EP0947708B1 - Ventilateur à courant transversal et climatiseur l'utilisant - Google Patents

Ventilateur à courant transversal et climatiseur l'utilisant Download PDF

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Publication number
EP0947708B1
EP0947708B1 EP99106442A EP99106442A EP0947708B1 EP 0947708 B1 EP0947708 B1 EP 0947708B1 EP 99106442 A EP99106442 A EP 99106442A EP 99106442 A EP99106442 A EP 99106442A EP 0947708 B1 EP0947708 B1 EP 0947708B1
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EP
European Patent Office
Prior art keywords
cross
flow fan
air
vanes
disposed
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
EP99106442A
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German (de)
English (en)
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EP0947708A3 (fr
EP0947708A2 (fr
Inventor
Noriyuki Nabeshima
Tomohito Takada
Michihiro Kurokawa
Tomohito Koizumi
Yoshinori Toya
Kiyoshi Koyama
Shigeya Ishigaki
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.)
Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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Publication date
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Publication of EP0947708A2 publication Critical patent/EP0947708A2/fr
Publication of EP0947708A3 publication Critical patent/EP0947708A3/fr
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Publication of EP0947708B1 publication Critical patent/EP0947708B1/fr
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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
    • F04D29/28—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • 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

Definitions

  • This invention relates to a cross-flow fan wherein a plurality of vanes are cylindrically disposed around the axis of rotation and an air-conditioner using it.
  • a cross-flow fan In conventional air-conditioners, wherein air in a room is conditioned by circulating it in the room via a heat exchanger, a cross-flow fan has been used, wherein the air being circulated flows across the fan (e.g. US-A-5 266 007).
  • Fig. 6 The structure of a room unit for such an air-conditioner equipped with a cross-flow fan is shown in Fig. 6.
  • Fig. 6 is used here, because its overall structure is substantially the same as that of the prior-art device, although it refers to an embodiment of this invention. It is a cross section of the room unit, wherein inlets 1a and 7a are provided in upper and front covers of a case 1 of the body of the unit, respectively, and wherein an outlet 1b is provided in a bottom portion of the body case 1.
  • An air filter 6, a heat exchanger 2, and a cross-flow fan 3 are disposed sequentially in that order in a flow path 5 connecting the inlet 1a and the outlet 1b.
  • Fig. 7 is a perspective of the cross-flow fan 3. As shown in it, a plurality of supporting disks 3b are disposed on a shaft 3c at given intervals therebetween, and also a plurality of vanes 3a are disposed on the peripheries of the supporting disks 3b.
  • Such a cross-flow fan 3 is driven by an electric motor (not shown).
  • the cross-flow fan 3 is disposed such that it is sandwiched between a rear-guider 1c and a stabilizer 4 so as to enhance the efficiency of the blowing air.
  • a tong-shaped surface 4a is formed at the end of the stabilizer 4.
  • These noises consist of first-order rotary sounds associated with intervals between adjacent vanes.
  • the frequencies of the first-order rotary sounds are defined by NxZ, where N is the number of rotations per second and Z is the number of vanes 3a.
  • adjacent vanes 3a be disposed along the peripheries of the disks, with their intervals therebetween being at random, to reduce the noises of the first-order rotary sounds.
  • vanes 3a being disposed at random intervals therebetween when vanes having low absorbing ability (adjacent vanes disposed at short intervals) exist at both the inlet and outlet sides, the flow of the air from the fan was reduced, and that conversely, when vanes with high absorbing ability exist at both the inlet and outlet sides, the reverse phenomenon was brought about.
  • the parties concerned include the applicant, experimentally certified that a problem was observed when the noise level increased and there existed discontinuous variations thereof in a frequency area at around 8N, and listeners perceived an unpleasant hearing impression.
  • the purpose of this invention is to provide a cross-flow fan and an air-conditioner using it, wherein to realize a cross-flow fan with a low noise level the intensity and variations of the noise level at around 8N on the low-frequency side, as well as the noise level caused by first-order rotary sounds, are reduced, without any unpleasant impression being given to listeners.
  • This invention provides a cross-flow fan, wherein a plurality of supporting disks are disposed on a shaft in an axial direction at given intervals therebetween, and wherein a number of vanes are disposed around the supporting disks, characterized in that angular intervals for arranging the vanes, at which angular intervals the vanes are arranged along the peripheries of the supporting disks, are determined by a logistic representation.
  • the effect of this invention will not be impaired, so long as it is within a range wherein the error ⁇ P(n) meets the following equation 4: -1.0 ⁇ ⁇ P ( n ) ⁇ 1.0
  • the angular interval P(n) of any vane for example, the Bth angular interval P(B), can be adjusted so that the total of the angular intervals P(n) of all vanes becomes 360 degrees.
  • the angular intervals, other than that of the angular-adjusted angular interval P(B), are determined by logistic representations.
  • each of the angular intervals P(n) can be adjusted to each of the angular intervals P ' (n), as determined by the following equation 5, respectively:
  • vanes are sequentially arranged so that their concave or front surfaces face the rotary direction of the cross-flow fan, at angular intervals determined by logistic representations.
  • a rear guider, a discharge outlet, and a stabilizer are sequentially disposed in the direction of rotation of the cross-flow fan.
  • the cross-flow fan is arranged so that its lowest point is positioned higher than that of the heat exchanger.
  • FIG. 1 is a front view showing an embodiment of the cross-flow fan of this invention
  • Fig. 2 is a cross section cut along the line shown by the arrows A-A of Fig. 1
  • Fig. 3 is an enlarged cross section of a vane of Fig. 1.
  • a plurality of supporting disks 13 are disposed substantially equidistantly along a rotary shaft 14 of the cross-flow fan 11.
  • a plurality of vanes 12 are disposed around the peripheries of the supporting disks 13 so as to surround the shaft 14.
  • a motor (not shown) is connected to one end 14a of the shaft 14 such that the shaft 14 is rotated in a direction ⁇ as shown by the arrow.
  • the approximate dimensions of an embodiment of the cross-flow fan 11 are as follows: the radius of the fan D4 is 88 mm and its axial length L2 is 600 mm.
  • Each fan 12 extends along the rotary shaft 14 and forms a so-called skew such that the end on the side to be driven advances more in the direction of rotation ⁇ than the end on the side to drive.
  • an angle of twist ⁇ formed over the shaft by the vane 12 with the shaft, is set at 43 degrees.
  • Fig. 3 shows a cross section, in a direction of its shorter side, of the vane 12.
  • the vane 12 is formed into a circular arc and is mounted on the supporting disk 13 so that its concave surface faces the direction of rotation ⁇ .
  • the dimensions of the vane 12 are as follows: the length of an arc L is 11.7 mm, the radius of the back side of an arc R1 is 9 mm, the radius of the front side of an arc R2 is 10 mm, and the radius at the end of an arc between its front and back sides R3 is 0.44 mm.
  • Angular intervals between adjacent vanes 12 in a peripheral direction are determined based on chaos logic or theory. That is, when the total number of vanes 12 is assumed to be B, and when an angle formed between the nth and (n+1)th vanes 12 centered around the rotary shaft 14 is assumed to be P(n), chaotic progression or pseudorandom numbers corresponding to each vane 12 is found based on a logistic function defined by equation 2, and then angles or pitches are determined per equation 3 by using the chaotic progression. Further, the total number B of the vanes 12 is assumed to be 35.
  • P ( n ) a + b ⁇ X ( n )
  • a is constants ranging from 297/B to 333/B
  • b is also constants ranging from 2.0 to 3.0
  • P(1) is an angular interval formed by the 1st vane 12 with the Bth vane 12.
  • the cross-flow fan 11 is formed such that each vane 12, whose an angular interval has thus been determined, is sequentially disposed in the direction of rotation ⁇ .
  • the sum of the angular intervals P(1) - P(35) of all the vanes 12 does not always total 360 degrees, the sum may be made to total 360 degrees by adjusting, for example, the angular interval P(35) of the last vane 12.
  • Table 1 lists the values of the angular intervals of each vane 12. They have been determined in the manner stated above. Nos. of vanes n Ang. int. P (n) deg. Nos. of vanes n Ang. int. P (n) deg. 1 9.30 19 9.63 2 9.95 20 10.83 3 11.35 21 11.10 4 9.77 22 10.53 5 11.10 23 11.47 6 10.51 24 9.37 7 11.48 25 10.15 8 9.33 26 11.52 9 10.05 27 9.18 10 11.45 28 9.56 11 9.42 29 10.67 12 10.31 30 11.33 13 9.05 31 9.85 14 9.05 32 11.23 15 9.06 33 10.17 16 9.09 34 11.52 17 9.20 35 10.84 18 9.63
  • the thus-constituted cross-flow fan 11 is mounted on a indoor unit shown in Fig. 6.
  • An air-conditioner to which this indoor unit is applied comprises a compressor to compress a heat medium, a decompressor to decompress or squeeze the heat medium, a condenser to condense the heat medium, and an evaporator to evaporate the heat medium.
  • a room is cooled such that a heat exchanger 2 is disposed in the indoor unit. It functions as an evaporator to exchange heat between the heat medium and the air that is in the room and that is circulating through the heat exchanger 2, such that the heat medium evaporates by receiving the heat of evaporation from the room air.
  • the room air is in turn cooled by being taken away the heat of evaporation to cool the room.
  • a room is warmed such that a heat exchanger 2, disposed in the indoor unit, functions as a condenser to exchange heat between the heat medium and the air in the room that is circulating through the heat exchanger 2, and such that the heat medium condenses by being taken away the heat of condensation through the room air.
  • the room air is in turn warmed by receiving the heat of condensation to warm the room.
  • heat exchanger 2 it is also possible to exchange heat between warm or cool water circulating through the heat exchanger 2 as a heat medium and the air in a room. In this case, warming and cooling operations are carried out by the radiation or absorption of heat in the heat exchanger 2.
  • inlets 1a and 7a provided in upper and front covers of a case 1 of the body of the unit, and an outlet 1b, provided in a bottom portion of the body case 1, define a flow path 5.
  • an air filter 6, a heat exchanger 2, and a cross-flow fan 11 are disposed sequentially, starting from the windward side.
  • the cross-flow fan 11 is driven by an electric motor (not shown), and structured such that it is sandwiched between a rear-guider 1c and a stabilizer 4 equipped with a tong-shaped surface 4a at an end thereof so as to enhance the efficiency in blowing the air.
  • the rear-guider 1c may be replaced by a rib functioning as a rectifier.
  • a drain pan 2a (a pan for receiving water) is formed at the lower end of the stabilizer 4 for receiving water flowing down from the heat exchanger 2 to remove frost.
  • cross-flow fan is appropriately arranged so that its lowest point is positioned higher than that of the heat exchanger.
  • the present invention was compared with the conventional one, wherein the angular intervals of each vane 12 were appropriately set at random to reduce first-order rotary sounds (NZ sounds), so as to support the effects of this invention.
  • Fig. 4 shows angular intervals of cross-flow fans 11 in accordance with the structures of both a conventional fan and this invention.
  • the abscissa axis of Fig. 4 shows the number of each vane 12, ranging from 1 to 35, and the coordinate axis shows angular intervals P(n), corresponding to each vane 12.
  • Fig. 5 shows the results of noise experiments when the cross-flow fans 11, whose angular intervals have been set as shown in Fig. 4, are rotated at a speed of 1360 rpm.
  • the abscissa axis of Fig. 5 shows frequencies (Hz) of noises, and the coordinate axis shows noise levels (dB).
  • the noise levels at the frequencies of rotary first-order sounds NZ (793 Hz) are 24dB and 27dB for the conventional fan and this invention, respectively.
  • this invention shows a noise level higher than that of the conventional device, there is little difference therebetween.
  • the mark X in Fig. 5, which indicates a value of 29 dB, shows the result of rotary first-order sounds when the angular interval or pitch of each vane 12 is constant.
  • the result of an experiment shows that the noise levels for this invention are considerably lower than those of the conventional fan, and that little variation of noise levels is observed in the range of frequencies around that frequency.
  • the structure of this invention allows a reduction in both the noise levels caused by rotary first-order sounds and the intensity and variation of noise levels at around 8N on the lower frequency side.
  • noises at around 8N on the lower frequency side will not give an unpleasant impression to listeners, such as was experienced in using the conventional fan.
  • an eddy is produced at the root of the tongue-shaped surface 4a by a flow of air passing through the lower part of the heat exchanger 2. If such an eddy is synchronized with another eddy that is generated when the eddy produced at the root of the tongue surface is discharged from the cross-flow fan 11 and impinges on the tongue surface, noises increase.
  • the flow-cross fan 11 in accordance with the structure of this invention, allows noise components to be dispersed in a wider frequency band, to prevent noise levels from considerably increasing in a certain frequency area.
  • the total angular interval of 360 degrees is achieved by adjusting the last interval P(35).
  • the vane 12 can be adjusted to any other interval.
  • each of the above-mentioned angular intervals P(n) can be adjusted respectively to each of angular intervals P'(n), as determined by the following equation 5:
  • all the vanes 12 can be arranged in a well-balanced way, with angular intervals determined by the logistic representation.
  • the method of manufacturing the cross-flow fan 11, is not limited to the method of combining one of the vane 12 with a plurality of supporting disks 13. Any other method can also be used, wherein a plurality of vanes 12 are mounted on the peripheries of a single supporting disk 13, and the resulting assemblies are stacked sequentially or may be formed into one unit (or divided into a plurality of units) by using plastics.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Claims (9)

  1. Ventilateur à écoulement transversal dans lequel une pluralité de disques supports (13) sont disposés sur un arbre (14) dans une direction axiale à intervalles donnés entre eux, et dans lequel un certain nombre (B) d'aubes (12) sont disposées dans une direction périphérique par rapport auxdits disques supports,
       caractérisé en ce que lesdites aubes (12) en un certain nombre sont disposées suivant des intervalles angulaires et en ce que l'intervalle angulaire de l'aube n est déterminé par l'équation (1) suivante, en utilisant une fonction logistique X(n) déduite de l'équation (2) suivante : P(n) = a + b * X(n) X(n + 1) = 4 * (1 - X(n)) * X(n)    dans laquelle n est un entier de 1 à B, a est une constante de 297/B à 333/B, b est une constante de 2,0 à 3,0 et P(1) est un intervalle angulaire formé par la première aube (12) avec la Bème aube (12).
  2. Ventilateur à écoulement transversal selon la revendication 1, dans lequel l'intervalle angulaire P(n) d'une aube quelconque choisie de manière arbitraire est ajusté de telle sorte que le total des intervalles angulaires P(1) à P(B) de toutes les aubes devienne égal à 360 degrés.
  3. Ventilateur à écoulement transversal selon la revendication 2, dans lequel l'intervalle angulaire P(B) de la Bème aube est ajusté.
  4. Ventilateur à écoulement transversal selon la revendication 1, dans lequel chacun des intervalles angulaires P(n) est ajusté respectivement afin d'obtenir l'intervalle angulaire de contrepartie de P'(n) déterminé par l'équation 5 suivante:
    Figure 00200001
  5. Ventilateur à écoulement transversal selon l'une quelconque des revendications 1 à 4, dans lequel lesdites aubes en un certain nombre sont disposées de manière séquentielle dans la direction de rotation du ventilateur à écoulement transversal, à intervalles réguliers comme cela est déterminé par les représentations logistiques.
  6. Ventilateur à écoulement transversal selon l'une quelconque des revendications 2 à 5, dans lequel des erreurs de fabrication δP(n) lors de la fabrication de l'intervalle angulaire P(n) de la nème aube sont formées de manière à satisfaire l'équation 4 suivante : - 1,0 ≤ δP(n) ≤ 1,0
  7. Conditionneur d'air dans lequel une entrée d'air, un échangeur thermique, un ventilateur à écoulement transversal et une sortie sont disposés successivement en commençant à partir du côté au vent, dans lequel le ventilateur à écoulement transversal fait circuler, à travers l'échangeur thermique, l'air dans une pièce à conditionner, de manière à conditionner l'air de la pièce par échange thermique entre un fluide thermique circulant à travers l'échangeur thermique et l'air, caractérisé en ce que ledit ventilateur à écoulement transversal est l'un quelconque des ventilateurs à écoulement transversal des revendications 1 à 6.
  8. Conditionneur d'air selon la revendication 7, dans lequel ledit ventilateur à écoulement transversal est intercalé entre un guide arrière et un stabilisateur et dans lequel ledit guide arrière, la sortie et le stabilisateur sont disposés successivement dans le même sens que le sens de rotation dudit ventilateur à écoulement transversal.
  9. Conditionneur d'air selon la revendication 7 ou 8, dans lequel ledit ventilateur à écoulement transversal est disposé de telle sorte que son point le plus bas est positionné à une hauteur supérieure à celle dudit échangeur thermique.
EP99106442A 1998-03-30 1999-03-29 Ventilateur à courant transversal et climatiseur l'utilisant Expired - Lifetime EP0947708B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP8327898 1998-03-30
JP8327898 1998-03-30

Publications (3)

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EP0947708A2 EP0947708A2 (fr) 1999-10-06
EP0947708A3 EP0947708A3 (fr) 2001-03-07
EP0947708B1 true EP0947708B1 (fr) 2005-02-02

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KR (1) KR100545985B1 (fr)
DE (1) DE69923490T2 (fr)
TW (1) TW377393B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110857701A (zh) * 2018-08-23 2020-03-03 广东威灵电机制造有限公司 叶轮的叶片布置方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1119082A3 (fr) * 2000-01-18 2004-05-26 Ushiodenki Kabushiki Kaisha Ventilateur à courant transversal pour un laser à gaz excité par décharge
CN112797483B (zh) * 2021-02-10 2021-12-07 珠海格力电器股份有限公司 一种空调器室内机送风控制方法、控制系统及其空调器
CN114060302B (zh) * 2021-10-09 2023-06-02 佛山市顺德区美的电子科技有限公司 双贯流风机的控制方法、装置、双贯流风机及介质

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5266007A (en) * 1993-03-01 1993-11-30 Carrier Corporation Impeller for transverse fan
DE4421604C1 (de) * 1994-06-21 1995-04-13 Siemens Ag Seitenkanalverdichter
JP3484854B2 (ja) * 1996-01-18 2004-01-06 三菱電機株式会社 貫流送風羽根車
US5681145A (en) * 1996-10-30 1997-10-28 Itt Automotive Electrical Systems, Inc. Low-noise, high-efficiency fan assembly combining unequal blade spacing angles and unequal blade setting angles

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110857701A (zh) * 2018-08-23 2020-03-03 广东威灵电机制造有限公司 叶轮的叶片布置方法

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Publication number Publication date
KR100545985B1 (ko) 2006-01-25
EP0947708A3 (fr) 2001-03-07
DE69923490T2 (de) 2006-02-16
KR19990078295A (ko) 1999-10-25
TW377393B (en) 1999-12-21
EP0947708A2 (fr) 1999-10-06
DE69923490D1 (de) 2005-03-10

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