EP2292935A2 - Boîtier de ventilateur radial - Google Patents

Boîtier de ventilateur radial Download PDF

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Publication number
EP2292935A2
EP2292935A2 EP10169984A EP10169984A EP2292935A2 EP 2292935 A2 EP2292935 A2 EP 2292935A2 EP 10169984 A EP10169984 A EP 10169984A EP 10169984 A EP10169984 A EP 10169984A EP 2292935 A2 EP2292935 A2 EP 2292935A2
Authority
EP
European Patent Office
Prior art keywords
radial fan
fan housing
wall
housing device
radial
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.)
Granted
Application number
EP10169984A
Other languages
German (de)
English (en)
Other versions
EP2292935A3 (fr
EP2292935B1 (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
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 Behr GmbH and Co KG filed Critical 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 ventilation devices, in particular for motor vehicles, which have at least one boundary wall which limits at least in regions a radial fan receiving space in the radial direction.
  • the invention relates to a Gebläsevorrchtung, in particular a blower device for a motor vehicle.
  • the invention relates to an air conditioner, in particular a motor vehicle air conditioning.
  • fans or blowers have been proven. This makes it possible to provide interiors with a sufficient supply of air, wherein the supplied air may optionally be preceded by heat exchanger (radiator and / or evaporator), filters and the like can be passed. Depending on the specific application, the fans or blowers must have different characteristics.
  • a particularly low operating noise for example in the ventilation of a motor vehicle interior
  • radial fans For ventilation of interiors, in particular of motor vehicle interiors, in particular radial fans are used. Basically, such radial fans satisfy the tasks assigned to them satisfactorily.
  • a radial fan has been proposed that has a housing which increases in the first region at a smaller angle than that of a continuous Archimedean spiral and enlarges in a second region at a greater angle than this Archimedean spiral.
  • the object of the invention is thus 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 blower device or air conditioning.
  • a radial fan housing device for ventilation devices which at least one boundary wall, which defines at least partially a radial fan receiving space in the radial direction in such a way that the boundary wall is formed such that the radial fan receiving space in at least a first wall area in a non-linear manner expands and at least a second wall area extended in a linear manner. It is particularly advantageous if the radial fan housing device is used for ventilation devices of motor vehicles. Experiments have shown that such a combination of non-linear 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 level of 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 crescendo of typically in the range of 2 to 3.5 dB per third compared to a purely logarithmic spiral shape.
  • a relative reference point for the "beginning" of the boundary wall in the circumferential direction an arbitrary reference point can be guaranteed.
  • a reference point should be selected which has a characteristic property and / or allows a 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 radial fan compartment and an air discharge duct (usually tangential to radial).
  • the proposed combination of non-linear extension and linear extension can not only provide particularly good acoustic performance , But in particular also have a very good efficiency.
  • the non-linear region can absorb the increasing air flow along the circumferential direction of the radial fan wheel, without having to come to undesirable flow phenomena in the corresponding area.
  • the radial fan housing device is designed in such a way that the radial fan mounting space expands logarithmically in at least one first wall area.
  • Such a logarithmic expansion essentially corresponds to the increase in the air mass flow in the circumferential direction of the radial fan, 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 channel.
  • This wall portion may have a substantially arbitrary shape.
  • the third wall region (the third wall regions) can be designed such that a funnel-like enlargement results.
  • the one or more third wall regions have a length which is small in relation to the first wall region and / or 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 °, 15 ° or 20 ° and / or at 85 °, 90 °, 95 °, 100 ° °, 105 °, 110 °, 115 °, 120 °, 125 °, 130 °, 135 °, 140 ° or 145 ° ends.
  • the mentioned initial or final values have proved to be particularly advantageous.
  • 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 arranged 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 optionally 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 conditioner which has at least one radial fan blower device with the structure 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 between the outside of the radial fan 3 and the boundary wall 5, a channel 6 is formed, starting from a so-called tongue 7, the cross section of the channel 6 increases steadily.
  • 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 third angle range 14 extends only over a relatively short length.
  • 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 Vietnameseab technologicalkanal 16 is formed.
  • the boundary wall 5 is formed in a larger region of the third angle portion 14 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 boundary line 9 (zero point).
  • the ordinate 19 in Fig. 2a shows the air flow 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 angular region 12 is adjoined by the third angular region 14 (transitional region 15), in which the boundary wall 5 is adapted to the following contour of an attachment component, such as, for example, the anti-theorbo 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 is the Geschwindigkestsvertellung 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, the level of activity 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)
  • Motor Or Generator Frames (AREA)
  • Air-Conditioning For Vehicles (AREA)
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 true EP2292935A2 (fr) 2011-03-09
EP2292935A3 EP2292935A3 (fr) 2013-01-30
EP2292935B1 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)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103994102A (zh) * 2014-05-07 2014-08-20 江苏大学 一种低比转速离心泵用螺旋形压水室设计方法
DE102014221955A1 (de) 2014-10-28 2016-05-12 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

Families Citing this family (4)

* 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
DE102017122987A1 (de) 2017-10-04 2019-04-04 Ebm-Papst Mulfingen Gmbh & Co. Kg Halbspiralgehäuse
US11060529B2 (en) * 2017-11-20 2021-07-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger including the same

Citations (5)

* Cited by examiner, † Cited by third party
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
US4735551A (en) * 1983-03-19 1988-04-05 Vaillant Gmbh U. Co. Radial blower
WO1990009524A1 (fr) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Ventilateur centrifuge et diffuseur a volute d'accumulation
US6273679B1 (en) * 1999-07-28 2001-08-14 Samsung Electronics Co., Ltd. Centrifugal blower

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3238913C2 (de) 1982-10-21 1985-10-03 Werner Dr. 8972 Sonthofen Röhrs Radialventilatorgehäuse
DE4143663B4 (de) * 1991-12-13 2007-03-29 Papst Licensing Gmbh & Co. Kg Radialgebläse
CA2314532C (fr) 1999-08-10 2009-10-27 Lg Electronics Inc. Ventilateur

Patent Citations (5)

* Cited by examiner, † Cited by third party
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
US4735551A (en) * 1983-03-19 1988-04-05 Vaillant Gmbh U. Co. Radial blower
WO1990009524A1 (fr) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Ventilateur centrifuge et diffuseur a volute d'accumulation
US6273679B1 (en) * 1999-07-28 2001-08-14 Samsung Electronics Co., Ltd. Centrifugal blower

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103994102A (zh) * 2014-05-07 2014-08-20 江苏大学 一种低比转速离心泵用螺旋形压水室设计方法
DE102014221955A1 (de) 2014-10-28 2016-05-12 Mahle International Gmbh Klimagerät
DE102014221955A8 (de) 2014-10-28 2016-08-04 Mahle International Gmbh Klimagerät
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

Also Published As

Publication number Publication date
EP2292935A3 (fr) 2013-01-30
DE102009033776A1 (de) 2011-01-20
EP2292935B1 (fr) 2016-11-02

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