EP1902220B1 - Laufrad - Google Patents

Laufrad Download PDF

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Publication number
EP1902220B1
EP1902220B1 EP06762397A EP06762397A EP1902220B1 EP 1902220 B1 EP1902220 B1 EP 1902220B1 EP 06762397 A EP06762397 A EP 06762397A EP 06762397 A EP06762397 A EP 06762397A EP 1902220 B1 EP1902220 B1 EP 1902220B1
Authority
EP
European Patent Office
Prior art keywords
blade
blades
blower wheel
profile
duct
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
EP06762397A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1902220A1 (de
Inventor
Jörg KILIAN
Peter Lucyga
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 EP1902220A1 publication Critical patent/EP1902220A1/de
Application granted granted Critical
Publication of EP1902220B1 publication Critical patent/EP1902220B1/de
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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the invention relates to an impeller, in particular a plastic impeller for a drum rotor radial fan for the heating and air conditioning of a motor vehicle, according to the preamble of claim 1.
  • Drum rotor centrifugal blowers which are used for the promotion of air in automotive heaters or automotive air conditioning systems, are often operated at the lowest possible speed level.
  • the inflow to a subsequent heat exchanger should be as low as possible, the existing space, which is usually very cramped, should be used as flexible as possible.
  • axially expanded spiral housings and impellers with static pressure generation in the blade channel are generally used in this case.
  • the blading are backward curved, radially ending or slightly curved forward and executed with or without slight profiling.
  • the flow in the blade channel triggers hereby and remains detached up to the blade channel end. Due to this type of blading very high to high speeds are necessary depending on the operating point and type of blading. For acoustic reasons are in motor vehicle heaters or automotive air conditioning systems usually does not use backward curved blading.
  • Radial fans which allow a low speed level, have a forward curved blading and achieve comparable operating points at much lower speeds.
  • the flow is greatly diverted and accelerated. This kinetic energy is delayed in ideally designed, parallel-walled volute casings and converted into static pressure. Flow separation takes place at the blade channel inlet, and the flow arrives again at the blade channel end.
  • Axially extended spiral housings which are favorable for the heat exchanger application and build radially closer, are generally not useful in these blowers with forward curved blading, because it comes to efficiency losses.
  • drum rotor radial blowers In order to operate a drum rotor radial fan, which is used for the promotion of air, for example in motor vehicle heaters or automotive air conditioning systems, even at the lowest possible speeds, drum rotor radial blowers are known which have a forward curved blading.
  • the blading is not or only slightly profiled.
  • the blades are usually massively sprayed (see left part of Fig. 5 in which the flow pattern is shown in a blade channel in a conventional, non-profiled impeller, wherein on the suction side of the blades, a vortex formation can be seen).
  • the prior art also includes the disclosure JP 60 156997 A ,
  • an impeller in particular a plastic impeller for a tumbler radial fan for the heating and air conditioning of a motor vehicle having a plurality of blades, wherein the flow channel between two blades on the inflow side convergent and outflow divergent, and profiled profiled.
  • the convergent-divergent design of the impeller in conjunction with the strong profiling allows essentially free of detachment in the blade channel. In this case, the flow in the corresponding channel part is accelerated by the strong curvature and sufficient thickness of the blade profile in the convergent region and deflected without detachment in the direction of rotation of the impeller.
  • the blade channel length ratio with an inflow-side convergent and outflow-divergent configuration of the flow channel is preferably between 0.1 and 0.9, in particular between 0.15 and 0.7, particularly preferably between 0.2 and 0.6.
  • the channel taper in the convergent part of the blade channel is between 0.030 and 0.2, in particular between 0.04 and 0.07, particularly preferably between 0.05 and 0.06.
  • the channel extension in the divergent part of the blade channel is between 0.05 and 0.17, in particular between 0.09 and 0.15, particularly preferred between 0.1 and 0.14.
  • the blades of the impeller are preferably formed strongly profiled. Particularly profiled blades are considered in particular, in which the ratio of profile thickness to total profile length is greater than 0.15, in particular greater than 0.2.
  • the pressure-side inlet angle between 30 ° and 90 °, more preferably between 35 ° and 80 °, and the suction-side inlet angle between 25 ° and 70 °, more preferably between 30 ° and 60 °, the pressure-side exit angle between 90 ° and 175 °, more preferably between 100 ° and 165 °, and the suction-side exit angle between 90 ° and 170 °, more preferably between 100 ° and 165 °, particularly preferably in the middle region, ie in particular +/- 10 ° around the mean of the respective ranges given above, in order to achieve an optimal flow pattern without detachment as well as an optimal efficiency and a low-noise operation.
  • the blades are formed by a load-bearing, preferably solid, structure, onto which a soft component is injected at least in regions or into which a soft component is injected at least in regions.
  • a load-bearing preferably solid, structure
  • This is preferably in the supporting structure to a first plastic, which has a sufficient strength, and the soft component to a second plastic, which is softer.
  • the second plastic is preferably a foamed plastic. This embodiment allows a substantially distortion and shrinkage-free manufacture of the impeller.
  • the maximum wall thickness of the supporting structure in the region of the blades is preferably 3 mm. With such a restriction of the wall thickness, distortion and shrinkage can be safely avoided by a appropriate choice of material of the structure forming material, however, a sufficient strength of the impeller can be ensured. In addition, by an appropriate choice of material of the soft component, the weight of the impeller can be reduced, so that the blower is lighter overall. Furthermore, the soft component has an acoustically absorbing effect, so that the fan is somewhat quieter than corresponding fans without a soft component.
  • the soft component at least partially forms the profile of the blade, in particular in the strongly profiled part.
  • a soft component layer is provided both on the suction and the pressure side, the ends of the blades are preferably soft component-free, whereby the soft component is additionally protected against damage during assembly.
  • the blades are preferably at least partially formed as a hollow profile.
  • webs may be formed in the hollow profiles to increase the rigidity. These are preferably closed on one side.
  • the blades are preferably conically tapered on the frame side.
  • the blades are preferably formed on the impeller hub side of the motor side cylindrical and the frame side conical, wherein they taper in the frame direction. This ensures that, despite the strong profiling in connection with the overlap by the frame, a sufficient intake cross-section is available and there is no obstruction of the Ansaugqueritess.
  • the production of such an impeller is preferably carried out by means of plastic injection molding, preferably first a supporting structure of a injection-molded first plastic and then or almost simultaneously at least a portion of the profiled formed blades of the impeller and / or a hollow profile is injection-molded by a second, softer plastic, which is injected onto the supporting structure or injected into a hollow profile formed by the supporting structure.
  • Suitable materials for the supporting structure are in particular PA or PP, but also metals.
  • the soft component surrounding the supporting structure is preferably in the form of a foamed plastic, in particular S-EPS. Also very suitable is PP-EPDM.
  • PUR foam, melamine foam, PE foam (use of propellant in the application), silicone foam or, with limitations, foamed elastomers can be used.
  • the mentioned materials for the supporting structure can be used accordingly for wheels without soft component, in which case, in particular foamed materials can be used.
  • a tumbler radial fan which is used for the promotion of air in an automotive air conditioning system, typically has an impeller 1 with a ring of blades 2, wherein between each two blades 2, a blade channel 3 is formed.
  • the impeller 1 is mounted on a fan motor shaft (not shown) in a known manner.
  • the impeller 1 is partially covered by the frame, which is part of the spiral housing.
  • the frame opening for the air intake is in Fig. 6 indicated.
  • the blades 2 are formed strongly profiled, the flow channel 3 is convergent in the inlet region 4 and divergent in the exit region 5 (see. Fig. 4 ).
  • the pressure side DS of the blades 2 is concave in the inlet region 4, optionally to the outlet region 5, and the suction side SS of the blades 2 is convex in the inlet region 4 and straight in the outlet region 5, the blade thickness d having its maximum in the convergent region.
  • the blades 2 in the present case consist of a structure 6, which in the present case is made of a solid plastic and has sufficient strength for the loads to be expected, as well as a layer 7 molded onto the structure 6 from a soft component which forms the profile in the strongly profiled region of the blade 2.
  • the thickness of the structure 6 is at most 3 mm, so that in the production of the structure 6 no problems with regard to distortion or shrinkage occur.
  • this is enough Thickness is usually sufficient for sufficient rigidity of the blade 2.
  • the sprayed-on layer 7 serves only for profiling and, apart from the requirement that it can not be compressed by the air to be conveyed, has no supporting function.
  • the molded layer 7 on its outer side 8 also have a skin or a coating, wherein the coating, in particular to avoid contamination, optionally also cover the entire blades 2 or the entire impeller 1 to simplify the production.
  • the supporting structure 6 is slightly tapered in the area covered by the soft component of the blade 2, wherein the taper occurs gradually.
  • the outer contour is not affected by the transition from supporting structure 6 to soft component.
  • the supporting structure 6 consists of PA, the soft component of PP-EPDM.
  • the structure 6 itself forms the profile, for which it is designed as a hollow profile, in the case of the second variant with a stiffening web.
  • a soft component corresponding to the molded layer 7 may be provided, in particular for rigidity reasons.
  • an externally molded layer may be provided according to the embodiment described above.
  • the thickness of the structure is at most 3 mm, so that no distortion or shrinkage occurs during manufacture.
  • the thickness of the soft component on the Schaufelsaug- and -druckseite can be adjusted so that in the fan operation only to a minimum, not the flow influencing deformation of the soft component, in particular on the blade pressure side comes.
  • Kverkonv A ⁇ 1 - A ⁇ 2 / Lgekrkonv is between 0.030 and 0.200.
  • A1 is the flow channel width at the inlet and A2 is the flow channel width at the narrowest cross section.
  • the channel extension Kerwdiv in the divergent part of the blade channel, which results from Kerwdiv A ⁇ 3 - A ⁇ 2 / Lgekrdiv is between 0.05 and 0.17.
  • A3 is the flow channel width at the exit.
  • the inlet-side inlet angle beta1DS is between 30 ° and 90 ° and the inlet-side inlet angle beta1SS is between 25 ° and 70 °.
  • the pressure-side outlet angle beta2DS between 90 ° and 175 ° and the outlet-side outlet angle beta2SS between 90 ° and 170 °.
  • beta1DS, beta1SS, beta2DS and beta2SS are also particularly suitable in the case of a divergent-convergent blade channel shape and a convergent blade channel shape.
  • the blades 2 are parallel over their length or at least one or more parts thereof Rotary axis formed with a different cross-section.
  • the cross section is on the inlet side, as in Fig. 7 shown, impeller hub side cylindrical (the impeller hub side is in Fig. 1 provided with the reference numeral 9) with a Ausformschräge and zargen lake conically tapered in the longitudinal direction of the frame towards.
  • FIGS. 8 to 10 show another variant too Fig. 6 in the direction of the upstream side tapered blades 2.
  • the blades over a large part of the blade length in the direction of the axis of rotation seen a constant cross-section. Only in the last quarter, the cross-section of the blades decreases and both in the longitudinal profile direction, wherein the inner diameter dinenn enlarged up to a tapered inner diameter diverj, the outer diameter but there remains constant, as well as in the thickness direction.
  • the skeleton line of the base profile is indicated by a star-dashed line.
  • the course of the taper over the entire blade length is in Fig. 8 shown.
  • the total blade length is hereby called Slgefel, the part of the blade length, in which the inner diameter is increased, is denoted by Slverj.
  • the inner diameter diverj takes this, as from Fig. 8 seen in the last quarter of the blade length too.
  • the representation of Fig. 8 in terms of profile length is not to scale.
  • ratios of blade length tapered to total blade length are from 0.1 to 0.7, preferably from 0.15 to 0.5, and more preferably from 0.20 to 0.25.
  • the thickness of the blade profile is also reduced, so that the cross-sectional area of the blade profile also decreases in the tapered region.
  • the change in the blade profile is particularly good Fig. 10 seen.
  • FIGS. 11a to 11d show exemplary variations in terms of the course of the taper, where Fig. 11a a convex rejuvenation course, Fig. 11b a concave rejuvenation process, Fig. 11c a linear rejuvenation course and Fig. 11d show a simply graduated rejuvenation course. Any combination as well as a possibly multi-graded rejuvenation course are possible.
  • FIGS. 12 to 14 show variants with respect to the shape of the taper of the blade profile in the direction of the inflow side.
  • the course of the taper can, for example, according to the representation of FIGS. 11a to 11d respectively.
  • the skeleton line of the respective base profile is indicated by a star-dashed line.
  • the taper relative to the base profile may be symmetrical to the skeleton line, as in FIG Fig. 12 represented by the dashed line in a blade 2 on the suction side.
  • the taper relative to the base profile can also be asymmetric to the skeleton line as in Fig. 13 represented in a blade 2 by the dotted line on the suction side.
  • the rejuvenation can also be partially symmetrical and partially asymmetrical to the skeleton line, as in the FIGS. 12 to 14 is shown by solid lines and is apparent when comparing the solid lines with respect to the dashed or dotted line.
  • the channel shape in the tapered portion of the blading may be both convergent and convergent-divergent or divergent.
  • the entry and exit angles in the tapered blade part deviate from those in the region of the base profile, i. in the part with a constant cross section, from which results in an aerodynamic distortion of the blade profile.
  • the angles may also remain constant or at least substantially constant.
  • an at least partial cover plate may also be present on the frame side.
  • blades are designed as (partial) hollow profiles, then they may be open or closed on the frame side.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP06762397A 2005-07-04 2006-07-04 Laufrad Not-in-force EP1902220B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005031471 2005-07-04
PCT/EP2006/006513 WO2007003416A1 (de) 2005-07-04 2006-07-04 Laufrad

Publications (2)

Publication Number Publication Date
EP1902220A1 EP1902220A1 (de) 2008-03-26
EP1902220B1 true EP1902220B1 (de) 2012-09-12

Family

ID=37156036

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06762397A Not-in-force EP1902220B1 (de) 2005-07-04 2006-07-04 Laufrad

Country Status (5)

Country Link
US (1) US8337157B2 (zh)
EP (1) EP1902220B1 (zh)
JP (1) JP5240926B2 (zh)
CN (1) CN101213373B (zh)
WO (1) WO2007003416A1 (zh)

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DE202010011507U1 (de) * 2010-08-18 2010-11-04 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Zweikomponenten-Lüfterrad
US20120164376A1 (en) 2010-12-23 2012-06-28 General Electric Company Method of modifying a substrate for passage hole formation therein, and related articles
US8881396B2 (en) 2011-02-07 2014-11-11 Revcor, Inc. Method of manufacturing a fan assembly
DE102011015360A1 (de) * 2011-03-28 2012-10-04 Berling Gmbh Dunstabzugshaube
CA2779592C (en) 2011-06-02 2019-05-07 Cary Products Company, Inc. Headliner vent housing
ITCO20130037A1 (it) * 2013-09-12 2015-03-13 Internat Consortium For Advanc Ed Design Girante resistente al liquido per compressori centrifughi/liquid tolerant impeller for centrifugal compressors
AT515236B1 (de) * 2013-12-23 2015-12-15 Fronius Int Gmbh Schweißdrahtförderrolle und Vorschubvorrichtung zum Fördern eines Schweißdrahts
DE102014208372A1 (de) * 2014-04-11 2015-10-15 Ebm-Papst Mulfingen Gmbh & Co. Kg Wuchttaschen
US9945389B2 (en) 2014-05-05 2018-04-17 Horton, Inc. Composite fan
CN108138798B (zh) * 2015-10-07 2019-10-11 三菱电机株式会社 鼓风机及具备该鼓风机的空气调节装置
WO2018075635A1 (en) 2016-10-18 2018-04-26 Carrier Corporation Asymmetric double inlet backward curved blower
USD836048S1 (en) 2016-10-26 2018-12-18 Cary Products Co., Inc. Three vane louver
CN110494654B (zh) * 2017-04-10 2021-09-14 夏普株式会社 远心风扇、成型用模具及流体输送装置
DE102017114679A1 (de) * 2017-06-30 2019-01-03 Ebm-Papst Mulfingen Gmbh & Co. Kg Gebläserad
US11041502B2 (en) 2018-01-30 2021-06-22 Carrier Corporation Double inlet backward curved blower
JP7467025B2 (ja) * 2018-03-26 2024-04-15 東芝キヤリア株式会社 送風機および空気調和機の室内ユニット
CN108825552B (zh) * 2018-07-17 2023-10-03 珠海格力电器股份有限公司 空气处理设备、风机及其离心风叶
US11274677B2 (en) 2018-10-25 2022-03-15 Revcor, Inc. Blower assembly

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US6033186A (en) * 1999-04-16 2000-03-07 General Electric Company Frequency tuned hybrid blade
EP1256722A2 (de) * 2001-05-11 2002-11-13 TCG UNITECH Aktiengesellschaft Kreiselpumpe
JP2005155579A (ja) * 2003-11-28 2005-06-16 Sanden Corp 多翼送風ファン

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60156997A (ja) * 1984-01-26 1985-08-17 Nippon Denso Co Ltd 遠心式送風機用フアン
US6033186A (en) * 1999-04-16 2000-03-07 General Electric Company Frequency tuned hybrid blade
EP1256722A2 (de) * 2001-05-11 2002-11-13 TCG UNITECH Aktiengesellschaft Kreiselpumpe
JP2005155579A (ja) * 2003-11-28 2005-06-16 Sanden Corp 多翼送風ファン

Also Published As

Publication number Publication date
EP1902220A1 (de) 2008-03-26
WO2007003416A1 (de) 2007-01-11
US20090129933A1 (en) 2009-05-21
US8337157B2 (en) 2012-12-25
JP5240926B2 (ja) 2013-07-17
CN101213373B (zh) 2012-05-09
CN101213373A (zh) 2008-07-02
JP2008545086A (ja) 2008-12-11

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