EP2107251A1 - Boîtier de ventilateur - Google Patents

Boîtier de ventilateur Download PDF

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Publication number
EP2107251A1
EP2107251A1 EP09004559A EP09004559A EP2107251A1 EP 2107251 A1 EP2107251 A1 EP 2107251A1 EP 09004559 A EP09004559 A EP 09004559A EP 09004559 A EP09004559 A EP 09004559A EP 2107251 A1 EP2107251 A1 EP 2107251A1
Authority
EP
European Patent Office
Prior art keywords
shapes
fluid
fluidleitvorrichtung
blower
receiving space
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.)
Ceased
Application number
EP09004559A
Other languages
German (de)
English (en)
Inventor
Matthias Lang
Nikolaus Zipf
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 EP2107251A1 publication Critical patent/EP2107251A1/fr
Ceased legal-status Critical Current

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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
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials 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
    • F04D29/4226—Fan casings

Definitions

  • the invention relates to a fan housing for a radial fan device. Furthermore, the invention relates to a blower device with such a blower housing.
  • Blowers are always needed if an air flow is to be generated artificially. It does not matter whether it is to move air into a room, to move it out of a room, or to move air from one room to another. Of course, instead of air, it may also be another gas, which may also contain, for example, drops of liquid (mist) and / or solid particles (smoke).
  • blowers there are a variety of characteristics, such as the maximum air flow rate, the pressure difference generated, the energy requirement of the blower, the available energy form (eg electrical Energy or the mechanical energy of a crankshaft), the space required by the blower, the insensitivity to contamination, the resistance to aggressive media and the noise generated during operation of the blower.
  • characteristics such as the maximum air flow rate, the pressure difference generated, the energy requirement of the blower, the available energy form (eg electrical Energy or the mechanical energy of a crankshaft), the space required by the blower, the insensitivity to contamination, the resistance to aggressive media and the noise generated during operation of the blower.
  • blower devices are required in a single technical device for their operation. It is also possible that at different locations of such a technical device different priorities with respect to the characteristics of the blower used are present.
  • An example of such a technical device in which a plurality of blowers of different designs are used, are motor vehicles, in particular land-based motor vehicles.
  • automobiles include a fan that, at higher load conditions, causes additional cooling of the coolant radiator, oil cooler, and / or condenser of an automotive air conditioning system by exposure to an airflow.
  • a fan that, at higher load conditions, causes additional cooling of the coolant radiator, oil cooler, and / or condenser of an automotive air conditioning system by exposure to an airflow.
  • it is particularly important to have the highest possible air throughput with the smallest possible space required.
  • Another fan is found in the air conditioning of the motor vehicle.
  • the supplied or circulated air is thereby required (as far as realized in the specific form of the motor vehicle air conditioning) heated by a radiator, cooled by an evaporator (and dehumidified), cleaned by filters and distributed by air distributor on different exhaust nozzles in the motor vehicle interior.
  • a particularly low operating noise is especially relevant in the blowers used there, a particularly low operating noise. This applies in particular to the part of the operating noise which is emitted into the motor vehicle interior.
  • the type of operating noise is also relevant.
  • operating noise in certain, narrow frequency intervals are perceived as unpleasant (tonal noise, colloquially also referred to as “howling"), whereas the most uniform possible noise over all frequency ranges (so-called “white noise”) is tolerated.
  • white noise the most uniform possible noise over all frequency ranges
  • low-frequency operating noise in particular those which are in the range of about 50 Hz to 500 Hz, in particular in the range of about 75 Hz to 200 Hz, perceived as particularly unpleasant.
  • ANR active noise reduction
  • the object of the invention is thus to propose a blower housing for radial fans, which has an improved noise emission behavior. Furthermore, the object of the invention is to propose a blower device with an improved noise emission behavior.
  • blower housing for a radial fan device which has at least one radial fan receiving space with at least one fluid inflow channel, at least one fluid outflow channel and at least one fluid guide device such that the extent of at least one fluid guide device is less than the extent of the fluid channel in which the fluid guide device is arranged.
  • a fluid channel is to be understood in particular as meaning a fluid inflow channel and / or a fluid outflow channel.
  • the inventors have surprisingly discovered that with many blowers, with regard to the operating noise generated, it is not only harmless to make the "length" of a fluid guiding device shorter than corresponds to the dimension of the fluid channel. But it can rather come in comparison with air guide elements, which pass through the fluid channel substantially completely, to reduced operating noise.
  • the "shortening" of the air guiding devices can also lead to a reduction of the air attack cross section, so that the flow resistance facing the air flow can be reduced. This, in turn, can result in reduced fan performance, which can further reduce noise emissions. Even if a relatively small shortening of the length of the Fluidleitvoriques (s) can lead to a significant decrease in noise emission, it has proved to be advantageous if the expansion of the Fluidleitvoroplasty less than or equal to 75%, 70%, 66.67%, 65%, 60%, 55%, 50%, 45%, 40%, 35%, 33.33%, 30%, 25%, 20%, 15% , 10% and / or 5% of the corresponding extent of the air flow channel.
  • the extent of a fluid guiding device is usually to be understood as meaning its width in the transverse direction of the direction of fluid flow. However, it may additionally or alternatively be the case width, the case height, the channel height and / or other dimensions.
  • the thickness of the corresponding fluid guide device can be designed analogously to known Fluidleitvoriquesen.
  • the proposed device In addition to the usually observable reduction in the total noise emission, the proposed device also often causes a reduction of the particularly disturbing low-frequency noise component, in particular in the frequency range of 50 Hz ⁇ f ⁇ 500 Hz, especially in the frequency range of 75 Hz ⁇ f ⁇ 200 Hz are in the context of the present description not only conventional radial fan, in which the air is supplied through the inside of a fan drum, and the air discharge in the tangential and / or radial direction, but also other designs, such as in particular cross-flow fan, in which both air supply and Air delivery in the tangential and / or radial direction, to understand. Mixed forms are of course conceivable.
  • the radial fan compartment may be particularly in the case of "classic" radial fans in the form of a fan spiral.
  • the fluid outflow channel may in particular be arranged at an angle relative to the tangential direction of the radial fan receiving space. In particular, angle ranges of 5 ° to 40 °, 10 ° to 35 °, 15 ° to 30 ° and 20 ° to 25 ° between the tangential direction and the direction of the Fluidabströmkanals can be particularly advantageous.
  • a meaningful development of the blower housing may result if at least one fluid guiding device is arranged in a fluid outflow channel.
  • Tests have shown that the noise cancellation may be particularly effective when at least one of the Fluidleitvoriquesen is arranged in a Fluidabströmkanal. This can lead to an interaction with otherwise particularly strongly noise-causing fluid which has been accelerated by the fan. This can cause a noticeably lower and / or more pleasant operating noise of the blower.
  • At least one fluid guiding device is arranged in the area of a radial fan receiving space and / or adjacent to a radial fan receiving space in the fan housing.
  • Such a (optionally additional) arrangement of a fluid-conducting device or a plurality of fluid-conducting devices can also result in particularly great noise-reduction effects.
  • the positioning region may be an area that lies between a region of the so-called fan spiral (or a region corresponding thereto in the case of another embodiment of the fan housing) and the fan wheel.
  • An arrangement of the fluid guiding device (s) has proven to be particularly advantageous, in which the fluid guiding device (or the fluid guiding devices) tends to be arranged closer and / or immediately adjacent to the housing wall (in particular the fan spiral).
  • the expansion of the at least one fluid guiding device is smaller in a direction parallel to the axial direction of the radial fan receiving space and / or in a direction perpendicular to the axial direction of the radial fan receiving space and / or in a direction parallel to an adjacent wall of the fluid channel is, as the extent of the fluid channel in which the fluid guide is arranged. With such an orientation usually the best noise reduction effects can be effected.
  • a usually occurring narrow fluid passage cross section between the fluid guide device and the wall of the fluid channel seems to have an advantageous effect on the noise emission behavior.
  • the distance between wall and fluid guiding device should not be more than (less than) 30%, 25%, 20%, 15%, 10% or 5% of the channel width.
  • blower housing results when at least one fluid channel, in particular at least one fluid outlet channel, extends at least partially along a direction lying in the radial plane of the radial fan receiving space and / or at least one fluid channel, in particular at least one fluid inflow channel at least in regions along a plane perpendicular to the radial plane the radial fan receiving space lying direction.
  • fluid directors are particularly effective when implemented in conjunction with the "classic" radial fan assembly.
  • angles are also possible which deviate slightly from the proposed "ideal shape", in particular if the deviation is less than 10 °, particularly preferably less than 5 °.
  • the air guide elements are arranged in a certain (preferably variable) angle of attack with respect to the regular Beeranströmeuros.
  • blower housing results when at least one fluid guide device is arranged in an overflow region which is close to an approach of fluid inflow channel and fluid outflow channel and / or in the region of a connecting edge of two fluid channel walls, in particular in the region between inlet frame and impeller or frame gap located.
  • the areas mentioned are usually characterized in that particularly large pressure differences, in particular in relation to the other areas of the blower device, can occur in their area.
  • the use of the Fluidleitvoriquesen at the proposed location therefore proves to be particularly effective in the rule.
  • the overflow region may in particular be the region in which the fluid supply channel of the fan cowl and the fluid discharge channel lie directly adjacent to one another. Due to never completely avoidable leaks in practice these are usually fluidly connected to a certain extent.
  • the overflow region may in particular be the (acute-angled) connection region between the radial fan receiving space and the fluid discharge channel. Also in this area are usually very high pressure differences and there is due to sealing problems in practice before a certain fluidic connection.
  • the fan housing is designed such that at least one Fluidleitvoriques is arranged at an angular distance from the region of a connecting edge of two fluid channel walls, between 10 ° and 60 °, preferably 20 ° to 50 °, more preferably 30 ° to 40 °, in particular 35 °.
  • the term "area of a connecting edge of two fluid channel walls" can be understood in particular as a housing tongue which separates a fluid drain passage from a radial fan receiving space.
  • a housing tongue is often rounded, it is of course also possible to use a radial center (for example, center of a circle, ellipse focal point or the like) of the housing tongue as a reference region (the same can of course also apply to other fluid channel connections).
  • said angular ranges have proven to be particularly advantageous, in particular with respect to a particularly large noise reduction capacity.
  • the angle range can be understood to mean that a central region of one or more fluid-conducting elements at least approximately coincides with an angle limb.
  • one or more fluid guide elements can lie substantially completely within the stated angular range.
  • other definitions are conceivable.
  • At least one fluid guide device has a shape having one and / or more shape features taken from the group, the wing-like shapes, teardrop-shaped shapes, ellipse-like shapes, plate-like shapes, rectangular shapes, triangular-shaped shapes, trapezoidal shapes Shapes, rounded shapes, shapes with convex boundary edges, shapes with concave boundary edges, and shapes with wavy boundary edges.
  • the proposed forms have proven to be particularly suitable in the previous experiments.
  • the convex or concave boundary edges can be arranged especially on windward or leeward areas of the fluid guide device.
  • At least one fluid guiding device is adjustable, in particular rotatable and / or displaceable.
  • the fan housing can be adapted to the respective operating condition.
  • the optimal shape and arrangement of the fluid directing device (s) also changes with changing operating conditions.
  • the adjustable arrangement of the fluid-guiding device (s) it is therefore usually possible to cover a larger operating range.
  • the main plane of at least one fluid guiding device runs parallel to the axial direction of the radial fan receiving space and / or is perpendicular to the axial direction of the radial fan receiving space.
  • the fan housing is provided with a plurality of fluid guide devices, in particular with an even number of fluid guide devices, which are preferably arranged symmetrically.
  • the positive effects of the individual Fluidleitvoriquesen can at least partially add, possibly even mutually positively influence, so that in the sum of a further enhanced noise reduction effect results.
  • the symmetrical arrangement of the fluid guiding devices may relate in particular to their orientation and / or arrangement with respect to the corresponding fluid channel.
  • a blower device in particular a blower device for motor vehicles, preferably a blower device for ventilating a motor vehicle interior, is proposed, which has at least one radial fan and which has a blower housing with the structure described above.
  • a blower device can be developed in an analogous manner as described with respect to the blower housing be and has the advantages and properties described in an analogous manner.
  • Fig. 1 is shown in a schematic, perspective view of a blower 1 of an automotive air conditioning system with a radial fan 3.
  • the radial fan 3 is accommodated in a receiving space suitable for radial fan wheels 3, a so-called fan spiral 2.
  • a so-called fan spiral 2 For illustrative reasons is in Fig. 1 only a partial section of the blower 1 shown.
  • Fig. 1 is to recognize on the right side of the tongue 4, which separates the air outlet channel 5 of the fan spiral 2.
  • the air delivered by the radial fan 3 passes through the air outlet channel 5 and is discharged for example via suitable air distributor and Heilausströmerdüsen in the motor vehicle interior and possibly pre-processed in a conventional manner with the help of radiators, evaporators and filters, if not already in the flow direction seen before the radial fan 3 is done.
  • a frame 7 is provided, on which a frame collar 8 is fixed, which extends a little way into the inner cavity 9 of the radial fan 3 into it.
  • an air guide 10 Adjacent to the air inlet side 6 of the radial fan 3 luv restaurant an air guide 10 is disposed in front of the tongue 4.
  • the air guide 10 is attached to a support rod 11.
  • the support rod 11 is connected to (not shown here) servomotors, so that the air guide 10 on the one hand about the axis of the support rod 11 pivoted (double arrow A) can be on the other hand moved (double arrow B) can be.
  • the air guiding element 10 can be placed closer to the tongue 4 or farther away from the tongue 4 so that its angle of attack to the incoming air or its distance from the tongue 4 can be adapted to the respective operating conditions.
  • the air guide element 10 is formed with a triangular shape and plate-like cross-section. However, other shapes may be used.
  • the height of the air guide element 10 is approximately one third of the total height of the air outlet channel 5.
  • the height of the air outlet channel 5 corresponds (in the illustrated embodiment) (approximately) to the height of the fan spiral 2, the height of the radial fan 3 or the height of the tongue 4.
  • the air guide element 10 despite its small dimensions effective noise reduction, especially in the low-frequency range cause.
  • Fig. 2 is that in Fig. 1 see fan 1 shown in a plan view from above. In other words, the view corresponds to the viewing direction from the air inlet side 6.
  • FIG. 3 is that in the Fig. 1 and Fig. 2 shown blower 1 additionally shown in a side view. Furthermore, in Fig. 3 the drive motor 12 of the radial fan 3 and the drive shaft 13 of the radial fan 3 shown.
  • blower housing 20 are not shown for reasons of better visibility.
  • FIG. 4 For example, several different conceivable forms for air guiding elements 10a-10e are shown.
  • substantially triangular air guide element 10a is the air flow facing windward edge 14a of the Lucassftelement 10a convexly curved.
  • the air flow facing Luvkante 14b of in Fig. 4b illustrated air guide element 10b concave.
  • illustrated air guide 10c is it is a kind of mixed form of convex 14a and concave 14b windward edge, so that a "wave-shaped" windward edge 14c results.
  • a rectangular basic shape 10d or a trapezoidal basic shape 10e can be used for the air guide.
  • the windward edge 14d, 14e not only (as shown in the drawing) can be rectilinear, but also convex, concave or wavy.
  • the sill edge 15a-e or one or more side edges 16a-e of the respective air guide element 10a-e may be convex, concave and / or wave-shaped.
  • FIG. 5 By way of example, different conceivable cross-sectional shapes 17g-j of air guiding elements 10g-j are shown.
  • the cross-sectional shape 17g-j for example, plate-like 17g, drop-like 17h, wing profile-like 17i or elliptical 17 j be formed.
  • FIG. 6 a second embodiment of a blower 18 is shown.
  • Fig. 7 shows that in Fig. 6 illustrated fan 18 seen from the side.
  • the blower 18 largely corresponds to the basic construction in FIG Fig. 1 shown blower 18.
  • the air guide element 19 is formed and arranged differently in the present blower 18. In the illustrated embodiment, it is a horizontally disposed air guide 19, which is arranged luv chart the tongue 4, and about half as wide as the width of the Heilausströmkanals 5 corresponds.
  • blower 1 In analogy to in Fig. 1 illustrated blower 1 is also present, the air guide 19 rotatably (double arrow C) and slidably arranged (double arrow B), so that it can be adapted to different operating conditions of the blower 18.
  • FIGs. 8 and 9 is a further, third embodiment of a blower 21 is shown. It shows Fig. 8 the blower 21 in a schematic plan view from above, while Fig. 9 the arrangement of the air guide elements 22, 23 of the blower 21 in the relevant air guide region of the blower housing 20 is illustrated.
  • the blower 21 in the present case two air guide elements 22, 23. Due to the in Fig. 8 selected perspective, only one of the two air guide elements 22, 23 (namely, the upper air guide 22) can be seen.
  • the air guide elements 22, 23 are each mounted on a support rod 11 and can be rotated via an actuator (not shown here) (double arrow C). In this way, the air guide elements 22, 23 have a variable angle of attack ⁇ 1 , ⁇ 2 with respect to the Lucasanströmcardi 27.
  • the two air guide elements 22, 23 are each provided with a separate actuator, so that the angle of attack ⁇ 1 , ⁇ 2 can be chosen to be different in size.
  • the angle of attack ⁇ 1 , ⁇ 2 can be chosen to be different in size.
  • the distance a 1 , a 2 of the two air guide elements 22, 23 to the respectively adjacent channel wall 24, 25 is in each case selected to be the same size and is 0.3 times the channel width B (in the presently illustrated embodiment). Distance between upper channel wall 24 and lower channel wall 25).
  • the distance a 1 , a 2 chosen in the present exemplary embodiment has proven particularly advantageous in practice as acoustically.
  • the arrangement of the air guide elements 22, 23 relative to the tongue 4 is particularly in Fig. 8 seen.
  • the air guide elements 22, 23 are arranged lying within the fan spiral 2, between Radiellularerrad 3 and blower housing 20.
  • the air guide elements 22, 23 are arranged leeward relative to the tongue 4.
  • the tongue 4 is rounded, serves as a reference point for a first leg 27 of the angular range ⁇ of the circle center 26 of the rounded portion of the tongue 4.
  • the axis of rotation 28 of Radial fan 3 which corresponds approximately to the center of the bent portion of the housing spiral 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP09004559A 2008-04-02 2009-03-30 Boîtier de ventilateur Ceased EP2107251A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008017121A DE102008017121A1 (de) 2008-04-02 2008-04-02 Gebläsegehäuse

Publications (1)

Publication Number Publication Date
EP2107251A1 true EP2107251A1 (fr) 2009-10-07

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Family Applications (1)

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EP09004559A Ceased EP2107251A1 (fr) 2008-04-02 2009-03-30 Boîtier de ventilateur

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EP (1) EP2107251A1 (fr)
DE (1) DE102008017121A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2333348A2 (fr) * 2009-11-23 2011-06-15 Behr GmbH & Co. KG Boîtier de ventilateur radial
EP2388159A3 (fr) * 2010-05-17 2014-09-03 Behr GmbH & Co. KG Climatisation de véhicule automobile
EP2500582A4 (fr) * 2009-11-09 2017-10-18 Mitsubishi Heavy Industries, Ltd. Ventilateur centrifuge multi-aubes et climatiseur l'utilisant

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1854515U (de) 1959-11-12 1962-07-05 Nikolaus Laing Heizgeblaese.
CH399645A (de) 1960-01-18 1965-09-30 Eck Bruno Ing Dr Querstromgebläse
CH461008A (de) * 1965-09-23 1968-08-15 Zenkner Kurt Ing Dr Brenner
DE2929140A1 (de) 1979-07-19 1981-02-12 Kurt Dr Ing Zenkner Gehaeuse fuer ein querstromgeblaese, insbesondere zur verwendung bei dachventilatoren
EP0341553A1 (fr) * 1988-05-09 1989-11-15 Gec Alsthom Sa Pompe centrifuge
EP0350427A2 (fr) * 1988-07-05 1990-01-10 Pratt & Whitney Canada, Inc. Pales d'entrée d'un compresseur radial à débit variable
EP0466983A1 (fr) * 1990-07-16 1992-01-22 Crosslee Plc Suppression de bruit
EP0915258A1 (fr) * 1997-11-10 1999-05-12 Carrier Corporation Ventilateur à courant transversal avec stabilisateur de courant
EP1022469A1 (fr) * 1999-01-20 2000-07-26 PUNKER GmbH & CO. Soufflante radial

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JPS63198798A (ja) * 1987-02-13 1988-08-17 Hitachi Ltd タ−ボ形流体機械の羽根付デイフユ−ザ
DE3706772A1 (de) * 1987-03-03 1988-09-15 Gebhardt Gmbh Wilhelm Ventilatoreinheit und verfahren zur herstellung der leitschaufeln einer solchen ventilatoreinheit
JPH07103874B2 (ja) * 1990-03-14 1995-11-08 株式会社日立製作所 斜流圧縮機
DE10250302B4 (de) * 2002-10-29 2004-12-09 Bayerische Motoren Werke Ag Drallerzeugungseinrichtung für einen Verdichter
TWI235205B (en) * 2003-10-31 2005-07-01 Delta Electronics Inc Centrifugal fan with stator blades

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1854515U (de) 1959-11-12 1962-07-05 Nikolaus Laing Heizgeblaese.
CH399645A (de) 1960-01-18 1965-09-30 Eck Bruno Ing Dr Querstromgebläse
DE1403545A1 (de) * 1960-01-18 1968-11-07 Eck Dr Ing Bruno Querstromgeblaese,bei dem zur Fuehrung der Durchsatzstroemang dieser im Innern des Laeufers das Feld eines Potentialwirbels ueberlagert wird
CH461008A (de) * 1965-09-23 1968-08-15 Zenkner Kurt Ing Dr Brenner
DE1501958A1 (de) 1965-09-23 1969-11-20 Zenkner Dipl Ing Kurt Brennet,z.B. Gasbrenner oder nach dem Prinzip der Druckzerstaeubung arbeitender OElbrenner
DE2929140A1 (de) 1979-07-19 1981-02-12 Kurt Dr Ing Zenkner Gehaeuse fuer ein querstromgeblaese, insbesondere zur verwendung bei dachventilatoren
EP0341553A1 (fr) * 1988-05-09 1989-11-15 Gec Alsthom Sa Pompe centrifuge
EP0350427A2 (fr) * 1988-07-05 1990-01-10 Pratt & Whitney Canada, Inc. Pales d'entrée d'un compresseur radial à débit variable
EP0466983A1 (fr) * 1990-07-16 1992-01-22 Crosslee Plc Suppression de bruit
EP0915258A1 (fr) * 1997-11-10 1999-05-12 Carrier Corporation Ventilateur à courant transversal avec stabilisateur de courant
EP1022469A1 (fr) * 1999-01-20 2000-07-26 PUNKER GmbH & CO. Soufflante radial

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2500582A4 (fr) * 2009-11-09 2017-10-18 Mitsubishi Heavy Industries, Ltd. Ventilateur centrifuge multi-aubes et climatiseur l'utilisant
EP2333348A2 (fr) * 2009-11-23 2011-06-15 Behr GmbH & Co. KG Boîtier de ventilateur radial
EP2333348A3 (fr) * 2009-11-23 2013-01-30 Behr GmbH & Co. KG Boîtier de ventilateur radial
EP2388159A3 (fr) * 2010-05-17 2014-09-03 Behr GmbH & Co. KG Climatisation de véhicule automobile

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DE102008017121A1 (de) 2009-10-08

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