EP1087146B1 - Impeller for fan, fan using the same, and air conditioner using the same - Google Patents

Impeller for fan, fan using the same, and air conditioner using the same Download PDF

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Publication number
EP1087146B1
EP1087146B1 EP20000119461 EP00119461A EP1087146B1 EP 1087146 B1 EP1087146 B1 EP 1087146B1 EP 20000119461 EP20000119461 EP 20000119461 EP 00119461 A EP00119461 A EP 00119461A EP 1087146 B1 EP1087146 B1 EP 1087146B1
Authority
EP
European Patent Office
Prior art keywords
blade
impeller
fan
hub
blades
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20000119461
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1087146A2 (en
EP1087146A3 (en
Inventor
Yoshiki Izumi
Takashi Sugio
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.)
Panasonic Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1087146A2 publication Critical patent/EP1087146A2/en
Publication of EP1087146A3 publication Critical patent/EP1087146A3/en
Application granted granted Critical
Publication of EP1087146B1 publication Critical patent/EP1087146B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/26—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

  • the present invention relates to an impeller used in a fan, a fan using the impeller, and an air conditioner using the same.
  • An impeller as specified in the preamble of Claim 1 is known from US-A-1 807 397 .
  • FIG. 15 A plan of an impeller of a conventional mixed flow fan is shown in Fig. 15 , and a rotation locus diagram of the impeller is given in Fig. 15 .
  • the gas flows in the impeller in inclination toward the rotary shaft.
  • the impeller 18 of the mixed flow fan comprises a truncated conical hub 20, and a plurality of blades 19 disposed in the hub 20.
  • the rotation locus of the impeller 18 is shown in Fig. 14 .
  • the fan comprises this impeller 18, a casing accommodating the impeller 18, a rotary shaft coupled to the hub 20, and a motor. As the impeller 18 is rotated by the motor, a blowing action takes place.
  • the number of blades 19 required for obtaining a sufficient static pressure is at least three or more.
  • the front edge 21 of the blades 19 has a logarithmic spiral or similar curve.
  • the impeller for fan of the invention is defined in Claim 1.
  • the two blades are disposed symmetrically to the center of the hub.
  • the fan of the invention comprises a motor, and an impeller connected to the motor as specified in Claim 9.
  • the air conditioner of the invention is specified in Claim 15.
  • the impeller having two blades is smaller in volume than the impeller having three or more blades, so that the manufacturing cost of the impeller is lowered.
  • the impeller for fan according to the invention is defined in Claim 1.
  • the individual blades are mutually disposed symmetrically to the center of the hub.
  • the impeller having two blades has a smaller volume than the impeller having three blades or four blades.
  • the portion from around the representative square mean radius position of the blade to the position at the outer circumference has a concave curve shape to the windward side
  • the portion from around the representative square mean radius position of the blade to the position at the hub side has a convex curve shape to the windward side.
  • the blade since the blade has a concave curve shape, the blade itself becomes a stream-line body in the rotating direction of the blade. Therefore, in the case of two blades, the blade rotating noise or "nZ" sound becomes lower than the sound pressure level of the turbulent flow noise. As a result, generation of abnormal sound in the entire impeller is prevented. Further, actual auditory sense is improved.
  • one point of triangular auxiliary blade is overlapped on the intersection of the front edge of the blade and the outer circumference, and one side of the triangular auxiliary blade is formed in tight contact with the front edge.
  • the triangular auxiliary vane is disposed in the blade as the principal blade.
  • the blade end vortex is generated conically on the negative pressure surface of the blade, and this blade end vortex is separated and flows away in the midst of the blade.
  • the triangular vane has an action of defining the generation of blade end vortex at its leading end. Accordingly, the triangular blade defines the state of generation of the blade end vortex on the negative pressure surface near the outer circumference of the blade, and the state of the blade end vortex separating from the blade and flowing away. Therefore the triangular blade has an action of minimizing the effect of the blade end vortex on the blade rotating behind.
  • the influent air state of the blade rotating behind can be kept in the smooth and optimum state having a further smaller turbulent flow.
  • the succeeding blade is less influenced by the effect of the blade end vortex, and the influent air into the blade is most smooth, and separation, decline of speed and other unstable phenomena in the succeeding blades are less likely to occur.
  • the fan having such impeller is installed in the outdoor unit of the air conditioner having a heat exchanger.
  • the outdoor unit operates quietly. Further, the manufacturing cost is low. The design is easier and it is more advantageous.
  • Fig. 1 to Fig. 9 show the impeller for fan of an example not covered by the invention.
  • Fig. 1 is a rotation locus diagram of impeller used in a mixed flow blower.
  • Fig. 2 is a plan of the impeller for the mixed flow fan.
  • Fig. 3 is a development by cutting off the impeller for the fan at a representative square mean radius position, and developing it. In Fig. 3 , the blade is a thick blade.
  • Fig. 4 is a development by cutting off the impeller for the fan at a representative square mean radius position, and developing it, in which a thin blade of a specific thickness is applied as the blade.
  • Fig. 5 is a schematic diagram showing an operating status of the impeller used in the fan.
  • Fig. 1 is a rotation locus diagram of impeller used in a mixed flow blower.
  • Fig. 2 is a plan of the impeller for the mixed flow fan.
  • Fig. 3 is a development by cutting off the impeller for the fan at
  • FIG. 6 is a characteristic diagram of characteristic experiment showing the performance of the impeller for the fan, in which the axis of abscissas denotes the aspect ratio b/L, and the axis of ordinates represents the air flow volume at blowing noise 41 dB.
  • Fig. 7 is a characteristic diagram comparing the static pressure characteristics between an impeller for fan having two blades in this example, and an impeller for fan having three blades in a prior art.
  • Fig. 8 is a rotation locus diagram of the impeller for fan when used in an axial flow fan.
  • Fig. 9 is a plan of the impeller for the axial flow fan.
  • the impeller 1 used in the mixed flow fan comprises a truncated conical hub 3, and two blades 2 disposed on the outer circumference of the hub 3.
  • the two blades 2 mutually have an identical shape, and the blades 2 are installed at mutually facing positions. That is, the blades 2 are disposed at mutually symmetrical positions to the center of the hub 3.
  • the blades 2 are defined by the aspect ratio b/L where L is the chord length of the blade at the representative square mean radius position of the blade and b is the representative actual length in the radial direction of the blade.
  • the aspect ratio is equal to 1 or less. That is, the aspect ratio is specified in a range of b/L ⁇ 1.
  • two blades 2 having the aspect ratio defined in this range are disposed.
  • the length "L” defined above is the chord length of the blade at this position of representative square mean radius "Rr”.
  • Fig. 1 the central line of the impeller 1 is 31C-31C, and the apex of the cone passing the representative square mean radius "Rr" is "P1".
  • the development by cutting off the blade 2 along the line 32A-32A of the cone is shown in Fig. 3 and Fig. 4 .
  • the chord length of the blade 2 is "L”.
  • the line 32A-32A is seen in curve 32A-32A in the plan in Fig. 2 .
  • the representative actual length "b" in the radial direction of the blade 2 is the actual length in the span direction of the blade 2 linking the position of the representative hub radius "r" and the position of the representative radius "R".
  • the shaft of the motor 12 is fixed to the hub 3, and they are accommodated in a proper casing 11.
  • a blowing action is generated as indicated by arrow.
  • the majority of the air In Fig. 1 flows in from the front edge 4 of the blade 2, and flows out from the rear edge 5.
  • the impeller 1 works pneumatically.
  • the ratio b/L of the chord length L at the representative square mean radius position of the impeller 1 for the mixed flow fan and the representative actual length "b" in the radial direction of the blade is the aspect ratio.
  • Fig. 6 is a characteristic diagram showing the relation between the aspect ratio b/L of the impeller having two blades, and the air flow rate at blowing noise 41 dB.
  • Fig. 6 is based on the data of the experiment of the impeller 1 having a diameter ( ⁇ ) of 415 mm.
  • the impeller 1 for mixed flow fan of this example has two blades 2 disposed in the hub 3.
  • the aspect ratio b/L of the chord length "L" of the blade 2 at the representative square mean radius position of the blade 2 and the representative actual length b in the radial direction of the blade 2 is set in a range of b/L ⁇ 1, and the impeller 1 has two blades having the specified aspect ratio.
  • the chord length of the outer side of the blade is longer than the chord length of the hub side.
  • Fig. 7 shows a characteristic curve of static pressure characteristic comparing two blades and three blades in the axial flow fan.
  • the impeller for axial flow fan with diameter of 415 mm is operated at a rotating speed of 712 rpm, and the static pressure characteristic is shown at the opening air flow rate point of 29.5 m 3 /min.
  • the opening air flow rate point is the air flow rate when the static pressure is 0.
  • the impeller having two blades shows a stronger static pressure than the impeller having three blades.
  • the impeller having two blades and the impeller having three blades show the same static pressure.
  • the impeller having three blades shows a slightly stronger static pressure than the impeller having two blades.
  • the fan used in the air conditioner is operated, in heating mode, usually in a range from the opening air flow rate point nearly to the air flow rate point Q2.
  • the impeller having two blades is smaller in occupying volume than the impeller having three blades or four blades. Hence, the manufacturing cost of the impeller is lower.
  • Fig. 1 the center line of the impeller is line 31C-31C, the apex of the line 32A-32A of the cone passing the representative square mean radius "Rr" is "P1", and the development of the blade cut off along the line 32A-32A of the cone is shown in Fig. 3 and Fig. 4.
  • Fig. 3 shows the blade having a thick blade 7.
  • the front edge 4 of the blade 7 in the sectional shape of the blade 7 is an arc
  • the rear edge 5 has a pointed end.
  • the blade 7 has a pressure surface 9 and a negative pressure surface 8.
  • each blade has a circular front edge 4 and a sharp rear edge 5, and the shape from the rear edge to the front edge is gradually increased in thickness.
  • Fig. 4 shows the blade having a thin blade 10.
  • the blade 10 has a thin section of a uniform thickness. That is, the shape from the rear edge to the front edge nearly has a same thickness.
  • the blade 10 has a pressure surface 9a and a negative pressure surface 8a.
  • the pressure surface 9a is positioned at the windward side
  • the negative pressure surface 8b is positioned at the windward side.
  • an impeller 15 As an impeller for fan in a further example not covered by the invention, an axial flow fan is explained.
  • a rotation locus diagram of the impeller in the axial flow fan is shown in Fig. 8 , and its plan is given in Fig. 9 .
  • an impeller 15 has two blades 14.
  • the position at the representative square mean radius "Rr" is indicated by line 34B-34B.
  • the aspect ratio b/L of the chord length "L" of the blade 14 at the representative square mean radius position of the blade 14 and the representative actual length b in the radial direction of the blade 14 is set in a range of b/L ⁇ 1.
  • Two blades having the aspect ratio set in the specified range are installed in a hub 13.
  • the impeller for the axial flow fan having such constitution has the same action and effect as the impeller for the mixed flow fan.
  • Fig. 10 is a sectional view in radial direction of the impeller for mixed flow blower in an exemplary embodiment of the invention.
  • Fig. 10 the radial sectional view along line 35B-35B in Fig. 2 is shown, but the vanes of the impeller of this exemplary embodiment are different from the blades of the impeller in previous example of Figures 1 to 9 .
  • Fig. 11 is a diagram showing results of experiment of noise spectrum of impeller for mixed flow fan in this exemplary embodiment of the invention.
  • the impeller of this exemplary embodiment is same as the impeller of the previous examples not covered by the invention, except that only the shape of the blades is different.
  • the parts having the same fan and same action and effect as in the previous examples are identified with same reference numerals, and detailed description is omitted, and different points are mainly explained.
  • the shape from around the line 36A-36A passing the representative square mean radius "Rr" of the blade 2 to the position at the tip 6 side is a concave curve shape 2a toward the windward side
  • the shape from around the line 36A-36A passing the representative square mean radius Rr to the position of the hub 3 side is a convex curve shape 2b toward the windward side.
  • Two blades 2 having such shape are disposed in the hub 3. These two blades 2 are disposed symmetrically to the center of the hub 3.
  • Each blade 2 has a negative pressure surface 8b and a pressure surface 9b.
  • the impeller 16 has two blades 2 having such shape. The impeller 16 is used in the mixed flow fan.
  • Fig. 11 shows the noise spectrum measured when the impeller for mixed flow fan shown in Fig. 10 is operating at a rotating speed of 720 rpm and the air flow rate is 29.8 m 3 /min.
  • the impeller 16 including the blades 2 has a diameter of 415 mm.
  • the blade has a circular front edge and a pointed rear edge.
  • the sound pressure level near 1 kHz is a turbulent flow noise.
  • the 1nZ sound, and its higher harmonics of 2nZ, 3nZ and 4nZ sound are rotating noise.
  • the sound pressure level of turbulent flow noise near 1 kHz it is clearly known from Fig. 11 that the sound pressure level is lower in the rotating noise of the blade, that is, 1nZ sound, and its higher harmonics of 2nZ, 3nZ and 4nZ sound.
  • Fig. 12 is a plan of the impeller for mixed flow fan in a further example not covered by the present invention.
  • the impeller of this further example is same as the impeller of the previous example according to Figures 1 to 9 , except that only the shape of the blades is different.
  • the parts having the same fan and same action and effect as in the said example of Figures 1 to 9 are identified with same reference numerals, and detailed description is omitted, and different points are mainly explained.
  • a triangular auxiliary blade 17 is overlapped with the intersection of the front edge 4 and tip 6 of the blade 2 as the principal blade, and one side of the triangular auxiliary blade 17 is disposed in tight contact with the front edge 4 of the blade 2.
  • Two blades 2 having such triangular auxiliary blade 17 are disposed in the hub 3.
  • the blades 2 are disposed symmetrically to the center of the hub 3.
  • an impeller 40 for mixed flow fan is composed.
  • the vane end vortex 33D is generated conically on the negative pressure surface of the blade 2, and this blade end vortex 33D is separated and flows away in the midst of the blade.
  • the leading end of the triangular auxiliary blade 17 has an action of defining the generation of blade end vortex 33D. Accordingly, it defines the basic points of the state of generation of the blade end vortex 33D on the negative pressure surface near the tip 6 of the blade 2, and the state thereof separating from the blade 2 and flowing away. Therefore it minimizes the effect of the blade end vortex 33D on the vane 2 rotating behind.
  • the influent air state of the blade 2 rotating behind can be kept in the smooth and optimum state having a further smaller turbulent flow.
  • the succeeding blade 2 is less influenced by the effect of the blade end vortex 33D, and the influent air into the blade is most smooth, and separation of air, decline of speed and other unstable phenomena in the blades 2 are less likely to occur.
  • the blade noise is further suppressed and the static pressure is further enhanced.
  • an air conditioner 50 comprises an indoor unit 51 installed indoors, an outdoor unit 52 installed outdoors, and a circulation piping 53 installed between the indoor unit 51 and outdoor unit 52.
  • the indoor unit 51, outdoor unit 52, and circulation piping 53 compose a refrigeration cycle of refrigerant.
  • the outdoor unit 52 includes a heat exchanger 54 and a fan 55.
  • the fan 55 has an impeller 56.
  • the impeller 56 the impeller 1, impeller 15 or impeller 40 explained in the examples of Figures 1 to 9 , 12 and 13 or that of the invention of Figures 9 and 10 are used.
  • the fan 55 has a blowing action for heat exchange of the heat exchanger 54.
  • the fan 55 sends wind into the heat exchanger 54.
  • the fan 55 has a function of moving the near around the heat exchanger 54 by force.
  • the noise generated from the fan 55 is extremely lower than in the air conditioner using the conventional fan. Further, the blowing performance and heat exchange performance are enhanced. Moreover, the manufacturing cost is lower.
  • the two blades are mutually free from effects of blade end vortex of the other blade, and the influent air coming into each blade is less turbulent and more smooth, and separation at blade, decline of speed and other unstable phenomena are less likely to occur.
  • the noise generated by the blade is extremely small.
  • the static pressure is improved.
  • the volume occupied by the impeller is decreased, and the manufacturing cost is saved.
  • the blade rotating noise of "nZ" sound and its higher harmonics are lower than the sound pressure level of turbulent flow noise, and generation of abnormal noise is prevented in the entire impeller. Further, the actual sensory feel is satisfactory.
  • the noise released from the outdoor unit is much lower than in the conventional air conditioner.
  • the blowing performance and heat exchange performance of the air conditioner are improved.
  • a more inexpensive air conditioner is obtained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20000119461 1999-09-24 2000-09-15 Impeller for fan, fan using the same, and air conditioner using the same Expired - Lifetime EP1087146B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP27083099A JP3743222B2 (ja) 1999-09-24 1999-09-24 送風機羽根車と空気調和機
JP27083099 1999-09-24

Publications (3)

Publication Number Publication Date
EP1087146A2 EP1087146A2 (en) 2001-03-28
EP1087146A3 EP1087146A3 (en) 2002-04-03
EP1087146B1 true EP1087146B1 (en) 2008-08-27

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EP20000119461 Expired - Lifetime EP1087146B1 (en) 1999-09-24 2000-09-15 Impeller for fan, fan using the same, and air conditioner using the same

Country Status (5)

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EP (1) EP1087146B1 (zh)
JP (1) JP3743222B2 (zh)
CN (1) CN1297751C (zh)
ES (1) ES2312316T3 (zh)
MY (1) MY131508A (zh)

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JP4492060B2 (ja) * 2003-08-06 2010-06-30 パナソニック株式会社 送風機羽根車
KR100547328B1 (ko) * 2003-09-05 2006-01-26 엘지전자 주식회사 에어컨 실외기의 축류팬
JP4572617B2 (ja) * 2004-07-30 2010-11-04 パナソニック株式会社 空調用送風機羽根車
JP4572633B2 (ja) * 2004-09-08 2010-11-04 パナソニック株式会社 空調用送風機羽根車
JP4529613B2 (ja) * 2004-09-22 2010-08-25 パナソニック株式会社 送風機羽根車
JP4521867B2 (ja) * 2004-10-19 2010-08-11 日立アプライアンス株式会社 空気調和機の室外機
JP4747784B2 (ja) * 2005-10-31 2011-08-17 パナソニック株式会社 軸流送風機の羽根車
JP4802694B2 (ja) * 2005-12-13 2011-10-26 パナソニック株式会社 送風機羽根車及び空気調和機
JP4749175B2 (ja) * 2006-02-14 2011-08-17 シャープ株式会社 プロペラファンと流体送り装置
JP4749176B2 (ja) * 2006-02-14 2011-08-17 シャープ株式会社 プロペラファンと流体送り装置
JP4797776B2 (ja) * 2006-04-24 2011-10-19 パナソニック株式会社 斜流送風機羽根車及び空気調和機
JP4910534B2 (ja) * 2006-07-21 2012-04-04 パナソニック株式会社 送風機羽根車
JP2007107530A (ja) * 2006-11-16 2007-04-26 Toshiba Kyaria Kk 軸流ファン
CN100584365C (zh) * 2006-12-01 2010-01-27 朱炜 用于治疗痤疮的药物组合物
JP4967883B2 (ja) * 2007-07-23 2012-07-04 パナソニック株式会社 斜流送風機羽根車と空気調和機
JP4967882B2 (ja) * 2007-07-23 2012-07-04 パナソニック株式会社 斜流送風機羽根車と空気調和機
JP2012107538A (ja) * 2010-11-16 2012-06-07 Panasonic Corp 軸流ファンまたは斜流ファンおよびこれを有する室外ユニットを搭載した空気調和機
WO2013082717A1 (en) 2011-12-06 2013-06-13 Bachellier Carl Roy Improved impeller apparatus and dispersion method
JP6058276B2 (ja) * 2012-04-10 2017-01-11 シャープ株式会社 プロペラファン、流体送り装置および成形用金型
WO2014050146A1 (ja) * 2012-09-28 2014-04-03 ダイキン工業株式会社 プロペラファン及びこれを備える空気調和機
WO2015092924A1 (ja) * 2013-12-20 2015-06-25 三菱電機株式会社 軸流送風機
WO2015160850A1 (en) 2014-04-14 2015-10-22 Enevor Inc. Conical impeller and applications thereof
JP6143725B2 (ja) * 2014-10-06 2017-06-07 シャープ株式会社 プロペラファン、流体送り装置および成形用金型
JP5905985B1 (ja) * 2015-08-18 2016-04-20 山洋電気株式会社 軸流送風機及び直列型軸流送風機
JP6068720B2 (ja) * 2016-07-29 2017-01-25 シャープ株式会社 扇風機またはサーキュレータ用プロペラファン、扇風機またはサーキュレータ、および成形用金型
CN106762823A (zh) * 2016-12-28 2017-05-31 东莞市卓奇电子科技有限公司 多流道轴流风聚焦叶轮
CN107013487B (zh) * 2017-05-31 2023-03-24 广东美的制冷设备有限公司 斜流风轮及具有其的空调器
CN108869358B (zh) * 2018-07-09 2023-09-01 广东美的环境电器制造有限公司 风扇
CN110513329B (zh) * 2019-09-30 2024-07-19 广东美的制冷设备有限公司 轴流风轮及具有其的空调器
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FR2723150B1 (fr) * 1994-07-29 1996-09-06 Morin Philippe Pale d'helice de ventilateur

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Publication number Publication date
JP2001090693A (ja) 2001-04-03
CN1297751C (zh) 2007-01-31
JP3743222B2 (ja) 2006-02-08
ES2312316T3 (es) 2009-03-01
MY131508A (en) 2007-08-30
EP1087146A2 (en) 2001-03-28
CN1289897A (zh) 2001-04-04
EP1087146A3 (en) 2002-04-03

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