EP0143235B2 - Ventilateur axial sans couronne de guidage particulièrement pour la ventilation d'échangeurs de chaleur - Google Patents

Ventilateur axial sans couronne de guidage particulièrement pour la ventilation d'échangeurs de chaleur Download PDF

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Publication number
EP0143235B2
EP0143235B2 EP84111075A EP84111075A EP0143235B2 EP 0143235 B2 EP0143235 B2 EP 0143235B2 EP 84111075 A EP84111075 A EP 84111075A EP 84111075 A EP84111075 A EP 84111075A EP 0143235 B2 EP0143235 B2 EP 0143235B2
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EP
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Prior art keywords
vane
housing part
impeller
guide ring
fan
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Expired - Lifetime
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EP84111075A
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German (de)
English (en)
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EP0143235B1 (fr
EP0143235A1 (fr
Inventor
Manfred Dr. Sellmann
Walter Dipl.-Ing. Koch
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Siemens AG
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Siemens AG
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans

Definitions

  • the invention relates to a stator-less axial fan, in particular for ventilation of heat exchangers, according to the preamble of claim 1; such an axial fan is known from DE-A-25 21 416.
  • the inside diameter of the housing piece which adjoins the housing part encasing the flow-active part of the fan, to increase by about 25% by leaps and bounds;
  • the inside diameter of the housing piece which adjoins the housing part encasing the flow-active part of the fan, to increase by about 25% by leaps and bounds;
  • the required amount of air should leave the fan with a speed profile that is as uniform as possible and a swirl component that is as low as possible, as a result of which flow noises on the components that are to be flowed and cooled are kept small.
  • the maximum dimensions of such fans are prescribed for reasons of installation. Since the suction and pressure sides of the fans are still accessible, protective grilles must be fitted there for safety reasons, which in themselves conflict with the aforementioned requirements.
  • axial fans for use in water coolers are known, in which the fan blades are rounded at their ends and run in a housing that consists of a cylindrical part and a downstream, expanding Part exists.
  • the housing expands steadily without jumping into a funnel, the lateral surfaces of which follow a quarter circle in the side view. Because of this housing structure, the air flow leaves the housing largely in the radial direction with deliberate use of the coander effect.
  • the AT-PS 240653 discloses a cooling fan also with a housing which is continuously opening towards the outflow side and is referred to as an air guide ring, in which the fan blades protrude beyond the housing on both sides. Here, too, the air flow exits the fan radially.
  • DE-OS 31 29 236 finally relates to the mechanical attachment of an air guide housing to an axial fan.
  • the fan blades run in a fan ring that widens steadily towards the outlet side and radially deflects the pumped air
  • An axial fan is already known from DE-A-2 327125, the housing of which is provided with an extension, which begins on the outflow side either steplessly or step-wise behind the impeller or already within the impeller area;
  • extension which begins on the outflow side either steplessly or step-wise behind the impeller or already within the impeller area;
  • rounded downstream corners of the blades in cooperation with a housing that has been expanded in a certain way are neither described nor illustrated. To reduce noise, only the lowest possible speed is used.
  • a construction has proven to be a particularly expedient design for the entire fan housing, which is provided with an abruptly expanded diffuser housing part, which is characterized in that a total opening or diameter ratio of 1.03 ⁇ D 2 / D A for the diffuser housing part: 9 1.25, and an entire axial length of 0.10 D a ⁇ l ⁇ 0.5 D D a vorgesenhen, where D a is approximately the inside width of the fan housing in the region of the impeller, and D 2 is the greatest diameter of the diffuser Designated housing part.
  • a technically particularly advantageous design of the diffuser housing part is characterized in that for this housing part, a sudden expansion beginning behind the impeller with a pitch angle: 15 ° ⁇ ⁇ 1 60 60 ° to a diameter dimension of 1.02 D A D D 21 ⁇ D 2 and a subsequent gradual expansion with the pitch angle 0 ° ⁇ 2 ⁇ 10 ° to the diameter dimension D 2 is provided.
  • the diffuser housing part consists of a piece of pipe widened in the area of its expansion by means of a corresponding stamp.
  • the impeller design provided according to the configuration deviates from the previously mentioned or generally recommended values, it has surprisingly been shown that the fan according to the invention with the special design parameters for the blade profile while observing the required values for volume flow and maximum pressure at a certain percentage this volume flow as well as given maximum installation conditions and the lowest possible peripheral speed as well as a low hub ratio, tear-off phenomena do not occur in the impeller and the flow is closer to the state of a uniform speed change for a given volume flow than with larger, known hub ratios and that the absolute amount of this speed is lower.
  • the blade wheel design provided according to the invention with a high work distribution in the outer area of the blade unexpectedly results in a further improvement in combination with the housing design according to the invention and the wing edge rounding with regard to the most uniform possible speed distribution with reduced peak values behind the fan and thus, despite the high delivery capacity, a further noise reduction, which in total results in a reduction from 3 to 4 dB (A).
  • a fan unit consisting essentially of a drive motor M with a fan wheel LR attached to its output shaft with blades S1-S8 is arranged in a surrounding housing, which consists of a first housing part G1 directly surrounding the fan unit M, LR and a second diffuser housing part G2.
  • a protective grille SG is attached to both the inlet and the outlet side of the housing.
  • a second diffuser housing part G2 of abruptly enlarged clear width in the distance range of ⁇ 0.31 a to the downstream corners of the blades S1-S8- is connected on the outlet side to the first housing part G1 surrounding the fan unit M, LR , size 2, the chord length of the blade profile in the outer cut, and starting point of the spacing area on the impeller side starting from non-rounded corners.
  • a sudden expansion behind the impeller LR in the aforementioned sense is initially with a pitch angle: 15 ° 5 ⁇ 1 ⁇ 60 ° except for a diameter dimension: 1.02 D 2 ⁇ D 21 ⁇ D 2 , which is followed by a gradual expansion with a pitch angle: 0 ° ⁇ 2 ⁇ 10 ° to the diameter dimension D 2 ;
  • a diffuser housing part designed in this way is expediently produced from a tube piece initially corresponding to the diameter dimension D A , which is widened by a stamping die having the external dimensions of the extension.
  • a total opening diameter ratio is provided for the diffuser housing part G2: 1.03 D D 2 / D A 1 1.25 and a total axial length: 0.10 D A l l D 0,5 0.5 D a , where D A denotes the inside width of the fan housing (first housing part G1) in the region of the impeller LR and D 2 the largest diameter of the diffuser housing part G2 on its outlet side.
  • the entire blade profile can be determined on the basis of the usual calculation methods for profiled blades of compressors and fans; the overlap ratios customary and recommended for the construction of axial impellers are to be used as a basis.

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

Claims (6)

1. Ventilateur axial sans couronne de guidage, en particulier pour l'aération d'échangeurs de chaleur, comportant au moins une première partie de carter entourant directement une unité de ventilateur et une seconde partie de carter à diffuseur s'y raccordant côté fuite, et possédant une section de passage libre qui croît brusquement, caractérisé par le fait qu'au moins les sommets sur le bord extérieur des aubes (S1-S6), côté fuite, de l'unité de ventilateur (M;LR) sont arrondies (rayon de courbure r), que le début de la section de passage libre, qui croît brusquement, de la partie de carter à diffusion (G2) est situé à une distance de ± 0,3 la par rapport au point d'intersection entre le prolongement du bord arrière des aubes, d'une part, et la corde de l'aile, d'autre part, dans la zone des sommets, côté fuite, des aubes (S1-S8) du rotor (LR), la partie de carter à diffuseur possédant un élargissement brusque qui commence derrière le rotor (LR), avec un angle de pente 15° ≤ α1 ≤ 60°, jusqu'à un diamètre 1,02 DA ≤ D21 ≤ D2 et un élargissement croissant progressivement et s'y raccordant, avec un angle de pente 0° ≤ α2 ≤10° jusqu'au diamètre D2, et avec un rapport d'ouverture totale ou un rapport de diamètres 1,03 ≤ D2/DA ≤ 1,25 et une longueur axiale totale 0, 10 DA ≤ ID ≤ 0, 5 DA, la représentant la longueur de la corde du profil des aubes au niveau de la coupe extérieure, DA le diamètre de passage libre de la première partie du carter (G1) et D2 le diamètre maximum de la partie de carter à diffuseur (G2).
2. Ventilateur axial sans couronne de guidage, caractérisé en ce que la partie de carter à diffuseur (G2) est constituée par une pièce tubulaire qui a été élargie, dans la zone de son élargissement, à l'aide d'un poinçon correspondant.
3. Ventilateur axial sans couronne de guidage suivant la revendication 1 ou 2, caractérisé par le fait que la première partie de carter (G1) et la partie de carter à diffuseur (G2) constituent, ensemble, une pièce tubulaire d'un seul tenant.
4. Ventilateur axial sans couronne de guidage suivant l'une des revendications 1 à 3, caractérisé par le fait que la partie de carter à diffuseur (G2) est pourvue, côté fuite, d'un grillage de protection (SG).
5. Ventilateur axial sans couronne suivant la revendication 1, caractérisé par le fait que les sommets, côté fuite, des aubes (S1-S8) sont arrondis avec un rayon de courbure 0,1 Ia ≤ r ≤ 0,3 Ia.
6. Ventilateur axial sans couronne de guidage comportant des aubes profilées et gauchies, disposées en étant réparties de façon uniforme ou non uniforme sur la périphérie du moyeu du rotor d'une unité de ventilateur et possédant une ligne de squelette galbée B, de telle sorte que le rapport (fll) entre la hauteur (f) du galbe de la ligne de squelette par rapport à la corde de l'aube, à l'écartement (I) entre le bord avant et le bord arrière d'une aube est compris dans la gamme : 0,02 ≤ f/I ≤ 0,1, suivant l'une des revendications 1 à 5, caractérisé par les paramètres suivants de construction pour le rotor de l'unité de ventilateur:
Figure imgb0004
avec les définitions suivantes :
Da = diamètre extérieur du rotor;
Dl = diamètre du moyeu du rotor;
la = longueur de la corde entre le bord avant et le bord arrière du profil de l'aube, dans la coupe extérieure;
Il = longueur de la corde entre le bord avant et le bord arrière du profil de l'aube, dans la coupe intérieure;
γa = angle de réglage des aubes au niveau de la coupe extérieure d'une aube, par rapport au sens périphérique D (sens de rotation);
γl = angle de réglage des aubes au niveau de la coupe intérieure d'une aube, par rapport au sens périphérique D (sens de rotation).
EP84111075A 1983-09-30 1984-09-17 Ventilateur axial sans couronne de guidage particulièrement pour la ventilation d'échangeurs de chaleur Expired - Lifetime EP0143235B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3335649 1983-09-30
DE19833335649 DE3335649A1 (de) 1983-09-30 1983-09-30 Leitradloser axialventilator, insbesondere zur belueftung von waermetauschern

Publications (3)

Publication Number Publication Date
EP0143235A1 EP0143235A1 (fr) 1985-06-05
EP0143235B1 EP0143235B1 (fr) 1987-12-16
EP0143235B2 true EP0143235B2 (fr) 1991-10-23

Family

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Family Applications (1)

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EP84111075A Expired - Lifetime EP0143235B2 (fr) 1983-09-30 1984-09-17 Ventilateur axial sans couronne de guidage particulièrement pour la ventilation d'échangeurs de chaleur

Country Status (2)

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EP (1) EP0143235B2 (fr)
DE (2) DE3335649A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3183459B1 (fr) 2014-08-18 2023-08-02 ebm-papst Mulfingen GmbH & Co. KG Ventilateur axial

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2227793B (en) * 1985-11-08 1990-10-31 Papst Motoren Gmbh & Co Kg Miniature axial fan
GB2185074B (en) * 1985-11-08 1990-12-19 Papst Motoren Gmbh & Co Kg Fan
FR2781843B1 (fr) * 1998-07-28 2000-10-20 Valeo Thermique Moteur Sa Helice de ventilateur compacte optimisee
EP2085709A1 (fr) * 2008-01-30 2009-08-05 LG Electronics Inc. Climatiseur

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334807A (en) * 1966-03-28 1967-08-08 Rotron Mfg Co Fan
DE2327125C3 (de) * 1973-05-28 1979-11-15 Siemens Ag, 1000 Berlin Und 8000 Muenchen Axialventilator mit Gehäuse
DE2541416C3 (de) 1975-09-17 1985-06-27 Knorr-Bremse GmbH, 8000 München Führerbremsventileinrichtung, insbesondere von Schienenfahrzeugen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3183459B1 (fr) 2014-08-18 2023-08-02 ebm-papst Mulfingen GmbH & Co. KG Ventilateur axial

Also Published As

Publication number Publication date
DE3335649A1 (de) 1985-04-18
EP0143235B1 (fr) 1987-12-16
DE3468134D1 (en) 1988-01-28
EP0143235A1 (fr) 1985-06-05

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