WO2023088870A1 - Carénage de ventilateur et ventilateur de radiateur pour un véhicule à moteur, le ventilateur de radiateur ayant un carénage de ventilateur - Google Patents

Carénage de ventilateur et ventilateur de radiateur pour un véhicule à moteur, le ventilateur de radiateur ayant un carénage de ventilateur Download PDF

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Publication number
WO2023088870A1
WO2023088870A1 PCT/EP2022/081911 EP2022081911W WO2023088870A1 WO 2023088870 A1 WO2023088870 A1 WO 2023088870A1 EP 2022081911 W EP2022081911 W EP 2022081911W WO 2023088870 A1 WO2023088870 A1 WO 2023088870A1
Authority
WO
WIPO (PCT)
Prior art keywords
strut
fan
angle
frame
tip
Prior art date
Application number
PCT/EP2022/081911
Other languages
German (de)
English (en)
Inventor
Christian Froh
Andre EVERS
Antje Findeisen
Original Assignee
Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg
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 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg filed Critical Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg
Publication of WO2023088870A1 publication Critical patent/WO2023088870A1/fr

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
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/542—Bladed diffusers
    • F04D29/544—Blade shapes

Definitions

  • the invention relates to a fan shroud which has a central wheel mount for accommodating a fan wheel, an outer shroud ring and a plurality of struts which are fastened to the shroud ring with a strut base on the wheel mount and with a strut tip on the shroud ring.
  • the invention further relates to a radiator fan with such a fan frame.
  • Such cooling fans are used in motor vehicles to cool other components, such as an internal combustion engine. In addition, they can also be used for heat exchange with other components.
  • a cooling fan can also be used in an air heat exchanger, for example a heat pump system in a motor vehicle, or for cooling high-performance electrical components, such as an electric traction motor or an electric traction battery in electric vehicles.
  • the cooling fan is connected upstream of a heat exchanger through which a heat transfer medium flows.
  • the heat transfer medium is often a coolant.
  • the actual fan wheel which rotates about an axis of rotation during operation and with which an air flow is conveyed from an inflow side to a pressure side, is rotatably held on the fan frame.
  • a hub part of the fan wheel is typically held in the central wheel mount of the fan frame.
  • the fan wheel is driven, for example by a belt drive and preferably by an electric motor, which is seated in the central wheel mount of the fan frame.
  • struts are distributed over the circumference between the wheel mount and the frame ring. These struts therefore form a flow obstacle for the air conveyed by the fan wheel during operation.
  • DE 10 2016 221 642 A1 discloses a fan frame in which the struts are oriented at a strut angle with respect to a fan plane that is oriented perpendicular to the axis of rotation of the fan wheel, which angle increases from the inside outwards in the direction of the fan frame.
  • the object of the invention is to enable a flow-optimized fan frame.
  • a fan shroud for a radiator fan of a motor vehicle and by a radiator fan with such a fan shroud according to the features of claims 1 and 12 Axis of rotation for the fan wheel.
  • the axial direction extends from an upstream side to a pressure side of the shroud, i. H.
  • air flows through the fan frame from the inflow side to the pressure side.
  • the fan shroud also has an outer shroud ring.
  • the frame ring and the wheel mount define a fan plane which is oriented perpendicularly to the axial direction and thus perpendicularly to the axis of rotation.
  • the fan shroud has a plurality of struts which, on the one hand, extend in a radial direction from the wheel mount to the shroud ring and, on the other hand, also extend from the inflow side in the direction of the pressure side.
  • the radial direction is understood as meaning the direction in which the respective strut extends, starting from the wheel mount in the direction of the frame ring. This radial direction typically deviates from a mathematical radial, which is oriented perpendicular to the axis of rotation.
  • the struts are attached to the wheel mount with a strut foot and to the frame ring with a strut tip.
  • the struts are designed overall in the manner of a strut or blade blade.
  • the struts are inclined with respect to the plane of the fan, so that a flow guiding function is achieved by the inclined strut.
  • the struts are oriented at a strut angle, which is also referred to as the angle of attack, with respect to the plane of the fan. They are usually set at an acute angle with respect to the pressure side, ie the struts form an acute angle with the plane of the fan on the pressure side.
  • the strut angle changes differently in a radially inner area compared to a radially outer area.
  • the radially inner area adjoins the wheel mount and extends to an intermediate position.
  • the radially outer area extends—preferably starting from the intermediate position—to the strut tip.
  • the strut as a whole is preferably divided only into the inner and outer areas, which are therefore connected to one another.
  • the strut is divided into more than two areas and thus has several intermediate positions.
  • the strut is divided in particular into three areas with two intermediate positions or else into four areas.
  • at least two of the areas have different changes in the strut angle.
  • all areas have different changes in the strut angle in relation to one another.
  • the inclination of the struts with respect to the fan level is initially based on the general consideration that the fan impeller generates a strong swirling flow, especially in the direction of flow, during operation, and that it is advantageous to position the struts with respect to the swirling air flow in such a way that flow resistance is reduced and thus an efficiency of the fan wheel is improved.
  • the invention is now based on the finding that the proportion of an axial component and a circumferential component of the flow and thus a so-called velocity triangle of the flow velocity change significantly from the wheel mount in the direction of the shroud ring.
  • the peripheral component of the flow increases significantly in the outer area.
  • the strut angle as a whole is adapted as optimally as possible to these flow conditions that vary in the radial direction, and that for this purpose a greater change and variation in the strut angle is set in the outer area in which the flow field changes particularly sharply.
  • a change in the strut angle is understood to mean a relative change per unit length of the strut in the radial direction. If the strut angle is plotted against the radial direction and thus against a length of the strut, the change in the strut angle corresponds to a gradient. This gradient is therefore different in the outer area compared to the inner area.
  • the gradient in a respective area is preferably constant. Alternatively, however, it can also vary within a range. In this case, the condition that the slope (change per unit length) of the two areas is different applies to an average slope (average change per unit length) of the respective area.
  • the relative change and thus the gradient in the outer area is greater than in the inner area, ie the absolute change in the strut angle per unit of length is greater in the outer area than in the inner area. This achieves the best possible adaptation to the real flow conditions.
  • the inner area preferably extends over 60% to 90% of the total length of the respective strut and in particular over 70% to 85% of the total length.
  • the strut angle at the strut base is greater than at the strut tip. Specifically, the strut angle increases, starting from the strut base, from an initial value to a maximum value at the intermediate position and from there decreases to a minimum value in the outer area. The absolute change in the strut angle in the inner area is therefore smaller than the absolute change in the outer area.
  • the inner area extends over 60% to 90% of the total length of the strut, that the further area adjoins it as an outer area, which extends to the strut tip and that the strut angle, starting from the strut foot in the inner area, increases continuously, in particular with a constant gradient, up to a maximum value and then in the outer area up to the strut tip, again preferably with a constant gradient, decreases to a minimum value which is smaller than the strut angle at the strut base.
  • the strut angle at the strut foot is in the range between 35° and 55° and in particular in the range of 40° and 50°.
  • the maximum strut angle is in a range between 55° to 80° and in particular in the range from 65° to 75°.
  • the strut angle at the strut tip has a value in the range from 25° to 45° and in particular in the range from 30° to 40°.
  • the strut angle changes by 10° to 30° and in particular by 15° to 25° in the inner area and/or that the strut angle in the outer area changes by 20° to 50° and in particular by 30° to 40° changes.
  • a fan frame In connection with a fan wheel, such a fan frame forms a radiator fan according to the invention.
  • the fan wheel sits with a hub in the wheel mount of the fan frame.
  • the wheel mount is in particular a mount for an electric motor which is provided to drive the fan wheel. In this respect, the wheel mount therefore forms a motor mount.
  • the fan frame described here is characterized in that it has an improved efficiency compared to a configuration according to the prior art, which is reflected, among other things, in a reduced speed level of the fan wheel and a reduced electrical power consumption of the Electric motor for driving the fan impeller is reflected. Furthermore, lower noise emissions are also achieved in this way.
  • FIG. 1 shows a plan view of an inflow side of a fan frame
  • FIG. 2 shows an enlarged representation of the illustration according to FIG. 1 in the area of a strut
  • FIG 3A-3C cross-sectional representations along the section line A-A, B-B, C-B of FIG 2,
  • FIG. 6A shows an enlarged representation of a detail of the inflow side of the fan frame
  • FIG. 6B shows an enlarged representation of a detail of the outflow side of the fan frame.
  • the fan frame 2 shown in FIG. 1 has a central wheel mount 4, a frame ring 6 and a plurality of struts 8 arranged between them.
  • the fan shroud 2 generally has a frame 10 with which it is mounted, for example, on a body component of a motor vehicle.
  • the central wheel mount 4 is used to fasten a fan wheel 12 (cf. FIG. 5 in particular) which has blades 14 via which an air flow is conveyed from an inflow side 16 to a pressure side 18 during operation.
  • the wheel mount 4 is circular when viewed in cross section and is generally used in a preferred embodiment for accommodating an electric motor which drives the fan wheel 12 .
  • the wheel mount 4 defines in this respect a motor carrier and also a tation axis around which the fan wheel 12 rotates during operation.
  • the wheel mount 4 also defines an axial direction 20 which runs parallel to the axis of rotation, specifically in the direction from the inflow side 16 to the pressure side 18 .
  • the fan wheel 12 rotates in the positive circumferential direction 22, ie in the clockwise direction (when looking at the inflow side 16), as shown in FIG.
  • each strut 8 each extend in a radial direction 24 which at the same time defines a longitudinal direction of the respective strut 8 .
  • each strut 8 has its own longitudinal and thus radial direction, which is inclined with respect to a mathematical radial to the axis of rotation and thus to the axial direction 20, as can be seen from FIG.
  • a respective strut 8 is formed overall approximately in the form of a blade in the manner of a blade and preferably has an approximately rectangular cross-sectional area, as can be seen in particular from the representation according to FIGS. 3A to 3C.
  • each strut has two opposite flat sides. In the exemplary embodiment, these extend in a straight line and specifically parallel to one another. Alternatively, these leaf surfaces can also be curved.
  • a respective strut 8 extends generally from a strut base 26 with which it is attached to the wheel mount 4 to a strut tip 28 with which it is attached to the frame ring 6 .
  • a respective strut 8 that is to say the respective leaf surface of the strut 8, is arranged inclined at a strut angle a in relation to a fan plane L.
  • a respective strut 8 is arranged at an acute angle with respect to the pressure side 18 .
  • the strut angle a is measured here between the fan plane L and the orientation of the blade surface along a transverse direction 30 (cf. FIG. 3B).
  • the transverse direction 30 is defined in particular by a central line never, which extends from one end of the strut leaf to the other end of the strut leaf perpendicular to the radial direction 24 and within a sectional plane perpendicular to the radial direction 24.
  • the strut angle a varies. In the exemplary embodiment, it has a value in the range between 40° and 50°, specifically a value of 45°, at the cutting position A-A, a value in the range between 65 and 75° and specifically a value of 69° at the cutting line B-B, and in the cutting area C-C has a value of between 30 and 40° and in particular a value of 35°.
  • FIG. 4 The course of the strut angle a over the length R of the strut 8 in the radial direction 24 is shown in FIG. 4 by way of example.
  • the solid line in FIG. 4 shows the configuration according to the invention and the dashed line shows the configuration according to the prior art.
  • the strut angle is indicated on the x-axis and the ratio of the radial length R to the overall length Ra of the strut 8 is indicated in percent on the y-axis.
  • the cutting positions shown in FIGS. 3A to 3C are also shown.
  • the cut position A - A is around 10%, the cut position B-B at around 78% and the cut position C-C at almost 100% of the total length Ra.
  • the strut angle has a value of 45°, which increases continuously and steadily up to a maximum value at the intermediate position (intersection line BB), at which the strut angle has a value of approximately 69°.
  • the strut angle a then again decreases, in particular continuously, down to a minimum value of 35°.
  • the strut angle ⁇ therefore shows a constant gradient and therefore runs linearly.
  • the outer area 34 is generally preferably significantly shorter than the inner area 32.
  • the inner area 32 has, for example, a length in the range between 60 and 85% of the total length Ra.
  • a radiator fan 36 as a combination of the fan frame 2 with the fan wheel 12 fastened to it can be seen in the sectional view shown in FIG. 5.
  • An electric motor 38 which drives the fan wheel 12 with the blades 14 , is inserted in the wheel mount 4 .
  • the fan wheel 12 is usually arranged on the inflow side 16 and the fan frame 2 is therefore arranged downstream on the pressure side 18 in the direction of flow.
  • the struts 8 are therefore “rear struts”.
  • the reverse variant, in which the struts 8 are arranged opposite one another, that is to say in the flow direction in front of the pressure side 18 and thus on the inflow side 16 (“front struts”), is also possible.
  • FIG. 6A shows a sectional view of the inflow side 16 and FIG. 6B shows a sectional view of the pressure side 18 of the fan frame 2
  • the strut angle a vary as a function of the length R of the strut 8 in the longitudinal direction, but also a width of the strut 8 in the transverse direction 30. Especially in the outer region 34 this width increases significantly.
  • the width up to the frame ring 6 increases, for example, by a factor of 1.5 and more, for example by at least a factor of 2.
  • the strut base 26 therefore has a significantly widened blade area.
  • the width in the inner area 32 preferably varies less and in particular only slightly and for example in the range of only 10-30%.
  • the width of the strut 8 decreases continuously starting from the strut foot 26 to the intermediate position 31 and then increases again.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un carénage de ventilateur (2) pour un ventilateur de radiateur (36) d'un véhicule à moteur, comprenant - un logement central d'impulseur (4) destiné à recevoir un impulseur de radiateur (12), lequel réceptacle définit un axe de rotation pour l'impulseur de radiateur (12), lequel axe est orienté dans une direction axiale (20), la direction axiale (20) s'étendant d'un côté d'afflux (16) à un côté de pression (18) du carénage de ventilateur (12), - une bague de carénage (6), un plan de ventilateur (L) perpendiculaire à la direction axiale (20) étant défini par le logement d'impulseur (4) et la bague de carénage (6), et - une pluralité d'entretoises (8) qui s'étendent du logement d'impulseur (4) à la bague de carénage (6) et s'étendent du côté d'afflux (16) au côté de pression (18), et qui, avec une base d'entretoise (26), sont fixées au logement d'impulseur (4), et, avec une pointe d'entretoise (28), sont fixées à la bague de carénage (6), les entretoises (8) étant orientées selon un angle d'entretoise (α) par rapport au plan de ventilateur (L), lequel angle varie de la base d'entretoise (26) à la pointe d'entretoise (28). Selon l'invention, la manière dont l'angle d'entretoise (α) varie dans une région interne (32) à partir de la base d'entretoise (32) est différente par comparaison à une région externe (34) jouxtant la région interne (32) afin d'assurer de bonnes caractéristiques d'écoulement.
PCT/EP2022/081911 2021-11-19 2022-11-15 Carénage de ventilateur et ventilateur de radiateur pour un véhicule à moteur, le ventilateur de radiateur ayant un carénage de ventilateur WO2023088870A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021213044.5 2021-11-19
DE102021213044.5A DE102021213044A1 (de) 2021-11-19 2021-11-19 Lüfterzarge sowie Kühlerlüfter für ein Kraftfahrzeug mit einer Lüfterzarge

Publications (1)

Publication Number Publication Date
WO2023088870A1 true WO2023088870A1 (fr) 2023-05-25

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PCT/EP2022/081911 WO2023088870A1 (fr) 2021-11-19 2022-11-15 Carénage de ventilateur et ventilateur de radiateur pour un véhicule à moteur, le ventilateur de radiateur ayant un carénage de ventilateur

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DE (1) DE102021213044A1 (fr)
WO (1) WO2023088870A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015151922A (ja) * 2014-02-14 2015-08-24 パナソニックＩｐマネジメント株式会社 送風機、およびその送風機を搭載した室外ユニット
EP3299737A1 (fr) * 2015-07-10 2018-03-28 Samsung Electronics Co., Ltd. Soufflante d'air et conditionneur d'air comportant celle-ci
DE102016221642A1 (de) 2016-11-04 2018-05-09 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Zargenvorrichtung für ein Kühlerlüftermodul, ein Kühlerlüftermodul mit einer Zargenvorrichtung und Fahrzeug mit einem solchen Kühlerlüftermodul
DE102019110934A1 (de) * 2019-04-29 2020-10-29 Ebm-Papst Mulfingen Gmbh & Co. Kg Nachleitvorrichtung für einen Axialventilator

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006062118A1 (de) 2005-12-23 2007-06-28 Behr Gmbh & Co. Kg Lüftersystem, Wärmetauschermodul, Verfahren zur Herstellung eines Lüftersystems und/oder eines Wärmetauschermoduls
JP6747469B2 (ja) 2017-07-25 2020-08-26 株式会社デンソー 車両用空調ユニット
DE102017012255A1 (de) 2017-11-15 2019-05-16 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Kühlerlüftermodul
DE202019102382U1 (de) 2019-04-29 2019-06-07 Ebm-Papst Mulfingen Gmbh & Co. Kg Nachleitvorrichtung für einen Axialventilator

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015151922A (ja) * 2014-02-14 2015-08-24 パナソニックＩｐマネジメント株式会社 送風機、およびその送風機を搭載した室外ユニット
EP3299737A1 (fr) * 2015-07-10 2018-03-28 Samsung Electronics Co., Ltd. Soufflante d'air et conditionneur d'air comportant celle-ci
DE102016221642A1 (de) 2016-11-04 2018-05-09 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Zargenvorrichtung für ein Kühlerlüftermodul, ein Kühlerlüftermodul mit einer Zargenvorrichtung und Fahrzeug mit einem solchen Kühlerlüftermodul
DE102019110934A1 (de) * 2019-04-29 2020-10-29 Ebm-Papst Mulfingen Gmbh & Co. Kg Nachleitvorrichtung für einen Axialventilator

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Publication number Publication date
DE102021213044A1 (de) 2023-05-25

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