EP1934484A1 - Module ventilateur - Google Patents

Module ventilateur

Info

Publication number
EP1934484A1
EP1934484A1 EP06793472A EP06793472A EP1934484A1 EP 1934484 A1 EP1934484 A1 EP 1934484A1 EP 06793472 A EP06793472 A EP 06793472A EP 06793472 A EP06793472 A EP 06793472A EP 1934484 A1 EP1934484 A1 EP 1934484A1
Authority
EP
European Patent Office
Prior art keywords
fan
air
module
hub
guide elements
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
EP06793472A
Other languages
German (de)
English (en)
Other versions
EP1934484B1 (fr
Inventor
Brian Havel
Harald Redelberger
Pietro De Filippis
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.)
Brose Fahrzeugteile SE and Co KG
Original Assignee
VDO Automotive AG
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 VDO Automotive AG filed Critical VDO Automotive AG
Publication of EP1934484A1 publication Critical patent/EP1934484A1/fr
Application granted granted Critical
Publication of EP1934484B1 publication Critical patent/EP1934484B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/682—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid extraction
    • 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
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection

Definitions

  • the invention relates to a fan module, in particular for the cooling of motor vehicle engines.
  • axial fans which are arranged between a radiator and an internal combustion engine of a motor vehicle.
  • Such axial fans are associated with air vanes which cover the entire outlet cross-section and serve to redirect the rotational energy of the flowing air in an axial direction, thus increasing the axial air flow.
  • FIGS. 14 and 15 schematically show a fan module 400 with a fan motor 500 arranged between a radiator 200 and an internal combustion engine 300 of a motor vehicle, wherein an axial air flow 600 is shown in FIG. 11 and an axial radial flow 700 is shown in FIG.
  • the air flow enters the fan axially and leaves it partially radially again.
  • the use of known air guide vanes leads to a reduction in the performance of the fan, since radial air currents are disturbed by the deflection of the air in the axial direction by the air guide vanes.
  • EP 0387987 A2 describes a retaining ring for receiving a Kuhlerluftermotors in a housing.
  • An inner retaining ring is placed centrally in a circular opening with the help of radial struts.
  • the radial struts are associated with additional stabilizing rings, which serve on the one hand to increase the mechanical stability of the holding device and on the other hand to deflect the Kuhlluftstromes from a radial to an axial direction and thus to increase the air efficiency.
  • US 2005/0186070 A1 shows an air arrangement in which the air passage opening is covered with air guide elements, wherein the number of air guide elements in a first region in the middle of the opening differs from the number of air guide elements in a second region at the periphery of the opening.
  • the number of air guiding elements is selected in accordance with any pressure differences over the length of the air blades in such a way that the air power is optimized.
  • An object of the present invention is to provide a Lucasermo- module that allows improved cooling of the air motor.
  • an air module is provided, in particular for the cooling of motor vehicle engines, with a Heilergehause, arranged in the Heilergehause Heilermotor (especially electric motor) and with an air motor driven Heilerrad, wherein the Heilergehause has fixed air guide elements in the region of Lufternabe the Heilerrades are arranged and only partially cover a defined by the air housing outlet cross-section.
  • a number of Lufterblatter in the Heilernabe a An air blade section for forming a Stromungso réelle formed in the manner of a fixed expansion flap for generating an increased static air pressure near the air hub.
  • the cooling of the Luftermoduls is improved by constructive changes to the Luftergehause, so the air motor retaining frame, made.
  • air guide elements are provided on the air housing, in particular in the form of air guide vanes. These air guide elements create an additional pressure difference between the front side and the rear side of the air module.
  • the otherwise unused rotational energy, or otherwise expressed the tangential portion of the air flow through the Heiler converted into static pressure.
  • the increased pressure difference between the engine front side and the engine pressure side leads to the fact that the air flow is increased by the air motor realized in an open design and thus the cooling of the air motor is significantly improved.
  • the air guide elements do not lead to a deterioration of the radial air flow, since they do not extend over the entire surface of the outlet cross section.
  • the air guide elements are arranged centrally in the outlet cross section, namely in the region of the air hub, so that the occurring at the outer periphery of the Heilerrades majority of the air flow from the air guide elements remains undisturbed.
  • the main air flow for cooling the internal combustion engine is converted in the outer area of the fan (in the area of the blade tip).
  • a number of air blades in the air hub have an air blade section for forming a flow opening, which is designed in the manner of a fixed expansion flap for generating an increased static air pressure in the vicinity of the air hub , hereby the pressure difference between the front and the back of the air module is increased.
  • a larger amount of air is passed at the gap between the air hub and the air motor, which leads to an intensification of the Venturi effect in the gap and thus to an increased Kuhlluftstrom through the Lucasermotor.
  • the cooling of the air module is improved in that structural changes are made to the Lufter- leaves.
  • a Heilerblattabterrorism is provided on each Heilerblatt in the vicinity of the Lufternabe firmly from the course of the Heilerblattes so that a kind of "split blade” (“split blade” or “slotted blade”) with a primary or main blade and a second
  • the auxiliary bucket is formed by the fixed airfoil section and the main bucket by the remaining airfoil (not shown).
  • Buoyancy aid is used at the trailing edge of Flugein.
  • the angle of the Hilfsschaufein acting air blade sections and thus the angle of attack for the air module flowing through the air is different from the angle of attack of the main blades.
  • the flow is directed by the auxiliary blade in such a way that an undesired flow separation from the air leaves is prevented can.
  • This achieves, on the one hand, that the maximum fan efficiency for the main air flow improves because the recirculation effects are reduced.
  • the tangential air speed (peripheral speed) is significantly increased compared to conventional fan modules, whereby at the same time the axial portion is increased, which leads to an increased cooling air flow.
  • improved cooling of the fan motor, including the integrated electronics is made possible.
  • the concentration of the flow openings in the area of the fan hub ensures that in the outer regions of the fan the radial ventilation effect desired on an axial-radial flow path on the rear side of the fan module is not impaired.
  • the air guide elements cover the air guide elements area of 10 to 50 percent of the outlet cross section.
  • the covered area is dependent on about 20% of the selected fan diameter, about 70% of the hub diameter and about 10% of the axial fan module distance to the engine.
  • the angular position of the air guide elements is dependent on the fan radius r.
  • the outer ends of the air guide elements are connected to each other in accordance with a further preferred embodiment of the invention via an outer ring.
  • the outer ring is preferably shaped such that the axial-radial air flow passing through is not hindered.
  • the ring is formed such that the axially incoming air is guided away radially, without a deliberate deflection (for example, with a deflection) takes place.
  • the flow openings extend radially from the fan hub radially outwards in the direction of the ends of the fan blades.
  • the radial length ("height") of the flow openings preferably corresponds to a maximum of 30 percent of the hub radius, but flow openings with a larger radial length are also possible, up to flow openings which extend over the entire radial length of the fan blade.
  • the width of the flow openings is preferably between 10 and 50 percent of the fan blade width, relative to the respective radial position. A particularly good cooling effect could be achieved if the width of the flow openings is between 35 and 45 percent of the fan blade width.
  • the angle of attack of the auxiliary blade formed by the exposed fan blade section is 25 to 70 degrees greater than the angle of attack of the main blade. A particularly good cooling effect could be achieved if the angle of attack of the auxiliary blade is 40 to 55 degrees greater than the angle of attack of the main blade.
  • the auxiliary blade formed by the exhibited fan blade section can be issued in various ways.
  • the flow opening is arranged either to the pressure side and to the suction side. Which variant is given preference, depends primarily on the available axial space.
  • the issued fan blade sections and thus the flow openings are preferably arranged in the region of the rear edge of the fan blades. This results in a particularly large flow enhancement effect.
  • the desired flow effect can be further improved.
  • the radial length of the flow openings is dimensioned such that the flow openings terminate with the outer ring of the air guide elements. Then there is a particularly effective higher tangential velocity.
  • This can be utilized by the air guide elements according to the invention arranged correspondingly on the fan housing, so that an optimal interaction of air guide elements and flow openings results.
  • Air flow through an air module (prior art) and
  • FIG. 15 shows a schematic representation of an axial-radial air flow through an air module (prior art).
  • FIGS 1 and 2 show an axial fan module 100, as seen between a radiator 200 and an internal combustion engine 300 in the engine compartment of a motor vehicle.
  • the air module 100 has a frame 101 with a circular opening 102 (Luft barntrittso réelle). This opening 102 serves as an air outlet opening for the cooling air flowing through the air module 100.
  • an engine mounting ring 104 is arranged, which serves to receive an electric motor, the air motor 105.
  • the air motor 105 drives an air wheel 1 via a drive axle 111.
  • the Heilerrad 1 has an air hub 2 and 3 Heilerblatter. With the help of Heilerrades 1, an air flow in the direction of the internal combustion engine 300 is generated. This is an axial radial flow.
  • the flow direction of the cooling air is shown with arrows 103 for the axially incoming air and arrows 103 'for the radially outflowing air.
  • a number of air guiding elements 109 in the form of air blades extend outward in the radial direction 116.
  • the radius 110 of the Lucaserrades 1 corresponds in the illustrated embodiment 1.3 times the diameter 112 of Heilernabe 2.
  • the outer ends 113 of the air guide elements 109 are connected via an outer ring 114 interconnected, which is shaped so that it does not obstruct the axially-radially passing air flow 103.
  • the outer ring 114 is connected to the frame 101 via radial struts 115 extending in the radial direction 116 in the manner of holding arms. In other words, the air motor 105 is thereby held in the frame 101.
  • the diameter 117 of the outer ring 114 is significantly smaller than the diameter 118 of the opening 102 of the frame 101, but larger than the diameter 112 of shipserabe second
  • a pressure difference between the upstream side 106 and the outlet side 107 of the air module 100 is required.
  • the arrangement of the air guide elements 109, the pressure on the outlet side 107 of the air module 100 and thus the pressure difference between upstream side 116 and exit side 107 is increased.
  • the radial flow of the cooling air in the outer regions of the Heilerrades 1 is not affected.
  • the illustrated air blade 3 has an air blade section 5 for forming a flow opening 6.
  • the Heilerblattabites 5 is designed in the manner of a fixed Sp Drardklappe and serves to generate an increased static air pressure in the vicinity of Heilernabe 2. For better clarity of Stromungsverhaltnisse the Heilstromrich- direction relative to the rotating Heilerblattern is marked with arrows 7 in the figures.
  • the airfoil 3 extends on the hub periphery 8 at an angle of attack from the leading edge 9 of the air hub 2 to the trailing edge 10 of the air hub 2.
  • the leading edge 11 of the airfoil 3 in FIG. 4 points to the viewer's right, while the rear one Edge 12 of the Vietnameseer- sheet 3 points to the left away from the viewer.
  • the extended placed Heilerblattabites 5 and thus the Stromungso réelle 6 is disposed in the region of the rear edge 12 of the airfoil 3.
  • the Stromungso réelle 6 formed by the flared Vietnamese Heilerblattabites 5 is bounded below by the hub circumference 8. In other words, the Stromungso réelle 6 goes directly from the air hub 2 radially outward in the direction of the Heilerblattendes 13.
  • Stromungso réelle 6 corresponds to 30 percent of the hub radius 15, wherein the hub radius corresponds to the distance from the hub axle 19 to the hub circumference 8.
  • the radial length 14 of the flow openings 6 is dimensioned such that the flow openings 6 terminate with the outer ring 114 of the air guiding elements 109.
  • the length 119 of the air-guiding elements 109 corresponds to the radial length 14 of the flow opening 6.
  • the width 16 of the flow opening amounts to 35 percent of the airfoil width 17.
  • the width 33 of the airfoil section 5 corresponds in the illustrated embodiment to the width 16 of the flow opening 6.
  • the angle of attack ß of the Lucaserblattabêtes 5 (auxiliary blade) is 25 degrees greater than the angle of attack of the air blade 3 (main blade).
  • the Stromungso réelle 6 is bounded outwardly in the direction of the Heilerblattendes 13 by a top surface 18 which connects the Heilerblattabites 5 with the airfoil 3.
  • a top surface 18 which connects the Heilerblattabites 5 with the airfoil 3.
  • an aerodynamically optimized flowing transition from the auxiliary blade 5 to the airfoil 3 can also be provided.
  • the width 33 of the air blade section 5 can also be smaller or larger than the width 16 of the flow opening 6.
  • the air blade sections 5 can be designed in different ways. In this case, the angle of incidence ⁇ 2 of the fan blade sections 5 acting as auxiliary blades 21 and thus the angle of attack for the air flowing through the fan module is always greater than the angle of incidence ⁇ i of the primary or main blades 20.
  • the rear edge 22 of the main blade 20 lies in the same plane as the front edge 23 of the auxiliary blade 21.
  • the leading edge 23 of the auxiliary blade 21 is negative to the trailing edge 22 of the main blade 20 in the axial direction by the distance 24, that is to say in FIG. H. in the direction of the trailing edge 10 of the fan hub 2, arranged offset.
  • the trailing edge 26 of the auxiliary blade 21 lies on the same plane as the trailing edge 22 of the main blade 20.
  • the leading edge 23 of the auxiliary blade 21 is toward the trailing edge 22 of the main blade 20 in the axial direction by the distance 25 positive, d. H. in the direction of the leading edge 9 of the fan hub 2, offset.
  • the rear edge 26 of the auxiliary blade 21 is at the rear edge 22 of FIG. 9
  • Main blade 20 in the axial direction by the distance 27 positive, d. H. in the direction of the leading edge 9 of the fan hub 2, offset.
  • the main blade 20 and the auxiliary blade 21 may also completely overlap.
  • the rear edge 26 of the auxiliary blade 21 is positioned in the axial direction by the distance 28. tively, ie in the direction of the leading edge 9 of the fan hub 2, arranged offset.
  • the distance of the rear edge 26 of the auxiliary blade 21 to the front edge 29 of the main blade 20 is shorter than the distance of the rear edge 22 of the main blade 20 to the front edge 29.
  • the front edge 23 of the auxiliary blade in the axial direction is positive over the leading edge 29 of the main blade 20 is also displaced.
  • the auxiliary blade 21 is strongly curved in the region of its rear edge 26.
  • the main blade 20 is strongly curved in the region of its rear edge 22.
  • both the main blade 20 and the auxiliary blade 21 are strongly curved in the region of their rear edges 22, 26.
  • the strong curvature 32 always serves to increase the airflow.
  • chord length 30 of the main blade 20 is always greater than the chord length 31 of the auxiliary blade 21, cf.
  • the chord length 30 of the main blade 20 may also be smaller than or equal to the chord length 31 of the auxiliary blade 21.
  • the concrete dimensioning depends strongly on the respective purpose of the application.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • External Artificial Organs (AREA)

Abstract

L'invention concerne un module ventilateur, servant en particulier à refroidir des moteurs de véhicules automobiles. Selon l'invention, pour améliorer le refroidissement du moteur du ventilateur, le carter (101) du ventilateur dans lequel est disposé le moteur (105) présente des éléments fixes de guidage d'air (109) qui sont disposés au niveau d'un moyeu (2) de la roue (1) du ventilateur, laquelle est entraînée par le moteur (105) du ventilateur, et qui recouvrent seulement partiellement une section de sortie (102, 118) définie par le carter (101) du ventilateur.
EP06793472A 2005-09-27 2006-09-13 Module ventilateur Not-in-force EP1934484B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005046180A DE102005046180B3 (de) 2005-09-27 2005-09-27 Lüftermodul
PCT/EP2006/066309 WO2007036431A1 (fr) 2005-09-27 2006-09-13 Module ventilateur

Publications (2)

Publication Number Publication Date
EP1934484A1 true EP1934484A1 (fr) 2008-06-25
EP1934484B1 EP1934484B1 (fr) 2009-03-04

Family

ID=37460293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06793472A Not-in-force EP1934484B1 (fr) 2005-09-27 2006-09-13 Module ventilateur

Country Status (6)

Country Link
US (1) US8100665B2 (fr)
EP (1) EP1934484B1 (fr)
CN (1) CN100554701C (fr)
AT (1) ATE424510T1 (fr)
DE (2) DE102005046180B3 (fr)
WO (1) WO2007036431A1 (fr)

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ITBO20070776A1 (it) * 2007-11-23 2009-05-24 Spal Automotive Srl Unita' di ventilazione in particolare per autoveicoli.
ITMI20130791A1 (it) * 2013-05-14 2014-11-15 Cofimco Srl Ventilatore assiale
US9869190B2 (en) 2014-05-30 2018-01-16 General Electric Company Variable-pitch rotor with remote counterweights
US10072510B2 (en) 2014-11-21 2018-09-11 General Electric Company Variable pitch fan for gas turbine engine and method of assembling the same
US10100653B2 (en) 2015-10-08 2018-10-16 General Electric Company Variable pitch fan blade retention system
DE102016119916A1 (de) 2016-10-19 2018-04-19 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilator mit Ventilatorrad und Leitrad
US11391295B2 (en) * 2017-05-22 2022-07-19 Fujitsu General Limited Propeller fan
JP6957971B2 (ja) * 2017-05-22 2021-11-02 株式会社富士通ゼネラル プロペラファン
DE102017116352A1 (de) * 2017-07-20 2019-01-24 Brose Fahrzeugteile Gmbh & Co. Kg, Würzburg Kühlerlüftermodul
JP6583397B2 (ja) * 2017-12-05 2019-10-02 株式会社富士通ゼネラル プロペラファン
JP6696525B2 (ja) * 2018-03-22 2020-05-20 株式会社富士通ゼネラル プロペラファン
JP7088307B2 (ja) * 2018-11-30 2022-06-21 株式会社富士通ゼネラル プロペラファン
CN113167291B (zh) * 2018-11-30 2023-05-09 富士通将军股份有限公司 螺旋桨式风扇
FR3093141B1 (fr) * 2019-02-25 2021-01-22 Valeo Systemes Thermiques Groupe moto-ventilateur pour vehicule automobile
US11674435B2 (en) 2021-06-29 2023-06-13 General Electric Company Levered counterweight feathering system
US11795964B2 (en) 2021-07-16 2023-10-24 General Electric Company Levered counterweight feathering system
US12601271B2 (en) 2022-10-21 2026-04-14 General Electric Company Variable pitch fan of a gas turbine engine

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Also Published As

Publication number Publication date
DE502006003033D1 (de) 2009-04-16
CN101278128A (zh) 2008-10-01
DE102005046180B3 (de) 2007-03-22
US8100665B2 (en) 2012-01-24
WO2007036431A1 (fr) 2007-04-05
CN100554701C (zh) 2009-10-28
US20090151911A1 (en) 2009-06-18
EP1934484B1 (fr) 2009-03-04
ATE424510T1 (de) 2009-03-15

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