EP1741933B1 - Roue à aubes et procédé pour sa fabrication - Google Patents

Roue à aubes et procédé pour sa fabrication Download PDF

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Publication number
EP1741933B1
EP1741933B1 EP06013819.5A EP06013819A EP1741933B1 EP 1741933 B1 EP1741933 B1 EP 1741933B1 EP 06013819 A EP06013819 A EP 06013819A EP 1741933 B1 EP1741933 B1 EP 1741933B1
Authority
EP
European Patent Office
Prior art keywords
impeller
impeller according
vanes
supporting structure
channel
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
EP06013819.5A
Other languages
German (de)
English (en)
Other versions
EP1741933A1 (fr
Inventor
Jörg Dipl.-Ing. Kilian
Peter Lucyga
Roland Rapp
Ulrich Schneider
Nikolaus Dipl.-Ing. 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
Mahle Behr GmbH and Co KG
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Filing date
Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP1741933A1 publication Critical patent/EP1741933A1/fr
Application granted granted Critical
Publication of EP1741933B1 publication Critical patent/EP1741933B1/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
    • F04D29/02—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
    • F04D29/26—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

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.
  • the invention also relates to a method for producing an impeller.
  • 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.
  • in motor vehicle heaters or automotive air conditioning systems usually no Wegritimmten blading is used.
  • 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 EP 1 035 330 A2 discloses an impeller for a tumbler radial fan for the heating and air conditioning of a motor vehicle having a plurality of blades, which have a supporting structure made of a first plastic and are formed of a plurality of layers.
  • a plastic impeller for a drum rotor radial fan for the heating and air conditioning of a motor vehicle which has a plurality of blades, wherein the blades are formed by a supporting, preferably solid, structure, sprayed onto the at least partially a soft component or in the at least partially a soft component is injected.
  • the supporting structure is a first plastic which has sufficient strength
  • the soft component is a second plastic which is softer.
  • the second plastic is preferably a foamed plastic.
  • 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, however, by a suitable choice of material of the structure forming material, 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 preferably forms at least in certain areas 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 flow channel between two blades is preferably convergent on the inflow side and divergent on the outflow side, but other configurations are also possible.
  • the convergent-divergent configuration of the impeller enables a substantially separation-free operation in the blade channel. It is accelerated by the strong curvature and sufficient thickness of the blade profile in the convergent region, the flow in the corresponding channel part and deflected in the direction of rotation of the impeller. In the subsequent, almost straight, divergent channel part, the flow is delayed, whereby the static pressure is increased.
  • 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 preferably between 0.030 and 0.2, in particular between 0.04 and 0.07, particularly preferably between 0.05 and 0.06.
  • the channel widening in the divergent part of the blade channel is preferably between 0.05 and 0.17, in particular between 0.09 and 0.15, particularly preferably 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 production of such an impeller is preferably carried out by means of plastic injection molding, wherein first the load-bearing structure injection molded from a first plastic and then or almost simultaneously injection molded at least a portion of the profiled trained blades of the impeller and / or a hollow profile by a second, softer plastic which is auf dioxide the supporting structure or injected into a formed by the supporting structure hollow profile.
  • 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.
  • a drum-type centrifugal fan used for the conveyance of air in an automotive air conditioner includes an impeller 1 having 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 implied
  • 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 consist of a structure 6, which in the present case is made of a solid plastic, and has sufficient strength for the expected loads, as well as a sprayed onto the structure 6 layer 7 of 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. In addition, this thickness usually suffices 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 simplify the production, optionally also the entire blades 2 or the entire impeller 1 can cover.
  • the supporting structure 6 is slightly tapered in the region of the blade 2 covered by the soft component, the taper being gradual.
  • 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 blade suction and pressure side can be adjusted such that only minimal, non-flow-influencing deformation of the soft component, in particular on the blade pressure side, occurs during blower operation.
  • the following geometries are particularly suitable for a convergent-divergent blade channel, in particular for heavily profiled blades, ie at d / lges greater than 0.15, in particular greater than 0.2, where d denotes the profile thickness and lges the total profile length (measured straight):
  • the blade channel length ratio Lkv is preferably between 0.1 and 0.9.
  • the channel taper Kverkonv in the convergent part of the blade channel, which results from Kverkonv A 1 - A 2 / Lgekrkonv is preferably 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 preferably 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 formed over their length or at least one or more parts thereof parallel to the axis of rotation 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 a further variant with tapering in the direction of the inflow side 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 diverj up to a tapered inner diameter enlarged, but the outer diameter remains constant as well as in the thickness direction.
  • Fig. 9 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.
  • the relative cross-sectional area decrease ⁇ V is in the range from 0.1 to 0.90, in particular from 0.2 to 0.8 and particularly preferably from 0.3 to 0.7.
  • 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, 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.
  • blades are designed as (partial) hollow profiles, then they may be open or closed on the frame side.
  • an at least partial cover plate may also be present 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)

Claims (16)

  1. Roue mobile pour un ventilateur centrifuge à rotor cylindrique conçu pour le chauffage et la climatisation d'un véhicule automobile, ladite roue mobile comprenant une pluralité d'aubes (2), présentant une structure porteuse (6) se composant d'une première matière plastique, caractérisée en ce qu'un composant souple constitué d'une deuxième matière plastique est appliqué par injection, au moins partiellement, sur la structure porteuse (6) de l'aube (2), ou bien un composant souple constitué d'une deuxième matière plastique est injecté au moins partiellement dans la structure porteuse (6) de l'aube (2).
  2. Roue mobile selon la revendication 1, caractérisée en ce que l'épaisseur de paroi massive maximale de la structure porteuse (6) est égale à 3 mm dans la zone des aubes.
  3. Roue mobile selon la revendication 1 ou 2, caractérisée en ce que le composant souple forme au moins partiellement le profil de l'aube (2).
  4. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que les aubes sont configurées au moins partiellement comme un profil creux.
  5. Roue mobile selon la revendication 4, caractérisée en ce qu'il est prévu des nervures dans les aubes configurées de manière creuse.
  6. Roue mobile selon la revendication 4 ou 5, caractérisée en ce que les aubes configurées comme un profil creux sont fermées sur un côté.
  7. Roue mobile selon l'une quelconque des revendications 4 à 6, caractérisée en ce qu'un composant souple est injecté à l'intérieur du profil creux.
  8. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que la roue mobile (1) est fabriquée au moyen d'un moulage par injection de matière plastique à deux composants.
  9. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que le profil de l'aube se réduit au moins partiellement en direction du châssis de ventilateur.
  10. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que les aubes (2) sont configurées de manière cylindrique sur le côté moyeu de la roue mobile et de manière conique sur le côté châssis de ventilateur.
  11. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal d'écoulement (3) situé entre deux aubes (2) est configuré de façon convergente sur le côté d'entrée de flux et de façon divergente sur le côté de sortie de flux.
  12. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que le rapport de longueur (Lkv) du canal de l'aube est compris entre 0,2 et 0,6.
  13. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que le rétrécissement du canal (Kverkonv) est compris entre 0,030 et 0,20 dans la partie convergente du canal (3) de l'aube.
  14. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élargissement du canal (Kerwdiv) est compris entre 0,05 et 0,17 dans la partie divergente du canal de l'aube.
  15. Roue mobile selon l'une quelconque des revendications précédentes, caractérisée en ce que les aubes (2) de la roue mobile (1) sont configurées en étant fortement profilées, où l'angle d'entrée côté pression (beta1DS) est compris entre 30° et 90° et l'angle d'entrée côté aspiration (beta1SS) compris entre 25° et 70°, l'angle de sortie côté pression (beta2DS) étant compris entre 90° et 175° et l'angle de sortie côté aspiration (beta2SS) compris entre 90° et 170°.
  16. Procédé de fabrication d'une roue mobile (1) selon l'une quelconque des revendications 1 à 15, caractérisé en ce que la structure porteuse (6) constituée d'une première matière plastique est en premier lieu moulée par injection et, ensuite, ou bien presque en même temps, au moins une partie des aubes (2) de la roue mobile (1), configurées de manière profilée, est moulée par injection par une deuxième matière plastique plus souple qui est injectée sur la structure porteuse (6) ou bien injectée dans un profil creux formé par la structure porteuse.
EP06013819.5A 2005-07-04 2006-07-04 Roue à aubes et procédé pour sa fabrication Not-in-force EP1741933B1 (fr)

Applications Claiming Priority (1)

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DE102005031472 2005-07-04

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EP1741933A1 EP1741933A1 (fr) 2007-01-10
EP1741933B1 true EP1741933B1 (fr) 2019-03-06

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EP06013819.5A Not-in-force EP1741933B1 (fr) 2005-07-04 2006-07-04 Roue à aubes et procédé pour sa fabrication

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109595200A (zh) * 2019-01-12 2019-04-09 中山宜必思科技有限公司 一种离心风轮及其制造方法和应用其的离心风机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1035330A2 (fr) * 1999-03-08 2000-09-13 Matsushita Electric Industrial Co., Ltd. Rouet pour soufflante, sa méthode de fabrication, et soufflante

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3536416A (en) * 1968-05-14 1970-10-27 Dov Z Glucksman Squirrel-cage rotor for fluid moving devices
NL7909202A (nl) * 1979-12-20 1981-07-16 Trioliet Mullos Blazer voor het transport van veevoeder.
JPH0798000A (ja) * 1993-09-28 1995-04-11 Takao Kobayashi 多翼遠心送風機の羽根車の構造、及びその製法。
DE19525829A1 (de) * 1995-07-15 1997-01-16 Abb Research Ltd Lüfter
KR100369919B1 (ko) * 1999-03-03 2003-01-29 미쓰비시덴키 가부시키가이샤 팬, 팬의 용융금속 성형방법 및 팬의 용융금속 성형장치

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1035330A2 (fr) * 1999-03-08 2000-09-13 Matsushita Electric Industrial Co., Ltd. Rouet pour soufflante, sa méthode de fabrication, et soufflante

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