EP0785362B1 - Cross flow fan impeller - Google Patents

Cross flow fan impeller Download PDF

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Publication number
EP0785362B1
EP0785362B1 EP96307582A EP96307582A EP0785362B1 EP 0785362 B1 EP0785362 B1 EP 0785362B1 EP 96307582 A EP96307582 A EP 96307582A EP 96307582 A EP96307582 A EP 96307582A EP 0785362 B1 EP0785362 B1 EP 0785362B1
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EP
European Patent Office
Prior art keywords
flow fan
cross flow
blades
fan impeller
blade
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
EP96307582A
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German (de)
French (fr)
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EP0785362A1 (en
Inventor
Yoshihashi Makoto
Ootsuta Katsuhisa
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.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP0785362A1 publication Critical patent/EP0785362A1/en
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Publication of EP0785362B1 publication Critical patent/EP0785362B1/en
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    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type

Definitions

  • the present invention relates to a cross flow fan, especially, to a cross flow fan impeller, where rotational noise of the impeller is reduced in a low frequency band of the noise.
  • a plurality of outlet nozzles 7 are provided in a lower front panel of a casing 6, a plurality of inlet ports 8 are provided in an upper front panel of the casing 6, and a heat exchanger 9 is provided behind the inlet ports 8 inside of the casing 6.
  • a cross flow fan impeller 4 is located between a back panel of the casing 6 and the heat exchanger 9 inside of the casing 6. Air is led through the inlet ports 8. The temperature of the air is changed by the heat exchanger 9 to cool or warm. The air is sent to the outlet nozzles 7 by rotation of the cross flow fan impeller 4 and the air is thus blown into the interior of a room through the outlet nozzles 7.
  • the cross flow fan impeller 4 includes a plurality of division plates 3, which are perpendicular to a rotational axis of the impeller, and a plurality of blades 1 as shown in Fig. 8.
  • the blades 1 are provided at periodic intervals between each pair of division plates 3.
  • the impeller 4 makes a noise, which corresponds to a number of blades.
  • the noise corresponding to the number of blades is called the noise "NZ", hereinafter.
  • the blades 1 are provided aperiodically, that is, provided at random intervals. This type of cross flow fan impeller is disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296.
  • DE-A-2 322 734 discloses a cross flow fan with equally spaced blades which have a skew angle.
  • US-A-5 266 007 discloses a cross flow fan in accordance with the pre-characterising part of claim 1.
  • Fig. 9 shows a result of frequency analysis of rotational noise of a known cross flow fan impeller, where the blades are provided periodically.
  • Fig. 10 shows a result of frequency analysis of rotational noise of a known cross flow fan impeller where the blades are provided aperiodically, as disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296.
  • the noise "NZ" can be reduced in the cross flow fan impeller where the blades are provided aperiodically, as disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296.
  • another problem is raised that noise of low frequency, less than 600Hz, is generated as shown in Fig. 10.
  • Fig. 10 is a simulation result of frequency analysis of rotational noise of a cross flow fan impeller, where the blades are provided at random intervals based on the following equation.
  • ⁇ k ⁇ k 0 + d ⁇ ⁇ ( rnd( ⁇ ) - ⁇ /2) where,
  • Fig. 11 shows the locating angle ⁇ k which indicates the location of the k-th blade.
  • An object of the present invention is to provide an improved cross flow fan impeller, whereby the noise "NZ” can be reduced and the noise "N” in the low frequency band (lower than 600 Hz) can be also reduced.
  • a cross flow fan impeller includes a plurality of division plates being perpendicular to a rotational axis of the impeller and a plurality of blades provided between each pair of the plurality of division plates.
  • Fig. 1 shows a first embodiment of a cross flow fan impeller 4 according to the present invention.
  • a plurality of blades 1 including a reference blade 2 and a plurality of division plates 3 are provided in the impeller 4 of the first embodiment.
  • Each of the blades 1 is located with a locating angle ⁇ k away from the reference blade 2 based on the following equation.
  • ⁇ k ⁇ k 0 + ⁇ ⁇ d ⁇ ⁇ Sin( ⁇ ⁇ d ⁇ ⁇ k) where,
  • ⁇ k 0 2 ⁇ ⁇ k/35.
  • the blades 1 are respectively located in positions obtained by the above equation (2).
  • Fig. 12 explains the above equation (2).
  • ⁇ ⁇ d ⁇ ⁇ Sin( ⁇ ⁇ d ⁇ ⁇ k) shows displacement from ⁇ k 0, that is, the locating angle in the case of providing blades at equal intervals.
  • Fig. 2 shows an air conditioner including the cross flow fan impeller 4 of Embodiment 1 of the present invention.
  • a casing 6, an outlet 7, a plurality of inlet ports 8, a heat exchanger 9, and a stabilizer 10 are provided in an internal unit 5 of the air conditioner.
  • Fig. 3 is a sine curve showing the variation location of the blades 1 according to Embodiment 1 of the invention, the points A through D corresponding to the 0° , 90° , 180° , and 270° positions, as indicated in Fig. 1.
  • the location of the blades 1 is varied cyclically.
  • the noise "NZ” is modulated as shown in Fig. 4. A peak level of the noise “NZ” is dispersed and the noise level is thus decreased.
  • the noise level of the noise "N” generated by the impeller itself is decreased because there is still correlation among the blades.
  • ⁇ the cyclic coefficient
  • NZ the noise "NZ" is further modulated and it is effective to locate the plurality of blades cyclically.
  • ⁇ the cyclic coefficient
  • ⁇ the locating angle displacement coefficient
  • each location of the plurality of blades is determined by the equation (2) as in Embodiment 1, and the locating angle ⁇ k further includes a skew angle ⁇ ' as shown in Fig. 5. It is well-known that providing each blade with the skew angle ⁇ ' reduces the noise "NZ". To the configuration of Embodiment 1, the above feature is added, that is, each blade is provided with the skew angle ⁇ '. The noise "NZ" is reduced further more than the cross flow fan impeller only including the feature of Embodiment 1.
  • the cyclic coefficient ⁇ is a natural number greater than 2 in the cross flow fan impeller of Embodiment 5.
  • the noise "NZ" is further modulated and it is effective to locate the plurality of blades cyclically.
  • the cyclic coefficient ⁇ is a natural even number greater than 2 in the cross flow fan impeller of Embodiment 5.
  • the impeller is thus well-balanced mechanically.
  • the locating angle displacement coefficient ⁇ is a rational number and 0 ⁇ 1 in the cross flow fan impeller of Embodiment 5. Accordingly, the interval between each pair of adjacent blades does not become the same and none of the plurality of blades touches the next blade.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

  • The present invention relates to a cross flow fan, especially, to a cross flow fan impeller, where rotational noise of the impeller is reduced in a low frequency band of the noise.
    • Description of the Related Art
  • Referring to Fig. 7, in an internal unit 5 of a known air conditioner, a plurality of outlet nozzles 7 are provided in a lower front panel of a casing 6, a plurality of inlet ports 8 are provided in an upper front panel of the casing 6, and a heat exchanger 9 is provided behind the inlet ports 8 inside of the casing 6. A cross flow fan impeller 4 is located between a back panel of the casing 6 and the heat exchanger 9 inside of the casing 6. Air is led through the inlet ports 8. The temperature of the air is changed by the heat exchanger 9 to cool or warm. The air is sent to the outlet nozzles 7 by rotation of the cross flow fan impeller 4 and the air is thus blown into the interior of a room through the outlet nozzles 7.
  • The cross flow fan impeller 4 includes a plurality of division plates 3, which are perpendicular to a rotational axis of the impeller, and a plurality of blades 1 as shown in Fig. 8. The blades 1 are provided at periodic intervals between each pair of division plates 3. As the cross flow fan impeller rotates, the impeller 4 makes a noise, which corresponds to a number of blades. The noise corresponding to the number of blades is called the noise "NZ", hereinafter. To reduce this noise, in another known cross flow fan impeller, for example, the blades 1 are provided aperiodically, that is, provided at random intervals. This type of cross flow fan impeller is disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296.
  • DE-A-2 322 734 discloses a cross flow fan with equally spaced blades which have a skew angle.
  • US-A-5 266 007 discloses a cross flow fan in accordance with the pre-characterising part of claim 1.
    • Problems
  • Fig. 9 shows a result of frequency analysis of rotational noise of a known cross flow fan impeller, where the blades are provided periodically. Fig. 10 shows a result of frequency analysis of rotational noise of a known cross flow fan impeller where the blades are provided aperiodically, as disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296. In Fig. 10, the noise "NZ" can be reduced in the cross flow fan impeller where the blades are provided aperiodically, as disclosed in Japanese Unexamined Patent Publication No. SHO 60-17296. However, another problem is raised that noise of low frequency, less than 600Hz, is generated as shown in Fig. 10.
  • Fig. 10 is a simulation result of frequency analysis of rotational noise of a cross flow fan impeller, where the blades are provided at random intervals based on the following equation. k = k0 + d × ( rnd(δ) - δ/2)    where,
    • k:
    the locating angle of the k-th blade
    k0:
    the locating angle of the k-th blade if the blades were provided at equal intervals
    d:
    the angle between each pair of adjacent blades if the blades were provided at equal intervals
    rnd():
    random number generation function
    δ:
    a distortion coefficient
    k:
    the ordinal number of each blade, assigning 0 to the reference blade.
  • Fig. 11 shows the locating angle k which indicates the location of the k-th blade.
  • When the blades 1 of the cross flow fan impeller pass near a stabilizer 10, noise is caused because of pressure fluctuation generated by the blades 1. The higher the distortion coefficient δ becomes, the more the noise "NZ" is reduced because correlation of the noise "NZ" among the blades 1 becomes less. On the other hand, rotational noise of the impeller generated by itself (this rotational noise is called the noise "N", hereinafter) becomes high especially in a low frequency band.
    • SUMMARY OF THE INVENTION
  • An object of the present invention is to provide an improved cross flow fan impeller, whereby the noise "NZ" can be reduced and the noise "N" in the low frequency band (lower than 600 Hz) can be also reduced.
  • According to the present invention, a cross flow fan impeller includes a plurality of division plates being perpendicular to a rotational axis of the impeller and a plurality of blades provided between each pair of the plurality of division plates. In the cross flow fan impeller of the invention, the blades are provided at intervals varied cyclically and each location of the blades is determined based on the following equation: k =  k 0 + α · d · Sin(β · d · k)    where,
    • k:
    the locating angle of the k-th blade
    k0:
    the locating angle of the k-th blade if the blades were provided at equal intervals
    α:
    a locating angle displacement coefficient
    d:
    the angle between each pair of adjacent blades if the blades were provided at equal intervals
    β:
    a cyclic coefficient
    k:
    the ordinal number of each blade, assigning 0 to the reference blade.
    Brief Explanation of the Drawings
  • A more complete appreciation of the present invention and many of the attendant advantages thereof will be readily obtained as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:
  • Fig. 1 is a sectional diagram of a cross flow fan impeller according to a first embodiment of the invention;
  • Fig. 2 is a sectional diagram of an air conditioner including the cross flow fan impeller of the first embodiment;
  • Fig. 3 is a sign curve representing the variation of the location of the blades of the cross flow fan impeller of the first embodiment;
  • Fig. 4 shows a result of frequency analysis of noise generated in the cross flow fan impeller of the first embodiment;
  • Fig. 5 diagrammatically shows a skew angle of blades of a cross flow fan impeller of a fifth embodiment;
  • Fig. 6 shows a result of frequency analysis of a rotational noise generated in the cross flow fan impeller of the fifth embodiment;
  • Fig. 7 shows a sectional diagram of an internal unit of air conditioner according to the prior art;
  • Fig. 8 shows a cross flow fan impeller according to the prior art;
  • Fig. 9 shows a result of frequency analysis of rotational noise generated in a prior art cross flow fan impeller, where the blades are provided periodically;
  • Fig. 10 shows a result of frequency analysis of a rotational noise generated in another prior art cross flow fan impeller, where the blades are provided aperiodically;
  • Fig. 11 is a diagram which shows the locating angle k which indicates the location of the k-th blade in a cross flow fan impeller according to the prior art; and
  • Fig. 12 is a diagram which explains the locating angle k of the k-th blade in a cross flow fan impeller according to the present invention.
    • DESCRIPTION OF PREFERRED EMBODIMENTS Embodiment 1.
  • Fig. 1 shows a first embodiment of a cross flow fan impeller 4 according to the present invention. Referring to Fig. 1, a plurality of blades 1 (including a reference blade 2) and a plurality of division plates 3 are provided in the impeller 4 of the first embodiment. Each of the blades 1 is located with a locating angle k away from the reference blade 2 based on the following equation. k =  k 0 + α · d · Sin(β · d · k)    where,
    • k:
    the locating angle of the k-th blade
    k0:
    the locating angle of the k-th blade if the blades were provided at equal intervals
    α:
    a locating angle displacement coefficient
    d:
    the angle between each pair of adjacent blades if the blades were provided at equal intervals
    β:
    a cyclic coefficient
    k:
    the ordinal number of each blade, assigning 0 to the reference blade.
  • In the cross flow fan impeller 4 of this embodiment, the total number of blades = 35, the locating angle displacement coefficient α = 0.2, the cyclic coefficient β = 2, and the angle between each pair of blades if the blades were provided at equal intervals d = 2π/35. In this case, k0 = 2π × k/35. The blades 1 are respectively located in positions obtained by the above equation (2).
  • Fig. 12 explains the above equation (2). Based on the equation (2), for example, when k = 2, a location angle 2 is obtained as follows: 2 = 20 + α · d · Sin(β · d · 2) = 2π × 2/35 + 0.2 · 2π/35 · Sin {2 · (2π/35) · 2}
  • As shown in Fig. 12, the second element of the above equation (3), α · d · Sin(β · d · k) shows displacement from k0, that is, the locating angle in the case of providing blades at equal intervals. The maximum value of Sin(β · d · k) is ±1 and the maximum value of the displacement is thus ±α · d. If α = 1.0, some of the blades touches the next blade. If α = 0, all the blades are located at the same intervals.
  • Fig. 2 shows an air conditioner including the cross flow fan impeller 4 of Embodiment 1 of the present invention. Referring to Fig. 2, a casing 6, an outlet 7, a plurality of inlet ports 8, a heat exchanger 9, and a stabilizer 10 are provided in an internal unit 5 of the air conditioner. Fig. 3 is a sine curve showing the variation location of the blades 1 according to Embodiment 1 of the invention, the points A through D corresponding to the 0° , 90° , 180° , and 270° positions, as indicated in Fig. 1.
  • In the cross flow fan impeller, the location of the blades 1 is varied cyclically. The noise "NZ" is modulated as shown in Fig. 4. A peak level of the noise "NZ" is dispersed and the noise level is thus decreased. On the other hand, the noise level of the noise "N" generated by the impeller itself is decreased because there is still correlation among the blades.
    • Embodiment 2.
  • As a second embodiment of the present invention, a modification of the cross flow fan impeller of the first embodiment is provided, where β, the cyclic coefficient, is a natural number greater than 2. The noise "NZ" is further modulated and it is effective to locate the plurality of blades cyclically.
    • Embodiment 3.
  • As a third embodiment of the present invention, a modification of the cross flow fan impeller of the first embodiment is provided, where β, the cyclic coefficient, is a natural even number greater than 2. The impeller is thus well-balanced mechanically.
    • Embodiment 4.
  • As a fourth embodiment of the present invention, a modification of the cross flow fan impeller of the first embodiment is provided, where α, the locating angle displacement coefficient, is a rational number and 0<α<1. Accordingly, the interval between each pair of adjacent blades does not become the same and none of the blades touches the next blade.
    • Embodiment 5.
  • According to a fifth embodiment of the invention, each location of the plurality of blades is determined by the equation (2) as in Embodiment 1, and the locating angle k further includes a skew angle ' as shown in Fig. 5. It is well-known that providing each blade with the skew angle ' reduces the noise "NZ". To the configuration of Embodiment 1, the above feature is added, that is, each blade is provided with the skew angle '. The noise "NZ" is reduced further more than the cross flow fan impeller only including the feature of Embodiment 1.
    • Embodiment 6.
  • According to a sixth embodiment of the invention, the cyclic coefficient β is a natural number greater than 2 in the cross flow fan impeller of Embodiment 5. As a result, the noise "NZ" is further modulated and it is effective to locate the plurality of blades cyclically.
    • Embodiment 7.
  • According to a seventh embodiment of the invention, the cyclic coefficient β is a natural even number greater than 2 in the cross flow fan impeller of Embodiment 5. The impeller is thus well-balanced mechanically.
    • Embodiment 8.
  • According to an eighth embodiment of the invention, the locating angle displacement coefficient α is a rational number and 0<α<1 in the cross flow fan impeller of Embodiment 5. Accordingly, the interval between each pair of adjacent blades does not become the same and none of the plurality of blades touches the next blade.
  • Having thus described several particular embodiments of the present invention, various alterations, modifications, and improvements will readily occur to those skilled in the art. Such alterations, modifications, and improvements are intended to be part of this disclosure, and are intended to be within the scope of the present invention. Accordingly, the foregoing description is by way of example only, and is not intended to be limiting. The present invention is limited only as defined in the following claims and the equivalents thereto.

Claims (8)

  1. A cross flow fan impeller (4), comprising:
    a plurality of division plates (3) perpendicular to a rotational axis of the impeller; and
    a plurality of blades (1) provided between each pair of division plates;
       wherein the blades are respectively located at intervals varied cyclically;
       characterised in that
    the blades are located in accordance with the following equation: k = k0 + α · d · Sin(β · d · k)    where,
    k:
    the locating angle of the k-th blade
    k0:
    the locating angle of the k-th blade if the blades were provided at equal intervals
    α:
    a locating angle displacement coefficient
    d:
    the angle between each pair of adjacent blades if the blades were provided at equal intervals
    β:
    a cyclic coefficient
    k:
    the ordinal number of each blade, assigning 0 to a reference blade (2).
  2. The cross flow fan impeller of claim 1, wherein β is a natural number greater than 2.
  3. The cross flow fan impeller of claim 1, wherein β is a natural even number greater than 2.
  4. The cross flow fan impeller of claim 1, wherein α is a rational number and 0<α<1.
  5. The cross flow fan impeller of claim 1, wherein the blades have a skew angle.
  6. The cross flow fan impeller of claim 5, wherein β is a natural number greater than 2.
  7. The cross flow fan impeller of claim 5, wherein β is a natural even number greater than 2.
  8. The cross flow fan impeller of claim 5, wherein α is a rational number and 0<α<1.
EP96307582A 1996-01-18 1996-10-18 Cross flow fan impeller Expired - Lifetime EP0785362B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP644796 1996-01-18
JP00644796A JP3484854B2 (en) 1996-01-18 1996-01-18 Once-through fan
JP6447/96 1996-01-18

Publications (2)

Publication Number Publication Date
EP0785362A1 EP0785362A1 (en) 1997-07-23
EP0785362B1 true EP0785362B1 (en) 2002-12-11

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EP96307582A Expired - Lifetime EP0785362B1 (en) 1996-01-18 1996-10-18 Cross flow fan impeller

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EP (1) EP0785362B1 (en)
JP (1) JP3484854B2 (en)
KR (1) KR100216104B1 (en)
CN (1) CN1076448C (en)
AU (1) AU680173B1 (en)
DE (1) DE69625322T2 (en)
ES (1) ES2191080T3 (en)
HK (1) HK1000496A1 (en)

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JP6601994B2 (en) * 2013-09-06 2019-11-06 日立ジョンソンコントロールズ空調株式会社 Indoor unit of air conditioner and air conditioner using the same
JP5804044B2 (en) 2013-12-27 2015-11-04 ダイキン工業株式会社 Multi-wing fan
CN104132004B (en) * 2014-08-04 2016-08-24 绿田机械股份有限公司 A kind of cooling fan of use for diesel engine
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CN105020176A (en) * 2015-08-20 2015-11-04 珠海格力电器股份有限公司 Fan blade and centrifugal ventilator
CN106837859B (en) * 2017-02-13 2019-11-29 美的集团股份有限公司 Draught fan impeller and centrifugal blower
CN110206753B (en) * 2018-06-29 2024-07-09 华帝股份有限公司 Centrifugal wind wheel for range hood
CN108916078A (en) * 2018-07-16 2018-11-30 大连碧蓝节能环保科技有限公司 Helical blade centrifugal blower
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Publication number Publication date
KR970059509A (en) 1997-08-12
HK1000496A1 (en) 2003-04-25
KR100216104B1 (en) 1999-08-16
JPH09195979A (en) 1997-07-29
CN1164619A (en) 1997-11-12
ES2191080T3 (en) 2003-09-01
EP0785362A1 (en) 1997-07-23
JP3484854B2 (en) 2004-01-06
DE69625322T2 (en) 2003-10-16
DE69625322D1 (en) 2003-01-23
CN1076448C (en) 2001-12-19
AU680173B1 (en) 1997-07-17

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