EP2292935B1 - Boîtier de ventilateur radial - Google Patents

Boîtier de ventilateur radial Download PDF

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Publication number
EP2292935B1
EP2292935B1 EP10169984.1A EP10169984A EP2292935B1 EP 2292935 B1 EP2292935 B1 EP 2292935B1 EP 10169984 A EP10169984 A EP 10169984A EP 2292935 B1 EP2292935 B1 EP 2292935B1
Authority
EP
European Patent Office
Prior art keywords
radial fan
fan housing
wall area
housing device
wall
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.)
Not-in-force
Application number
EP10169984.1A
Other languages
German (de)
English (en)
Other versions
EP2292935A2 (fr
EP2292935A3 (fr
Inventor
Paul Zerelles
Matthias Lang
Dieter Sartorius
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Mahle Behr 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.)
Filing date
Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2292935A2 publication Critical patent/EP2292935A2/fr
Publication of EP2292935A3 publication Critical patent/EP2292935A3/fr
Application granted granted Critical
Publication of EP2292935B1 publication Critical patent/EP2292935B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a radial fan housing device for Ventilvorvvo asparagusen, in particular for ventilation devices of motor vehicles, which have at least one boundary wall which limits at least partially a Radiaitufter effectivenessraum in the radial direction as defined in the preamble of claim 1.
  • a radial fan housing device for Ventilvorvvo Vietnamese, a radial fan housing device for Ventilvorvvo Vietnamese, a radial fan housing device for Ventilvorvvo asparagusen, in particular for ventilation devices of motor vehicles, which have at least one boundary wall which limits at least partially a Radiaitufterabilityraum in the radial direction as defined in the preamble of claim 1.
  • a blower device in particular a manure device for a motor vehicle.
  • an air conditioner in particular a Kraftfullyktimastrom.
  • fans or blowers have been proven. This makes it possible to provide interiors with a sufficient Luftzufahr, the air supplied may optionally be preceded by heat exchanger (radiator and / or evaporator), filters and the like can be passed. Depending on the specific application, the fan or blower must have different characteristics. While for example, in a first application (such as in a radiator of a motor vehicle), primarily a high air flow rate (and thus a high cooling capacity) arrives, in some applications, for example, a particularly low operating noise (for example in the ventilation of a motor vehicle interior) is in the foreground.
  • a particularly low operating noise for example in the ventilation of a motor vehicle interior
  • radio fans For ventilation of interiors, especially of motor vehicle interior spaces, radial fans are used in particular. Such radio fans fulfill the tasks assigned to them satisfactorily.
  • the object of the invention is therefore to propose a comparison with the prior art improved radial fan housing device.
  • the object of the invention is to propose a comparison with the prior art improved Gebläsevörraum or air conditioning.
  • a radial fan housing device for Ventilationsvörraumen which at least one boundary wall, which defines at least partially a radial fan receiving space in the radial direction such that the boundary wall is formed such that the radial fan receiving space extends downstream in at least a first wall region in a logarithmic manner and in at least one extended second wall area in a linear manner. It is particularly advantageous if the radial fan housing device is used for ventilation devices of motor vehicles. Tests have shown that such a combination of logarithmic extension and subsequent linear expansion of the radial fan compartment (relative to a radial fan located in the radial fan compartment) can result in a surprisingly high noise reduction.
  • a particularly significant noise reduction can result, especially in the low-frequency range, which is particularly advantageous because operating noise in the low-frequency range are often perceived as particularly disturbing and / or are relatively difficult to dampen.
  • First experiments have shown that the proposed design of the radial fan housing device can result in a noise reduction of typically in the range of 2 to 3.5 dB per third compared to a purely logarithmic spiral shape.
  • an arbitrary reference point can be selected.
  • a reference point should be chosen which has a characteristic property and / or allows reference that is as clear as possible or easily referenceable.
  • a typical example of this is, for example, a fan blade, which typically forms a transition between the Radillstageerageraum and a Heilab USAkanal (usually running in the tangential to radial direction).
  • the proposed combination of logarithmic extension and linear expansion can not only have a particularly good acoustic behavior, but in particular also a very good efficiency.
  • the logarithmic range can absorb the increasing air flow along the direction of the radial fan impeller, without the need for undesirable flow phenomena in the corresponding area.
  • a logarithmic expansion essentially corresponds to the increase of the air mass flow in the circumferential direction of the radial fan wheel, so that in particular undesirable flow phenomena of the delivered air can be avoided. In this way, in particular a particularly good efficiency of the radial fan housing device can be achieved.
  • At least one first wall area is arranged in front of at least one second wall area.
  • Experiments have shown that in this case usually particularly good efficiencies, coupled with a particularly good acoustic behavior can result.
  • At least one third wall region is provided, which forms a transition region to an air outlet duct.
  • This wall portion may have a substantially arbitrary shape.
  • the third wall region (the third warhead regions) can be embodied such that a trichelike extension results.
  • the one or more third wall regions have a length which is small in relation to the first wall region and / or the second wall region.
  • the increase in cross-sectional area is relatively greatly increased without favoring flow separation, for example, to avoid over-speed caused by too narrow cross sections, which can generate high-frequency noise and / or loss of efficiency at high mass flows can result.
  • At least one third wall region has at least one rectilinear boundary wall at least in regions.
  • the first wall region is formed in a region which starts at 0 °, 5 °, 10 °, 16 ° or 20 ° and / or at 85 °, 90 °, 90 °, 100 ° °, 105 °, 110 °, 115 °, 120 °, 125 °, 130 °, 135 °, 140 ° or 145 ° ends.
  • the mentioned start or end values have proven to be particularly advantageous.
  • a further advantageous design results if the second wall region is formed in a region which is at 85 °, 90 °, 95 °, 100 °, 105 °, 110 °, 115 °, 120 °, 125 °, 130 °, 135 °, 140 ° or 145 ° and / or at 270 °, 275 °, 280 °, 285 °, 290 °, 295 °, 300 °, 305 °, 310 °, 315 °, 320 °, 325 ° or 330 ° ends. Again, it has been shown that particularly advantageous results can be achieved with the above-mentioned initial and final values.
  • the radial fan housing device has at least one housing tongue.
  • This can in particular the transition region between a tangentially and / or radially angeordnentem air discharge channel and the radial fan receiving area.
  • the fan tongue can also serve as a reference point (starting point) for the formation of the boundary wall (and possibly further assemblies).
  • blower device which has at least one radial fan housing device with the structure described above.
  • the blower device then has the advantages and properties already described in an analogous manner.
  • the blower device may be a blower device for a motor vehicle.
  • an air conditioning system which has at least one radial fan blower device with the construction described above and / or at least one blower device with the structure described above.
  • Such an air conditioning system then has the properties and advantages described above in an analogous manner.
  • the air conditioning system may be an automotive air conditioning system.
  • a conceivable embodiment of a radial fan 1 is shown in a schematic plan view.
  • the radial fan 1 has a radial fan housing 2, in whose interior 4 a radial fan 3 is arranged.
  • the radial fan 3 and the boundary wall 5 are formed and arranged so that a channel 6 is formed between the outside of the radial fan 3 and the boundary wall 5.
  • tongue 7 Starting from a so-called tongue 7, the cross section of the channel 6 increases steadily.
  • the air mass flow steadily increasing along the circumference of the radial fan 3 the radial fan 3 discharges over its entire circumference a substantially angle independent air mass flow towards its outside is taken into account.
  • the tongue 7 is rounded.
  • the circle center 8 of the rounded surface of the tongue 7 is used.
  • the reference line 9 extending in the radial direction is represented by the circle center 8 of the rounded tongue 7.
  • the boundary wall 5 in Fig. 1 marked as a bold line.
  • a first angular range 10 the boundary wall 5 of the radial fan housing 2 follows the shape of a conventional logarithmic spiral 13.
  • Fig. 1 a linearly expanding coil 11 is shown.
  • the (variable) slope of the boundary wall 5 is approximately smaller in the first quarter of the angular range 10 than the slope of the drawn for comparison linear spiral 11.
  • the boundary wall 5 in this first angular range 10 is always within the drawn for comparison linear spiral 11 is located. In this way it is possible to save space. Nevertheless, the radial fan 1 in this configuration has a good efficiency and low noise.
  • the boundary wall 5 now follows a spiral 11 with a linear gradient.
  • the logarithmic spiral 13 which follows the boundary wall 5 in the first angular range 10, continued for comparison. How one Fig. 1 can thus take, the boundary wall 5 thus always runs in the second angle range 12 within the "alternative" logarithmic spiral 13, so that space can be saved here as well.
  • experiments have shown that the linear continuation of the boundary wall 5 in the second angular range beyond usually leads in most of operating conditions to a noise reduction.
  • a third angle range 14 follows.
  • the boundary wall 5 is formed in this area such that a transition area 15 from the interior 4 of the radial fan housing 2 to an outwardly leading Vietnameseabtechnologykanal 16 is formed.
  • the boundary wall 5 in a larger area of the third Winkelbereicils 14 is formed as a rectilinear wall 17.
  • Fig. 2 is the dimensioning of the boundary wall 5 of in Fig. 1 illustrated radial fan 1 shown in Cartesian coordinates.
  • the abscissa 18 is in both Fig. 2a as well as in Fig. 2b the angle, starting from the Begrenzüngsline 9 (zero point) shown.
  • the ordinate 19 in Fig. 2a shows the air passage cross section of the channel as a function of the respective angular position Fig. 2b along the ordinate 19 is the differential one Change in the air passage cross section through the channel 6 per unit angle shown.
  • the second angle region 12 is adjoined by the third angle region 14 (transition region 15), in which the boundary wall 5 is adapted to the following contour of a connection component, such as the evaporator housing of the air conditioning system.
  • the boundary wall 5 is formed so that finally the cross section of the logarithmic spiral 13 is reached again.
  • Fig. 3 Finally, the result of two measurements is shown. There, the velocity distribution of the air flowing through the channel 6 at a radial fan 20 with pure logarithmic spiral 13 with the air velocity distribution of in Fig. 1 illustrated radial fan 1 (having different angular ranges 10, 12, 14) shown. As you can see, the velocity of the air flowing through channel 6 is distributed much more homogeneously. In addition, speed peaks can be avoided. Both effects together result in a particularly effective noise reduction, in particular in the low-frequency frequency range, which is usually perceived as particularly disturbing. In addition, the efficiency of the radial fan 1 can be particularly high.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Motor Or Generator Frames (AREA)

Claims (10)

  1. Dispositif de carter de ventilateur radial (2) pour des dispositifs de ventilation (1), en particulier pour des dispositifs de ventilation (1) de véhicules automobiles, présentant au moins une paroi de délimitation (5) qui délimite au moins partiellement, dans la direction radiale, un espace de logement de ventilateur radial (4), caractérisé en ce que la paroi de délimitation (5) est conçue de telle façon, que l'espace de logement de ventilateur radial (4) s'élargit en aval, de manière logarithmique, dans au moins une première zone de paroi (10), et s'élargit de manière linéaire dans au moins une deuxième zone de paroi (12).
  2. Dispositif de carter de ventilateur radial (2) selon la revendication 1, caractérisé en ce qu'au moins une première zone de paroi (10) est disposée, suivant une plage angulaire, en amont d'au moins une deuxième zone de paroi (12).
  3. Dispositif de carter de ventilateur radial (2) selon l'une des revendications précédentes, caractérisé en ce que seulement une première zone de paroi (10) et seulement une deuxième zone de paroi (12) sont présentes.
  4. Dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu au moins une troisième zone de paroi (14) qui forme une zone de transition (15) en direction d'un conduit de sortie d'air (16).
  5. Dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une troisième zone de paroi (14) présente au moins partiellement au moins une paroi de délimitation rectiligne (17).
  6. Dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu en outre une languette de carter, et un centre de cercle, qui peut être relié au centre du dispositif de carter de ventilateur radial, par une ligne de référence, présente au moins une première zone de paroi et une deuxième zone de paroi, où la première zone de paroi (10) est configurée dans une plage qui, considérée par rapport à la ligne de référence, commence à environ 0°, 5°, 10°, 15° ou 20° et / ou se termine à environ 85°, 90°, 95°, 100°, 105°, 110°, 115°, 120°, 125°, 130°, 135°, 140° ou 145°.
  7. Dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu en outre une languette de carter, et un centre de cercle, qui peut être relié au centre du dispositif de carter de ventilateur radial, par une ligne de référence, présente au moins une première zone de paroi et une deuxième zone de paroi, où la deuxième zone de paroi (12) est configurée dans une plage qui, considérée par rapport à la ligne de référence, commence à environ 85°, 90°, 95°, 100°, 105°, 110°, 115°, 120°, 125°, 130°, 135°, 140° ou 145° et / ou se termine à environ 270°, 275°, 280°, 285°, 290°, 295°, 300°, 305°, 310°, 315°, 320°, 325° ou 330°.
  8. Dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de carter de ventilateur radial (2) présente au moins une languette de carter (7).
  9. Dispositif de soufflante (1), en particulier dispositif de soufflante (1) pour un véhicule automobile, présentant au moins un dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications 1 à 8.
  10. Système de climatisation, en particulier système de climatisation d'un véhicule automobile, présentant au moins un dispositif de carter de ventilateur radial (2) selon l'une quelconque des revendications 1 à 8 et / ou présentant au moins un dispositif de soufflante (1) selon la revendication 9.
EP10169984.1A 2009-07-17 2010-07-19 Boîtier de ventilateur radial Not-in-force EP2292935B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009033776A DE102009033776A1 (de) 2009-07-17 2009-07-17 Radiallüftergehäuse

Publications (3)

Publication Number Publication Date
EP2292935A2 EP2292935A2 (fr) 2011-03-09
EP2292935A3 EP2292935A3 (fr) 2013-01-30
EP2292935B1 true EP2292935B1 (fr) 2016-11-02

Family

ID=42989227

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10169984.1A Not-in-force EP2292935B1 (fr) 2009-07-17 2010-07-19 Boîtier de ventilateur radial

Country Status (2)

Country Link
EP (1) EP2292935B1 (fr)
DE (1) DE102009033776A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5517914B2 (ja) * 2010-12-27 2014-06-11 三菱重工業株式会社 遠心圧縮機のスクロール構造
EP2811170A1 (fr) 2013-06-04 2014-12-10 Behr GmbH & Co. KG Ventilateur radial
CN103994102B (zh) * 2014-05-07 2016-08-24 江苏大学 一种低比转速离心泵用螺旋形压水室设计方法
DE102014221955B4 (de) 2014-10-28 2017-10-19 Mahle International Gmbh Klimagerät
CN106989063A (zh) * 2017-05-10 2017-07-28 江苏双达泵业股份有限公司 一种离心泵用准螺旋型压水室设计方法
DE102017122987A1 (de) 2017-10-04 2019-04-04 Ebm-Papst Mulfingen Gmbh & Co. Kg Halbspiralgehäuse
WO2019097730A1 (fr) * 2017-11-20 2019-05-23 三菱重工エンジン＆ターボチャージャ株式会社 Compresseur centrifuge et turbocompresseur pourvu dudit compresseur

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
US1778015A (en) * 1929-01-24 1930-10-14 Hoover Co Fan casing
US3846040A (en) * 1972-06-16 1974-11-05 D Dennis Blower housing
DE3238913C2 (de) 1982-10-21 1985-10-03 Werner Dr. 8972 Sonthofen Röhrs Radialventilatorgehäuse
DE8308535U1 (de) * 1983-03-19 1984-06-20 Joh. Vaillant Gmbh U. Co, 5630 Remscheid Radialgeblaese
WO1990009524A1 (fr) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Ventilateur centrifuge et diffuseur a volute d'accumulation
DE4141106C2 (de) * 1991-12-13 2001-10-04 Papst Licensing Gmbh & Co Kg Radialgebläse
KR100337287B1 (ko) * 1999-07-28 2002-05-17 윤종용 원심 송풍기
CA2314532C (fr) 1999-08-10 2009-10-27 Lg Electronics Inc. Ventilateur

Non-Patent Citations (1)

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Title
None *

Also Published As

Publication number Publication date
DE102009033776A1 (de) 2011-01-20
EP2292935A2 (fr) 2011-03-09
EP2292935A3 (fr) 2013-01-30

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