EP0602007B1 - Soufflante et diffuseur d'aspirateur - Google Patents

Soufflante et diffuseur d'aspirateur Download PDF

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Publication number
EP0602007B1
EP0602007B1 EP94101775A EP94101775A EP0602007B1 EP 0602007 B1 EP0602007 B1 EP 0602007B1 EP 94101775 A EP94101775 A EP 94101775A EP 94101775 A EP94101775 A EP 94101775A EP 0602007 B1 EP0602007 B1 EP 0602007B1
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EP
European Patent Office
Prior art keywords
diffuser
impeller
vanes
vacuum cleaner
vane
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
EP94101775A
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German (de)
English (en)
Other versions
EP0602007A2 (fr
EP0602007A3 (fr
Inventor
Yukiji Iwase
Shigenori Sato
Masao Sunagawa
Hisanori Toyoshima
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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Publication date
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Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0602007A2 publication Critical patent/EP0602007A2/fr
Publication of EP0602007A3 publication Critical patent/EP0602007A3/fr
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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L5/00—Structural features of suction cleaners
    • A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
    • A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L9/00—Details or accessories of suction cleaners, e.g. mechanical means for controlling the suction or for effecting pulsating action; Storing devices specially adapted to suction cleaners or parts thereof; Carrying-vehicles specially adapted for suction cleaners
    • A47L9/02—Nozzles
    • A47L9/08—Nozzles with means adapted for blowing

Definitions

  • This invention relates to vacuum cleaners and particularly to impellers and diffusers in vacuum cleaners.
  • the specific speed of the electric blower for use in the vacuum cleaner is low (a small flow rate is provided in spite of a high pressure with respect to a relative rotational speed) and generally, the outlet width of the impeller is designed to be small; therefore, since the friction loss within the impeller becomes large as the outlet width of the impeller is decreased, the width and outlet angle of the vanes are made comparatively large. Accordingly, in the electric blower for use in a household vacuum cleaner, the outlet absolute flow angle of the impeller is designed to be about 6°, and the inlet angle of the diffuser is set to as large as 5° in practice.
  • the object of the present invention is at least partly to avoid the disadvantages described above, and to improve the air flow efficiency through the blower of a vacuum cleaner.
  • the present invention is set out in claim 1.
  • Embodiments of impellers and vacuum cleaner blowers of the invention will now be described. They may be fitted in conventional vacuum cleaners. Examples of vacuum cleaners in which they may be mounted are shown in European Patent Applications EP-A-0 453 163 and EP-A-0 453 296.
  • the electric vacuum cleaner blower shown in Figs. 1 and 2 is composed of a blower portion 80 and a motor portion 81. Disposed inside a housing 81a of the motor portion 81 are a rotor 83 secured to a rotating shaft 82 and a stator 85 including coils 84a and 84b.
  • the housing 81a has a bearing-retaining portion 81b formed at the centre of its end wall, and a bearing 86a for rotatably supporting one end of the rotating shaft 82 is disposed in the bearing-retaining portion 81b.
  • the housing 81a also has exhaust ports 81c in its peripheral surface.
  • the housing 81a has an end bracket 87 at the opposite end, and this end bracket 87 connects the blower portion 80 and the motor 81 together.
  • the end bracket 87 has a bearing retaining portion 87a at its centre and a flat portion 87b around its circumference.
  • the flat portion 87b is formed with suction ports 88 through which the air from the blower 80 is sent into the motor 81 to cool it.
  • Disposed in the bearing-retaining portion 87a is a bearing 86b for rotatably supporting the other end of the rotating shaft 82.
  • the end bracket 87 carries a diffuser 89, and on the upstream side of the diffuser, a centrifugal impeller 90 is secured to the rotating shaft 82 by means of a nut 91.
  • the centrifugal impeller 90 and the diffuser 89 are covered by a blower casing 92 pressure-fitted to the circumference of the end bracket 87.
  • the blower casing 92 has a suction port 93 formed in its central portion to provide an inlet to the central inlet region of the impeller.
  • the diffuser 89 is composed of a plurality of diffuser vanes 94 arranged radially outside the circumference of the centrifugal impeller 90.
  • a plurality of return guide vanes 95 are arranged on the back of a wall 89a lying adjacent the impeller 90 and supporting the diffuser vanes 94.
  • the wall 89a has a rounded outer peripheral edge to smooth the air flow from the diffuser vanes 94 to the return guide vanes 95, and in conjunction with the wall 89a and the end bracket 87, the return guide vanes 95 define a return guide passage through which the air flow is guided to the suction ports 88.
  • Fig. 2 shows the configuration of the centrifugal impeller 90 and the diffuser region in more detail.
  • the impeller 90 is composed of a plurality of vanes 96, a shroud plate 97 and hub plate 98.
  • Each vane 96 has on each edge three protrusions which are fitted in holes formed in the shroud plate 97 and the hub plate 98 and then caulked or upset, so that these components are rigidly and tightly secured together at these connection points.
  • the vanes 96 are curved as they extend outwardly, but for convenience this is not indicated in Fig. 2.
  • the shroud plate 97 is straight in its outer diameter portion, as viewed in the axial plane, and has a rounded portion 97a inwardly from the innermost point of connection 99, as in Fig. 2.
  • the shroud plate 97 in this case is provided with a cylindrical portion 97b extending axially from the end of the rounded portion 97a.
  • the blower casing 101 has an inwardly bent flange 101a at its inner diameter region, so that the gap 100 is left between the flange 101a and the cylindrical portion 97b of the impeller 90. Since the length of the gap 100 is much larger than the thickness of the shroud plate 97, the friction loss of the leak flow can be made very large, the leak flow can be reduced remarkably, and the efficiency of the electric blower can be improved.
  • Figs. 4 and 5 show the diffuser 89 of Figs. 1 and 2 with its vanes 94, as viewed from the suction port 93 of the electric blower.
  • the inlet angle ⁇ 3 of the diffuser vane 94 as shown in Fig. 5 is 3°.
  • the inlet angle ⁇ 3 is the angle between the inner face of the vane at its leading edge and the tangential line at this point.
  • the throat width ws is 2.2 mm, and its ratio to the inner diameter of the diffuser is 0.02.
  • the radius of the rounded leading edge of the vane 94 is 0.5 mm.
  • the air flow coming out of the impeller 90 is decelerated in a semi-vaneless space of the vaned diffuser 89 and further decelerated in each passage defined between two vanes 94.
  • the air discharge velocity of the blower can be made large, particularly about 0.8 times the peripheral speed of the impeller. Accordingly, the size of the impeller can be reduced.
  • Fig. 6 shows the relative efficiency of an electric blower including the impeller according to the embodiment of Figs. 3 to 5, relative to a varying diffuser inlet angle ⁇ 3.
  • the efficiency under the condition that the diffuser inlet angle ⁇ 3 is 5° was taken as a reference. Where the diffuser inlet angle ⁇ 3 is smaller than 2°, the length of the semi-vaneless space is longer, the friction loss increases, and the efficiency decreases. Where the diffuser inlet angle ⁇ 3 is larger than 3°, it tends to come out of the flow angle from the impeller; thus, the performance degrades.
  • the efficiency is about 2% greater than that in the prior art based on an angle of 5°, and even where the diffuser inlet angle is within the range of 1 to 2° or within the range of 3 to 4°, the efficiency is 1% greater.
  • Fig. 7 shows the efficiency of the same electric blower relative to a varying throat width ws.
  • the ratio of the throat width ws to the diffuser inner diameter is smaller than 0.017, the deceleration is insufficient in the semi-open portion but increases in the passages defined between two vanes 94; thus, the flow breaks away in such a passage, thereby decreasing the efficiency.
  • the ratio of the throat width ws to the diffuser inner diameter is larger than 0.025, the deceleration becomes too significant in the semi-open portion; thus, the flow deviates remarkably as it flows into each passage defined between two vanes, thereby decreasing the efficiency.
  • the ratio of the throat width ws to the diffuser inner diameter is 0.02, the efficiency is high.
  • the inlet diameter of the diffuser can be reduced as shown in Figs. 4 and 5, and the energy loss compared with a diffuser with no vanes can be reduced. Further, since the relative velocity at the outlet of the impeller can be decreased, noise can be reduced.
  • Fig. 8 shows the relative efficiency of this electric blower obtained when varying the ratio total area of diffuser vane throats real area of diffuser inlets given by Z vd . b 3 . ws D 3 . b 3 . sin ⁇ 3
  • Fig. 9 shows the diffuser 89 in another embodiment of the present invention.
  • Each passage of the diffuser is defined by the vane portions overlapped.
  • the outer end of each vane 94 is rounded while the inner end is tapered, and by this tapering, the throat width ws can be kept within an optimum range.
  • the air discharged from the impeller 90 flows along the vane 94 at about the set flow rate, but the air flow at a small flow rate breaks away in the semi-vaneless space, as indicated by the arrows in the drawing, on the suction pressure side of the diffuser vane; therefore, the direction of the air stream is forcibly changed by the taper portion on the pressure side of the adjacent vane, thereby alleviating the broken air stream, so that the zone of surge generation is shifted more to the side of a small flow rate.
  • Fig. 10 shows the result of experiments on the relationship between the flow rate and pressure (static pressure) of the electric blower, in which the solid curve corresponds to the case including a diffuser based on the embodiment of Fig. 9.
  • the broken curve corresponds to the case for comparison including a diffuser whose inlet angle is 5°.
  • the comparison case shows the surge generation zone in the vicinity of a design point
  • the embodiment with a diffuser inlet angle of 3° can shift the surge generation zone to a small flow rate range.

Claims (5)

  1. Aspirateur de poussière Comportant un rotor-impulseur (90), un moteur de soufflage (81) accouplé au rotor-impulseur (90) et un diffuseur (89) comportant une pluralité de palettes de diffuseur (94) agencée radialement à l'extérieur du rotor-impulseur, caractérisé en ce que l'angle d'entrée (β3) desdites palettes de diffuseur (94) se situe dans la plage de 1° à 4°.
  2. Aspirateur de poussière selon la revendication 1, où le rapport de la largeur de gorge (ws) entre des paires adjacentes desdites palettes de diffuseur (94) au diamètre d'entrée (D3) desdites palettes de diffuseur (94) se situe dans la plage de 0,017 à 0,025.
  3. Aspirateur de poussière selon la revendication 1 ou la revendication 2, comportant un passage de guidage de retour pour guider l'air desdites palettes de diffuseur audit moteur de soufflage pour refroidir le moteur.
  4. Aspirateur de poussière selon la revendication 3, où ledit passage de guidage de retour s'étend radialement vers l'intérieur et est séparé de la région dudit rotor-impulseur (90) et desdits palettes de diffuseur (94) par une paroi (89a) ayant un bord périphérique extérieur arrondi.
  5. Aspirateur de poussière selon l'une des revendications 1 à 4, où le rapport zone totale des gorges des palettes de diffuseur zone réelle des entrées de diffuseur
    Figure imgb0007
     fourni par Z vd . b 3 . ws D 3 . b 3 . sin β 3
    Figure imgb0008
     situe dans la plage de 1,75 à 3,5,
    où
    Zvd   = nombre des palettes de diffuseur
    b3   = largeur axiale des palettes de diffuseur
    ws   = largeur de gorge des palettes de diffuseur
    D3   = diamètre d'entrée des palettes de diffuseur
    β3   = angle d'entrée des palettes de diffuseur.
EP94101775A 1990-07-20 1991-07-03 Soufflante et diffuseur d'aspirateur Expired - Lifetime EP0602007B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2190540A JP2852106B2 (ja) 1990-07-20 1990-07-20 電気掃除機及び電動送風機
JP190540/90 1990-07-20
EP91306038A EP0467557B2 (fr) 1990-07-20 1991-07-03 Soufflante d'aspirateur avec roue de ventilateur

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP91306038A Division EP0467557B2 (fr) 1990-07-20 1991-07-03 Soufflante d'aspirateur avec roue de ventilateur
EP91306038.0 Division 1991-07-03

Publications (3)

Publication Number Publication Date
EP0602007A2 EP0602007A2 (fr) 1994-06-15
EP0602007A3 EP0602007A3 (fr) 1994-12-28
EP0602007B1 true EP0602007B1 (fr) 1997-10-01

Family

ID=16259788

Family Applications (2)

Application Number Title Priority Date Filing Date
EP94101775A Expired - Lifetime EP0602007B1 (fr) 1990-07-20 1991-07-03 Soufflante et diffuseur d'aspirateur
EP91306038A Expired - Lifetime EP0467557B2 (fr) 1990-07-20 1991-07-03 Soufflante d'aspirateur avec roue de ventilateur

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP91306038A Expired - Lifetime EP0467557B2 (fr) 1990-07-20 1991-07-03 Soufflante d'aspirateur avec roue de ventilateur

Country Status (4)

Country Link
EP (2) EP0602007B1 (fr)
JP (1) JP2852106B2 (fr)
KR (1) KR0180742B1 (fr)
DE (2) DE69127832T2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008019869A (ja) * 2006-07-12 2008-01-31 Johnson Electric Sa 送風機

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KR100409173B1 (ko) * 1995-06-26 2004-03-26 가부시끼가이샤 히다치 세이사꾸쇼 전기청소기
AU7691196A (en) * 1995-11-24 1997-06-19 Nilfisk A/S A blower for a vacuum cleaner
DE19605742A1 (de) * 1996-02-16 1997-08-21 Vorwerk Co Interholding Elektromotor mit einem Gebläserad
DE19606146A1 (de) * 1996-02-20 1997-08-21 Vorwerk Co Interholding Schnellaufender Elektromotor
WO1997037423A2 (fr) * 1996-03-29 1997-10-09 AEG Hausgeräte GmbH Turbomachine destinee notamment a un appareil electromenager
DE19733687B4 (de) * 1996-08-12 2005-04-21 Samsung Kwangju Electronics Co., Ltd. Motorgebläse für ein Reinigungsgerät
JP3840299B2 (ja) 1996-12-27 2006-11-01 日本テトラパック株式会社 パッケージ製造装置の折り線形成装置
DE19717154A1 (de) * 1997-04-23 1998-10-29 Bosch Siemens Hausgeraete Gebläseanordnung
EP1135610B1 (fr) * 1998-09-11 2005-05-11 Peter John King Pompes a fluide
DE19855905B4 (de) * 1998-12-03 2013-02-21 BSH Bosch und Siemens Hausgeräte GmbH Gebläseanordnung
CN1124417C (zh) * 1999-04-20 2003-10-15 三洋电机株式会社 电动送风机以及使用它的电动吸尘器
KR100437018B1 (ko) * 2001-08-29 2004-06-23 엘지전자 주식회사 진공 청소기용 원심 송풍기
KR20030048918A (ko) * 2001-12-13 2003-06-25 주식회사 엘지이아이 진공청소기용 원심송풍기
GB0203147D0 (en) * 2002-02-11 2002-03-27 Dyson Ltd An exhaust assembly
CN103321922B (zh) * 2012-03-22 2016-11-23 德昌电机(深圳)有限公司 风机及具有该风机的真空吸尘器和干手机
DE102017215261B4 (de) 2017-08-31 2020-12-24 BSH Hausgeräte GmbH Gebläse für ein elektrogerät
WO2023108921A1 (fr) * 2021-12-16 2023-06-22 广东威灵电机制造有限公司 Ventilateur et dispositif de nettoyage le comprenant

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US4012166A (en) * 1974-12-04 1977-03-15 Deere & Company Supersonic shock wave compressor diffuser with circular arc channels
JPS5349313A (en) * 1976-10-18 1978-05-04 Matsushita Electric Ind Co Ltd Motor fan for vacuum cleaners
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JPS60173398A (ja) * 1984-02-16 1985-09-06 Matsushita Electric Ind Co Ltd 送風機
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JPH02156920A (ja) * 1988-12-09 1990-06-15 Hitachi Ltd 電気掃除機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008019869A (ja) * 2006-07-12 2008-01-31 Johnson Electric Sa 送風機
US8152488B2 (en) 2006-07-12 2012-04-10 Johnson Electric S.A. Blower

Also Published As

Publication number Publication date
DE69105845T2 (de) 1995-04-27
JPH0481600A (ja) 1992-03-16
EP0602007A2 (fr) 1994-06-15
DE69127832D1 (de) 1997-11-06
EP0467557B2 (fr) 2001-09-26
KR0180742B1 (ko) 1999-02-01
JP2852106B2 (ja) 1999-01-27
EP0467557A1 (fr) 1992-01-22
DE69127832T2 (de) 1998-04-30
DE69105845D1 (de) 1995-01-26
EP0602007A3 (fr) 1994-12-28
EP0467557B1 (fr) 1994-12-14
KR920002084A (ko) 1992-02-28

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