EP1934484B1 - Module ventilateur - Google Patents

Module ventilateur Download PDF

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Publication number
EP1934484B1
EP1934484B1 EP06793472A EP06793472A EP1934484B1 EP 1934484 B1 EP1934484 B1 EP 1934484B1 EP 06793472 A EP06793472 A EP 06793472A EP 06793472 A EP06793472 A EP 06793472A EP 1934484 B1 EP1934484 B1 EP 1934484B1
Authority
EP
European Patent Office
Prior art keywords
fan
blade
hub
module
air
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
EP06793472A
Other languages
German (de)
English (en)
Other versions
EP1934484A1 (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
Continental Automotive GmbH
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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
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

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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
    • F04D29/26—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 are known from the prior art, 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 12 schematically shows a fan module 400 arranged between a radiator 200 and internal combustion engine 300 of a motor vehicle with a fan motor 500, wherein FIG. 11 an axial air flow 600 and in FIG. 12 an axial-radial air flow 700 is shown.
  • FIG. 11 an axial air flow 600 and in FIG. 12 an axial-radial air flow 700 is shown.
  • 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 radiator fan motor in a housing.
  • an inner retaining ring is placed with the aid of radial struts in the middle in a circular opening.
  • 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 thede povertystromes.von a radial in an axial direction and thus to increase the L compellingereffizienz.
  • US 2005/0186070 A1 shows a fan assembly 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 center 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 guide elements is selected according to any pressure differences over the length of the fan blades so that the fan performance is optimized.
  • An object of the present invention is to provide a fan module that enables improved cooling of the fan motor.
  • a fan module is provided, in particular for the cooling of motor vehicle engines, with a fan housing, with a fan housing arranged in the fan motor (in particular electric motor) and with a driven by the fan motor fan, wherein the fan housing has fixed air guide elements in the region of a fan hub of Fan are arranged and only partially cover a defined by the fan housing outlet cross-section.
  • fan blades are arranged, with a number of fan blades in the fan hub a A fan 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 fan hub.
  • the cooling of the fan module is improved by constructive changes to the fan housing, ie the frame holding the fan motor.
  • air guide elements are provided on the fan housing, in particular in the form of air guide vanes. With these air guide elements, an additional pressure difference between the front and the rear of the fan module is generated.
  • the otherwise unused rotational energy or in other words the tangential portion of the air flow through the fan, is converted into static pressure.
  • the increased pressure difference between the front of the engine and the rear of the engine means that the air flow is increased by the open-type fan motor and thus the cooling of the fan 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 fan hub, so that the part of the air flow occurring at the outer circumference of the fan wheel remains undisturbed by the air guide elements.
  • 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 fan blades in the region of the fan hub have a fan 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 fan hub. hereby the pressure difference between the front and the back of the fan module is increased. As a result, a larger amount of air is guided past the gap between the fan hub and the fan motor, which leads to an intensification of the Venturi effect in the gap and thus to an increased flow of cooling air through the fan motor.
  • the cooling of the fan module is improved by constructive changes are made to the fan blades.
  • a fan blade section fixedly mounted from the course of the fan blade is provided, so that a type of "split blade” or “slotted blade” with a primary or main blade and a secondary blade or auxiliary blade arises.
  • the auxiliary blade is formed by the fixedly exhibited fan blade section and the main blade by the (not flared) remaining fan blade.
  • the terms "split blade” and “split fan blade” are used interchangeably.
  • This embodiment is based on the use of such split fan blades in axial fans.
  • the operating principle of such an exposed and serving as an auxiliary blade fan blade section substantially corresponds to that of a Sp Drklappe, as used for example in aviation as a buoyancy aid at the trailing edge of wings.
  • On the fan blades caused by the exhibition of the fan blade sections flow openings according to the invention.
  • the angle of attack of the auxiliary blades acting fan blade sections and thus the angle of attack for the air flowing through the fan module is different from the angle of attack of the main blades.
  • the flow is directed by the auxiliary blades in such a way that undesired flow separation from the fan blades 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 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 angle of attack of the air guide elements changes in the radial direction and in such a way that the best possible recovery of the tangential air energy is possible for the respective air vector and its direction.
  • 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 directly 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 there are also flow openings with a larger radial length 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 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 used by the correspondingly arranged on the fan housing, inventive air guide elements, so that there is an optimal interaction of air guide elements and flow openings.
  • FIG. 1 and 2 show an axial fan module 100, as it is arranged between a radiator 200 and an internal combustion engine 300 in the engine compartment of a motor vehicle.
  • the fan module 100 has a frame 101 with a circular opening 102 (air passage opening). This opening 102 serves as an air outlet opening for the cooling air flowing through the fan module 100.
  • an engine mounting ring 104 is arranged, which serves to receive an electric motor, the fan motor 105.
  • the fan motor 105 drives a fan 1 via a drive axle 111.
  • the fan 1 has a fan hub 2 and fan blades 3. With the help of the fan wheel 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 fan wheel 1 in the illustrated embodiment corresponds to 1.3 times the diameter 112 of the fan hub 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 fan 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 the fan hub second
  • a pressure difference is required between the inflow side 106 and the exit side 107 of the fan module 100.
  • the arrangement of the air guide elements 109, the pressure on the outlet side 107 of the fan module 100 and thus the pressure difference between the upstream side 116 and exit side 107 is increased.
  • the radial flow of the cooling air in the outer regions of the fan wheel 1 is not affected.
  • FIG. 4 and 5 is a part of the fan 1 shown.
  • the illustrated fan blade 3 has a fan blade section 5 for forming a flow opening 6.
  • the fan blade section 5 is designed in the manner of a fixed expansion flap and serves to generate an increased static air pressure in the vicinity of the fan hub 2.
  • the air flow direction is shown relative to the rotating fan blades with arrows 7 in the figures.
  • the fan blade 3 extends on the hub circumference 8 at an angle of attack from the front edge 9 of the fan hub 2 to the trailing edge 10 of the fan hub 2.
  • the front edge 11 of the fan blade 3 in FIG FIG. 4 to the right toward the viewer, while the rear edge 12 of the fan blade 3 faces away from the viewer to the left.
  • the issued Fan blade section 5 and thus the flow opening 6 is arranged in the region of the rear edge 12 of the fan blade 3.
  • the flow opening 6 formed by the exposed fan blade section 5 is bounded downwardly by the hub periphery 8. In other words, the flow opening 6 goes radially outward radially from the fan hub 2 in the direction of the fan blade end 13.
  • the radial length (“height") 14 of the flow opening 6 corresponds to 30 percent of the hub radius 15, the hub radius being the distance from the hub axis 19 corresponds 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. In other words, the length 119 of the air guide elements 109 corresponds to the radial length 14 of the flow opening 6.
  • the width 16 of the flow opening is 35 percent of the fan blade width 17.
  • the width 33 of the fan blade section 5 corresponds in the illustrated embodiment, the width 16 of the flow opening 6.
  • the angle of attack ⁇ of the fan blade section 5 (auxiliary blade) is 25 degrees larger than the angle of attack of the fan blade 3 (main blade).
  • the flow opening 6 is bounded outward in the direction of the fan blade end 13 by a cover surface 18, which connects the fan blade section 5 with the fan blade 3. Instead of the top surface 18, however, an aerodynamically optimized flowing transition from the auxiliary blade 5 to the fan blade 3 may be provided.
  • the width 33 of the fan blade section 5 may also be smaller or larger than the width 16 of the flow opening 6.
  • the issued fan blade section 5 secondary or auxiliary blade 21 can be issued in various ways.
  • the angle of attack ⁇ 2 acting as the auxiliary blades 21 fan blade sections 5 and thus the angle of attack for the air flowing through the fan module is always greater than the angle of attack ⁇ 1 of the primary or main blades 20th
  • 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 front edge 23 of the auxiliary blade 21 is offset relative to the rear edge 22 of the main blade 20 in the axial direction by the distance 24 negative, ie in the direction of the trailing edge 10 of the fan hub 2.
  • 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 positive to the trailing edge 22 of the main blade 20 in the axial direction by the distance 25, ie 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 positive in the axial direction by the distance 28, ie in the direction of the leading edge 9 of the fan hub 2, 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.
  • FIG. 11 In a sixth embodiment ( FIG. 11 ) is - similar to the FIGS. 6 to 10 ⁇ the auxiliary blade 21 in the region of its rear edge 26 is strongly curved.
  • the main blade 20 In a seventh embodiment ( FIG. 12 ), 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 in the region of their rear edges 22, 26 is strongly curved.
  • 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. FIG. 10 , However, according to the invention, the chord length 30 of the main blade 20 may be less 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)

Claims (10)

  1. Module ventilateur (100), notamment pour le refroidissement de moteurs de véhicules automobiles, avec une enveloppe de ventilateur (101), avec un moteur de ventilateur (105) placé dans l'enveloppe de ventilateur (101) et avec une roue de ventilateur (1) entraînée par le moteur de ventilateur (105), l'enveloppe de ventilateur (101) comportant des éléments de canalisation d'air fixes (109) qui sont placés dans la zone d'un moyeu de ventilateur (2) de la roue de ventilateur (1) et qui couvrent seulement partiellement une section transversale de sortie (102, 118) définie dans l'enveloppe de ventilateur (101), caractérisé en ce que des pales de ventilateur (3) sont agencées sur le moyeu de ventilateur (2), un certain nombre de pales de ventilateur (3) comportant dans la zone du moyeu de ventilateur (2) un tronçon de pale de ventilateur (5) qui est destiné à la formation d'un orifice d'écoulement (6) et qui est conçu à la manière d'un volet d'écartement fixe pour la production d'une pression d'air statique accrue à proximité du moyeu de ventilateur (2).
  2. Module ventilateur (100) selon la revendication 1, caractérisé en ce que les éléments de canalisation d'air (109) couvrent une surface de 10 à 50 % de la section transversale de sortie (102, 118).
  3. Module ventilateur (100) selon la revendication 1 ou 2, caractérisé en ce que des éléments de canalisation d'air (109) sont agencés selon un angle d'inclinaison α par rapport à la direction d'écoulement (103) de l'air de refroidissement et en ce que la position angulaire des éléments de canalisation d'air (109) dépend du rayon (110) de la roue de ventilateur (1).
  4. Module ventilateur (100) selon la revendication 3, caractérisé en ce que l'angle d'inclinaison α des éléments de canalisation d'air (109) est compris entre α = 12° pour r = d et α = 45° pour r = 1,3 x d, « r » étant le rayon (110) de la roue de ventilateur (1) et « d » le diamètre (112) du moyeu de ventilateur (2).
  5. Module ventilateur (100) selon l'une des revendications 1 à 4, caractérisé en ce que les extrémités extérieures (13) des éléments de canalisation d'air (109) sont reliées les unes aux autres par l'intermédiaire d'un anneau extérieur (114).
  6. Module ventilateur (100) selon l'une des revendications 1 à 5, caractérisé en ce que la longueur radiale (14) de l'orifice d'écoulement (6) correspond au maximum à 30 % du rayon de moyeu (15).
  7. Module ventilateur (100) selon l'une des revendications 1 à 6, caractérisé en ce que la largeur (16) de l'orifice d'écoulement (6) vaut entre 35 et 45 % de la largeur de pale de ventilateur (17).
  8. Module ventilateur (100) selon l'une des revendications 1 à 7, caractérisé en ce que l'angle d'inclinaison (β2) du tronçon de pale de ventilateur (5) est supérieur de 40 à 55° à l'angle d'inclinaison (β1) de la pale de ventilateur (2).
  9. Module ventilateur (100) selon l'une des revendications 1 à 8, caractérisé en ce que le tronçon de pale de ventilateur (5) est agencé dans la zone de l'arête arrière (12) de la pale de ventilateur (2).
  10. Module ventilateur (100) selon l'une des revendications 1 à 9, caractérisé en ce que la longueur radiale (14) de l'orifice d'écoulement (6) est dimensionnée de telle sorte que l'orifice d'écoulement (6) se termine au niveau de l'anneau extérieur (114) des éléments de canalisation d'air (109).
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 EP1934484A1 (fr) 2008-06-25
EP1934484B1 true 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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EP3312427B1 (fr) 2016-10-19 2022-08-17 ebm-papst Mulfingen GmbH & Co. KG Ventilateur doté de la roue de ventilateur et des ailettes de diffusion

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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
US11391295B2 (en) * 2017-05-22 2022-07-19 Fujitsu General Limited Propeller fan
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
WO2020110967A1 (fr) 2018-11-30 2020-06-04 株式会社富士通ゼネラル Ventilateur à hélice
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
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Publication number Priority date Publication date Assignee Title
EP3312427B1 (fr) 2016-10-19 2022-08-17 ebm-papst Mulfingen GmbH & Co. KG Ventilateur doté de la roue de ventilateur et des ailettes de diffusion

Also Published As

Publication number Publication date
ATE424510T1 (de) 2009-03-15
DE102005046180B3 (de) 2007-03-22
WO2007036431A1 (fr) 2007-04-05
US20090151911A1 (en) 2009-06-18
EP1934484A1 (fr) 2008-06-25
CN101278128A (zh) 2008-10-01
DE502006003033D1 (de) 2009-04-16
US8100665B2 (en) 2012-01-24
CN100554701C (zh) 2009-10-28

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