EP3306100B1 - Buse d'entrée pour un ventilateur centrifuge - Google Patents

Buse d'entrée pour un ventilateur centrifuge Download PDF

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Publication number
EP3306100B1
EP3306100B1 EP17188456.2A EP17188456A EP3306100B1 EP 3306100 B1 EP3306100 B1 EP 3306100B1 EP 17188456 A EP17188456 A EP 17188456A EP 3306100 B1 EP3306100 B1 EP 3306100B1
Authority
EP
European Patent Office
Prior art keywords
section
inlet nozzle
inlet
flow
axial
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.)
Active
Application number
EP17188456.2A
Other languages
German (de)
English (en)
Other versions
EP3306100A1 (fr
Inventor
Christian Haag
Erhardt Gruber
Oliver Haaf
Konrad Schmitt
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.)
Ebm Papst Mulfingen GmbH and Co KG
Original Assignee
Ebm Papst Mulfingen GmbH and Co KG
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.)
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Publication date
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Publication of EP3306100A1 publication Critical patent/EP3306100A1/fr
Application granted granted Critical
Publication of EP3306100B1 publication Critical patent/EP3306100B1/fr
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression

Definitions

  • the invention relates to an inlet nozzle for a radial fan.
  • Generic inlet nozzles are, for example, from the prior art EP 1 122 444 B1 famous.
  • the construction is based on the knowledge that sound is caused by local pressure fluctuations in the air flow, which in turn can be traced back to separation phenomena or strong changes in the speed of the air flow.
  • the boundary layer on the nozzle wall which is widened by the disruptive element, causes a lower velocity gradient when balancing the air flow emerging from the inlet nozzle and the air flow emerging in the gap between the inlet nozzle and the impeller.
  • the velocity gradient has a direct influence on the sound power, as it is proportional to the interaction forces that act on the air particles. These interaction forces on the air particles are in turn proportional to the acoustic power and thus to the noise level.
  • the invention is therefore based on the object of providing an inlet nozzle that is easy to manufacture and that effectively dampens noise with little manufacturing effort, without significant losses in the air output of the connected fan.
  • an inlet nozzle for a radial fan with a plurality of flow sections determined over the wall of the inlet nozzle as seen in the flow direction comprising an inlet section E having an inlet opening, a disturbance section S directly adjoining the inlet section and an outlet section A directly adjoining the disturbance section
  • the flow cross-section of the inlet nozzle is reduced in the inlet section.
  • the interfering section formed between the inlet section and the outlet section is cylindrical over its entire axial length and extends parallel to the axis of rotation of the inlet nozzle, so that the flow cross section of the inlet nozzle in the interfering section is constant.
  • the inlet nozzle is preferably funnel-shaped and rotationally symmetrical about the axis of rotation.
  • the cylindrical shape of the wall of the inlet nozzle in the disturbance section is easier to manufacture compared to the beads of the prior art.
  • the transition between the flow cross-section of the inlet section, which decreases in the direction of flow, to the disturbance section and its cylindrical shape produce the noise-reducing disturbance of the flow the inlet nozzle.
  • the shape of the disturbance section adjoining the tapering inlet section as cylindrical is sufficient to influence the flow sufficiently to ensure at least the disturbance achieved in the prior art via beads.
  • the interference section is cylindrical and extends parallel to the axis of rotation of the inlet nozzle. This means that the air flow flowing through the inlet nozzle, after passing through the interfering section in the outlet section, is again influenced by a changed shape of the inner wall.
  • An embodiment is advantageous in which the transition from the inlet section to the interfering section and from the interfering section to the outlet section is in each case discontinuous. The discontinuous transition creates increased turbulence between the inlet section, the disturbance section and the outlet section, but detachment of the boundary layer is inhibited.
  • the flow cross-section of the inlet nozzle is reduced in the outlet section, i.e. the wall of the outlet section extends at least in sections towards the axis of rotation.
  • An embodiment is favorable here in which the outlet section extends over its entire axial length in the direction of flow convergent to the axis of rotation of the inlet nozzle.
  • an embodiment of the inlet nozzle is advantageous in which the inlet section tapering in the direction of flow has a rounded contour in axial section.
  • the inlet section expediently has a steady course viewed in the direction of flow.
  • the outlet section has a plurality of mutually adjoining sub-sections in the flow direction, at least one of the sub-sections having a rounded contour as seen in axial section.
  • both sub-sections advantageously run convergent to the axis of rotation.
  • the inlet nozzle comprises, as a further flow section, the outlet section Z directly adjoining the outlet section, as seen in the direction of flow, which also forms the outlet opening of the inlet nozzle.
  • the outlet section which advantageously runs divergent to the axis of rotation of the inlet nozzle in the flow direction, has a flow cross-section that increases in the flow direction (diffuser shape), so that the inlet nozzle forms a Venturi shape over its axial extent.
  • a geometric design of the inlet nozzle has an advantageous effect in which the size ratio of the axial interference height S of the interference section to the total axial height H of the inlet nozzle is in a range of 0.08 S / H 0.14, more preferably at 0 , 09-0.11, more preferably 0.1.
  • a geometric design of the inlet nozzle has an advantageous effect in which the size ratio of the axial outlet height A of the outlet section to the axial outlet height Z of the outlet section of the inlet nozzle is in a range of 1.8 A / Z 2.8, more preferably at 2 , 2-2.4, more preferably 2.30.
  • FIG. 1 an embodiment of a rotationally symmetrical funnel-shaped inlet nozzle 1, arranged on an impeller 30, is shown in axial section, with only the details of the wall to illustrate the flow sections being reproduced.
  • the cover disk 31 of the impeller 30 can essentially be seen.
  • the inlet nozzle 1 comprises the inlet section 2 defining the inlet opening 7, the interfering section 3 directly adjoining the inlet section 2, the outlet section 4 directly adjoining the interfering section 3 and the outlet section directly adjoining the outlet section 4 and forming the outlet opening 8 5.
  • the inlet section 2 merges at its axial edge into a fastening flange 6, the shape of which can be variably round or angular.
  • the flow cross-section of the inlet nozzle 1 in the flow sections is ensured by the geometric shape of the respective wall.
  • the outer wall shape corresponds in each case to the inner wall shape, but the flow cross-section is defined exclusively via the inner wall shape.
  • the flow cross-section is reduced in the inlet section 2, the wall having an elliptical curvature R E when viewed in cross-section.
  • the interfering section 3 adjoining the inlet section 2 is circumferentially cylindrical over its entire axial length and extends parallel to the axis of rotation of the inlet nozzle 1.
  • the flow cross section of the inlet nozzle 1 is constant in the interfering section 3.
  • the outlet section 4 adjoining the interfering section 3 has, in cross section according to FIG Figure 1 seen, likewise a rounding R AL which reduces the flow cross section, but which is less than the rounding R E of the inlet section 2.
  • the outlet section 4 runs convergently to the axis of rotation of the inlet nozzle 1.
  • the outlet section 4 adjoins the outlet section 4 with a continuous transition from the outlet section 5, which increases the flow cross-section and has a radially outwardly directed rounding R AT , so that the inlet nozzle 1 overall has a venturi shape.
  • the courses of the individual flow sections 2, 3, 4, 5 are each continuous, but the transitions between the inlet section 2 and the interfering section 3 and the interfering section 3 and the outlet section 4 are discontinuous.
  • the size ratio of the axial inlet height E of the inlet section 2 in relation to the overall axial height H of the inlet nozzle 1 corresponds to a value of 0.22.
  • the size ratio of the axial disturbance height S of the disturbance section 3 in relation to the total axial height H corresponds to a value of 0.10.
  • the size ratio of the axial outlet height A of the outlet section 4 to the axial outlet height Z of the outlet section 5 of the inlet nozzle 1 has a value of 2.30.
  • the inlet nozzle 1 achieved those in the Figures 2 and 3 Noise values (sound power) which are improved compared to inlet nozzles of the state of the art without interference section, with values of the pressure, the speed and the power of the connected identical centrifugal fan that are not significantly changed, shown on the basis of curve diagrams.
  • the values of the prior art are always marked with squares, those of the inlet nozzle 1 with dots.
  • the noise behavior improves, especially at high volume flows, ie the sound power level is reduced.
  • This is also shown in the frequency third octave band representation Figure 4 the sound pressure level inlet nozzle 1 out Fig. 1 in which there is a significant reduction in the sound pressure level at frequency values of 125-160 and 4000-8000Hz.

Landscapes

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

Claims (10)

  1. Buse d'entrée pour un ventilateur centrifuge avec, vu dans le sens d'écoulement, plusieurs sections d'écoulement déterminées par le biais de la paroi de la buse d'entrée (1), qui comprennent au moins : une section d'admission (2) présentant une ouverture d'admission (7), une section de perturbation (3) se raccordant directement à la section d'admission (2) et une section d'évacuation se raccordant directement à la section de perturbation (3), dans laquelle une section transversale d'écoulement de la buse d'entrée (1) décroît dans la section d'admission (2), dans laquelle la section de perturbation (3) réalisée entre la section d'admission (2) et la section d'évacuation (4) est réalisée sur toute sa longueur axiale de manière cylindrique et s'étendant parallèlement à l'axe de rotation de la buse d'entrée (1), de sorte que la section transversale d'écoulement de la buse d'entrée (1) est constante dans la section de perturbation (3), caractérisée en ce qu'une section transversale d'écoulement de la buse d'entrée (1) décroît dans la section d'évacuation (4), et dans laquelle une section de sortie (5) formant une ouverture de sortie (8) se raccorde directement à la section d'évacuation (4) vu, dans le sens d'écoulement, en tant qu'autre section d'écoulement, qui s'étend dans le sens d'écoulement de manière divergente à l'axe de rotation de la buse d'entrée (1) et dont la section transversale d'écoulement s'agrandit dans le sens d'écoulement.
  2. Buse d'entrée selon la revendication 1, caractérisée en ce que la section d'admission (2) effilée dans le sens d'écoulement présente vu dans la coupe axiale un contour arrondi.
  3. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce que la section d'admission (2) présente vu dans le sens d'écoulement une allure constante.
  4. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un passage de la section d'admission (2) à la section de perturbation (3) et de la section de perturbation (3) à la section d'évacuation (4) est respectivement discontinu.
  5. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce que la section d'évacuation (4) s'étend dans le sens d'écoulement de manière convergente à l'axe de rotation de la buse d'entrée (1).
  6. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce que la section d'évacuation (4) présente dans le sens d'écoulement plusieurs sous-sections se raccordant l'une à l'autre dans le sens d'écoulement, dans laquelle au moins une des sous-sections présente vu dans la coupe axiale un contour arrondi.
  7. Buse d'entrée selon la revendication 1, caractérisée en ce qu'un passage de la section d'évacuation (4) à la section de sortie (5) présente une allure constante.
  8. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rapport de grandeur d'une hauteur d'admission axiale E de la section d'admission (2) par rapport à une hauteur totale axiale H de la buse d'entrée (1) est fixé de sorte que 0,15 ≤ E/H ≤ 0,30.
  9. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rapport de grandeur d'une hauteur de perturbation axiale S de la section de perturbation (3) par rapport à une hauteur totale axiale H de la buse d'entrée (1) est fixé de sorte que 0,08 ≤ S/H ≤ 0,14.
  10. Buse d'entrée selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rapport de grandeur d'une hauteur d'évacuation axiale A de la section d'évacuation (4) par rapport à une hauteur de sortie axiale Z de la coupe de sortie (5) de la buse d'entrée (1) est fixé de sorte que 1,8 ≤ A/Z ≤ 2,8.
EP17188456.2A 2016-10-05 2017-08-30 Buse d'entrée pour un ventilateur centrifuge Active EP3306100B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016118856.5A DE102016118856A1 (de) 2016-10-05 2016-10-05 Einlaufdüse für einen Radialventilator

Publications (2)

Publication Number Publication Date
EP3306100A1 EP3306100A1 (fr) 2018-04-11
EP3306100B1 true EP3306100B1 (fr) 2021-07-21

Family

ID=59000249

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17188456.2A Active EP3306100B1 (fr) 2016-10-05 2017-08-30 Buse d'entrée pour un ventilateur centrifuge

Country Status (4)

Country Link
US (1) US10612561B2 (fr)
EP (1) EP3306100B1 (fr)
CN (1) CN206246418U (fr)
DE (1) DE102016118856A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020115540A1 (fr) * 2018-12-07 2020-06-11 Regal Beloit America, Inc. Ensemble soufflante centrifuge

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2083186A (en) * 1936-03-23 1937-06-08 American Blower Corp Fan
DE3304963A1 (de) * 1983-02-12 1984-08-16 Hans Joachim 7440 Nürtingen Leithner Radailventilator fuer lueftungstechnische anlagen
DE4222131C3 (de) * 1992-07-06 2000-01-27 Vem Motors Gmbh Belüftungseinrichtung für die Druckbelüftung von oberflächenbelüfteten elektrischen Maschinen
DE29506691U1 (de) * 1995-04-20 1996-08-29 Papst-Motoren GmbH & Co KG, 78112 St Georgen Brennergebläse mit Radiallaufrad
DE20001746U1 (de) * 2000-02-01 2001-06-21 ebm Werke GmbH & Co., 74673 Mulfingen Radialventilator und Düse für einen Radialventilator
US6499948B1 (en) * 2000-02-07 2002-12-31 Penn Ventilation, Inc. Shroud and axial fan therefor
DE102012021372B4 (de) * 2012-10-25 2023-05-04 Ziehl-Abegg Se Einlaufdüse für Radialventilatoren sowie Radialventilator
DE102015207948A1 (de) * 2015-04-29 2016-11-03 Ziehl-Abegg Se Einströmdüse für einen Radial-, Diagonal- oder Axialventilator und Radial-, Diagonal- oder Axialventilator mit einer Einströmdüse

Also Published As

Publication number Publication date
US20180094641A1 (en) 2018-04-05
US10612561B2 (en) 2020-04-07
CN206246418U (zh) 2017-06-13
EP3306100A1 (fr) 2018-04-11
DE102016118856A1 (de) 2018-04-05

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