodiment has blades shaping as a wing.
- Passage centerline B-B is drawn between the midpoints of the leading and trailing edges of
blade 12 on a revolution locus. In this embodiment,blade 12 has the following measurements on its cross section taken on the passage center line B-B: 5% ≤ t/c ≤ 12%,
where: t = maximum thickness ofblade 12 taken on line B-B,
c = distance between the leading and trailing edges ofblade 12, and the blade shapes as a wing having an arc front edge and a sharp rear edge. - Further in this embodiment, the cross sectional view of
blade 12 in the radial direction shows a valley in the upper half and shows a peak in the lower half, with regard to windward. The upper half is defined as a portion between around the centerline B-B andtip 14, and the lower half is defined as a portion between around the centerline B-B andhub 13. - The structure discussed above allows a valley-curved portion of
blade 12 to promote the production of blade-tip-vortex produced aroundtip 14 on the suction surface side by airflow taking over frompressure surface 16 towardsuction surface 15 so that the airflow is restrained from breaking away off theblade 12. As a result,impeller 11 having less noise can be achieved. - At the same time, a peak-curved portion of
blade 12 smoothens the airflow increasingly drawn in the radial direction during high load operation, i.e. the airflow flowed in fromtip 14 side, thereby increasing the static pressure. - The second exemplary embodiment proves that less noise and greater static pressure are achieved in
impeller 11, as the first exemplary embodiment shows the same effects. - Compared with blades having a constant thickness, the blade of the second exemplary embodiment has the measurement such as 5% ≤ t/c ≤ 12%, where: t= maximum thickness, c= blade depth spanning between the mid- points of leading and trailing edges, and the blade shaping as a wing having an arc front edge and a sharp rear edge, so that the airflow is more securely prevented from breaking away off the blade. Accordingly, the noise level can be further lowered.
- The following result is reported by the measurement of low noise effect on the impeller used in the second exemplary embodiment: Low noise effect is noticed starting from t/c = 5%, and is saturated at t/c=12%. In the case of the impeller measuring 400 mm across, employed in a mixed flow fan, when the blade shape of t/c =9% is used, the experiment shows that noise level is lowered by 2 dB comparing with the blade having a constant thickness.
- Not limited to the impeller of the mixed flow fan, the technique of the present invention can also produce the same effect in an impeller of axial flow fan where gas flows along a rotary shaft within the impeller.
Claims (5)
- Impeller of a fan, said impeller including a hub (3) mounted with a plurality of blades (2), and arranged to spin the blades (2), thereby blowing air:wherein a cross-sectional view of the blade (2) in a radial direction shows a peak in a portion between a center portion of the blade and the hub (3) with regard to windward;said cross-sectional view of the blade (2) shows a valley in a portion between the center portion and the tip (8); anda revolution locus of a leading edge (6) of the blade (2) shows a valley in a portion between the tip (8) and the center portion of the blade (2), and shows a peak in a portion between the center portion and the hub (3), with regard to windward.
- The impeller of a fan as defined in Claim 1 wherein the thickness of the blade (2) is constant.
- The impeller of a fan as defined in Claim I wherein a cross sectional view of the blade (12) taken on a passage center running from the leading edge (6) to a trailing edge (7) is shaped to have a ratio of a maximum thickness at the passage center vs. a distance between the leading edge (6) and the trailing edge (7) ranging from 5% to 12% inclusive both the values.
- The impeller of a fan as defined in Claim 1 whereinthe cross sectional view of the blade (12) taken on a passage centerline connecting the leading edge (6) and a trailing edge (7) of the blade (12) is shaped to be 5% ≤ t/c ≤ 12%, where: t = maximum thickness of the blade (12), and c = blade depth spanning between the midpoints of leading and trailing edges.
- The impeller of a fan as defined in any one of the preceding claims, wherein said fan is a mixed flow fan.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10234498 | 1998-04-14 | ||
JP10234498A JP3204208B2 (en) | 1998-04-14 | 1998-04-14 | Mixed-flow blower impeller |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0955469A2 EP0955469A2 (en) | 1999-11-10 |
EP0955469A3 EP0955469A3 (en) | 2001-02-28 |
EP0955469B1 true EP0955469B1 (en) | 2004-10-20 |
Family
ID=14324890
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99106357A Expired - Lifetime EP0955469B1 (en) | 1998-04-14 | 1999-03-29 | Impeller of fan |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0955469B1 (en) |
JP (1) | JP3204208B2 (en) |
CN (1) | CN1107808C (en) |
ES (1) | ES2230759T3 (en) |
MY (1) | MY123252A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8894354B2 (en) | 2010-09-07 | 2014-11-25 | Dyson Technology Limited | Fan |
US9328739B2 (en) | 2012-01-19 | 2016-05-03 | Dyson Technology Limited | Fan |
US9568021B2 (en) | 2012-05-16 | 2017-02-14 | Dyson Technology Limited | Fan |
US9568006B2 (en) | 2012-05-16 | 2017-02-14 | Dyson Technology Limited | Fan |
DE102022119333A1 (en) | 2022-08-02 | 2024-02-08 | Technische Universität Darmstadt, Körperschaft des öffentlichen Rechts | Turbomachine with an adjustable axial impeller arrangement |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3473549B2 (en) * | 2000-04-28 | 2003-12-08 | 松下電器産業株式会社 | Blower impeller and air conditioner equipped with the blower impeller |
BR0003706A (en) | 2000-05-30 | 2002-02-13 | Tecsis Tecnologia E Sist S Ava | Axle fan for low noise and high efficiency |
DE10110243A1 (en) * | 2001-03-05 | 2002-09-12 | Glen Dimplex Deutschland Gmbh | heater |
TW524928B (en) * | 2001-04-26 | 2003-03-21 | Daikin Ind Ltd | Blower and air conditioner with the same |
KR100761153B1 (en) * | 2001-06-12 | 2007-09-21 | 한라공조주식회사 | Axial flow fan |
JP3960776B2 (en) * | 2001-11-09 | 2007-08-15 | 松下電器産業株式会社 | Blower impeller for air conditioning |
KR100487339B1 (en) * | 2002-11-18 | 2005-05-03 | 엘지전자 주식회사 | axial flow fan |
KR100484824B1 (en) * | 2002-11-19 | 2005-04-22 | 엘지전자 주식회사 | An axial flow fan |
KR101187223B1 (en) | 2005-04-06 | 2012-10-02 | 한라공조주식회사 | Axial Flow Fan |
JP4631563B2 (en) * | 2005-06-29 | 2011-02-16 | パナソニック株式会社 | Blower |
JP4802694B2 (en) * | 2005-12-13 | 2011-10-26 | パナソニック株式会社 | Blower impeller and air conditioner |
JP5003198B2 (en) * | 2006-06-19 | 2012-08-15 | パナソニック株式会社 | Air conditioner outdoor unit |
JP4967882B2 (en) * | 2007-07-23 | 2012-07-04 | パナソニック株式会社 | Mixed flow blower impeller and air conditioner |
JP4967883B2 (en) * | 2007-07-23 | 2012-07-04 | パナソニック株式会社 | Mixed flow blower impeller and air conditioner |
GB2468312A (en) | 2009-03-04 | 2010-09-08 | Dyson Technology Ltd | Fan assembly |
GB2476172B (en) | 2009-03-04 | 2011-11-16 | Dyson Technology Ltd | Tilting fan stand |
JP2012026402A (en) * | 2010-07-27 | 2012-02-09 | Panasonic Corp | Mixed flow fan and air conditioner with the same |
GB2486019B (en) | 2010-12-02 | 2013-02-20 | Dyson Technology Ltd | A fan |
CN102003412B (en) * | 2010-12-03 | 2014-04-02 | 陈新 | Wing shaped blade of high-pressure axial fan |
CN103161759B (en) * | 2011-12-09 | 2016-03-02 | 珠海格力电器股份有限公司 | Axial-flow leaf |
EP2850324A2 (en) | 2012-05-16 | 2015-03-25 | Dyson Technology Limited | A fan |
FR2991012B1 (en) * | 2012-05-23 | 2016-08-12 | Valeo Systemes Thermiques | AUTOMOBILE FAN WITH OPTIMIZED BLADES |
GB2503907B (en) | 2012-07-11 | 2014-05-28 | Dyson Technology Ltd | A fan assembly |
WO2014162552A1 (en) | 2013-04-04 | 2014-10-09 | 三菱電機株式会社 | Propeller fan, blower device, and outdoor equipment |
GB2530906B (en) | 2013-07-09 | 2017-05-10 | Dyson Technology Ltd | A fan assembly |
DE102015216579A1 (en) | 2015-08-31 | 2017-03-02 | Ziehl-Abegg Se | Fan, fan and system with at least one fan |
CN108431428B (en) | 2015-11-16 | 2020-06-16 | 雷姆控股有限公司 | Ultra-low noise axial flow fan for industry |
US11519422B2 (en) * | 2018-05-09 | 2022-12-06 | York Guangzhou Air Conditioning And Refrigeration Co., Ltd. | Blade and axial flow impeller using same |
CN108506247A (en) * | 2018-05-09 | 2018-09-07 | 约克广州空调冷冻设备有限公司 | Blade and use its axial wheel |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1964525A (en) * | 1932-07-30 | 1934-06-26 | Gen Electric | Fan blade |
US3416725A (en) * | 1967-10-12 | 1968-12-17 | Acme Engineering And Mfg Corp | Dihedral bladed ventilating fan |
JPS5783696A (en) * | 1980-11-14 | 1982-05-25 | Nippon Denso Co Ltd | Fan |
US5906179A (en) * | 1997-06-27 | 1999-05-25 | Siemens Canada Limited | High efficiency, low solidity, low weight, axial flow fan |
-
1998
- 1998-04-14 JP JP10234498A patent/JP3204208B2/en not_active Expired - Lifetime
-
1999
- 1999-03-27 MY MYPI99001194A patent/MY123252A/en unknown
- 1999-03-29 ES ES99106357T patent/ES2230759T3/en not_active Expired - Lifetime
- 1999-03-29 EP EP99106357A patent/EP0955469B1/en not_active Expired - Lifetime
- 1999-04-13 CN CN99105133A patent/CN1107808C/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8894354B2 (en) | 2010-09-07 | 2014-11-25 | Dyson Technology Limited | Fan |
US9328739B2 (en) | 2012-01-19 | 2016-05-03 | Dyson Technology Limited | Fan |
US9568021B2 (en) | 2012-05-16 | 2017-02-14 | Dyson Technology Limited | Fan |
US9568006B2 (en) | 2012-05-16 | 2017-02-14 | Dyson Technology Limited | Fan |
DE102022119333A1 (en) | 2022-08-02 | 2024-02-08 | Technische Universität Darmstadt, Körperschaft des öffentlichen Rechts | Turbomachine with an adjustable axial impeller arrangement |
Also Published As
Publication number | Publication date |
---|---|
CN1232143A (en) | 1999-10-20 |
EP0955469A2 (en) | 1999-11-10 |
JP3204208B2 (en) | 2001-09-04 |
ES2230759T3 (en) | 2005-05-01 |
MY123252A (en) | 2006-05-31 |
EP0955469A3 (en) | 2001-02-28 |
JPH11294389A (en) | 1999-10-26 |
CN1107808C (en) | 2003-05-07 |
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