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WO2012072779A1 - Axial fan - Google Patents

Axial fan

Info

Publication number
WO2012072779A1
WO2012072779A1 PCT/EP2011/071579 EP2011071579W WO2012072779A1 WO 2012072779 A1 WO2012072779 A1 WO 2012072779A1 EP 2011071579 W EP2011071579 W EP 2011071579W WO 2012072779 A1 WO2012072779 A1 WO 2012072779A1
Authority
WO
Grant status
Application
Patent type
Prior art keywords
fan
hub
blade
edge
axial
Prior art date
Application number
PCT/EP2011/071579
Other languages
German (de)
French (fr)
Inventor
Uwe Aschermann
Uwe Blass
Frederic Guilbaud
Original Assignee
Behr Gmbh & 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

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE DISPLACEMENT PUMPS
    • F04D19/00Axial-flow pumps
    • F04D19/002Axial flow fans
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE DISPLACEMENT PUMPS
    • F04D25/00Pumping installations or systems
    • F04D25/02Units comprising pumps and their driving means
    • F04D25/022Units comprising pumps and their driving means comprising a yielding coupling, e.g. hydraulic
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/26Rotors specially for elastic fluids
    • F04D29/32Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/329Details of the hub

Abstract

The invention relates to an axial fan for delivering cooling air, in particular for an internal combustion engine of a motor vehicle, comprising fan blades (13, 14, 15) which are fastened to a hub (12) and which have a pressure side and a suction side and a trailing edge (16, 17, 18) and a blade depth (t), on the pressure side of which fan blades is arranged a hub ramp (13a, 14a, 15a) which rises counter to the direction of rotation (D) of the axial fan (11), wherein the trailing edge (16, 17, 18) has an outer region (16a, 17a, 18a) situated radially outside the hub ramp (13a, 14a, 15a) and has an inner region (16b, 17b, 18b) situated radially within the hub ramp (13a, 14a, 15a).

Description

Axial

The invention relates to a Axialiüfter for conveying cooling air in particular for an internal combustion engine of a motor vehicle according to the preamble of claim 1.

A generic axial fan is disclosed in the earlier patent application of the applicant with the official file reference 10 2010 042 325.4. The axial flow fan comprises a hub ring attached to the fan blades, which called on its pressure side a hub ramp and on its suction side air guiding elements, even stabilizers which serve to influence the fan flow, have. The fan blades each have a leading edge, also called the leading edge, as well as called a trailing edge, trailing edge and, on. The trailing edge of the fan blade essentially has two radially extending portions, namely an outer ramp disposed outside of the hub portion and an inner, disposed within the hub ramp portion. The inner portion of the trailing edge is made of weight-saving reasons inwardly, that is angled in the direction of the hub ring, so that a groove for the rear edge, thereby reducing the width of the fan blade is obtained. It has been found that due to this groove the trailing edge of a transverse and / or return flow of the fan blade flow results which produces an unfavorable influence on the flow on the pressure side of the adjacent fan blade. By this back and / or transverse flow results in the region of the hub ramp a vortex structure, which has a waste of the Wirkungsgra- result.

From EP 0515839 A1 an axial fan with fan blades has been known on the pressure side of a flow direction opposite to the rising ramp hub is arranged. The hub ramp fills virtually the dead water region in the blade root and thus avoids afflicted with losses turbulence.

From DE 199 29 978 B4 an axial fan with fan blades has been known Nabenram- pen are arranged on the suction side of air-directing elements and on the pressure side. Thereby, a flow channel is formed, which causes a stable guidance of the flow in the region of the blade root.

The object of the present invention to improve the flow conditions in a axial fan of the type mentioned and in particular to avoid a lossy turbulence.

The object of the invention is achieved by the independent patent claim. 1 Advantageous embodiments result from the dependent chen.Anspruchsgemäß, the fan blade has a trailing edge with two From "cut on, wherein a first outer portion located radially outside the hub ramp and a second inner portion radially inside of the hub ramp. According to the invention it is advantageous when the rear edge outside the hub ramp identifies a curve in the outer region radially, which substantially continues over the radial position of the hub ramp away radially inwards in the inner region unchanged and in the radially innermost area toward the hub runs , Thus, the inventions dung proper success is achieved that a stabilization of the fan blade flow is achieved in the hub ramp region, d, h, a transverse and / or return flow to the trailing edge of the fan blade is at least reduced or eliminated. This leads to a significant increase in the efficiency of the fan and to a considerable increase funded by the fan volume flow at the operating point of the fan. In addition, the specific sound pressure level is reduced.

Furthermore, it is advantageous when the radially innermost area is the radially inner portion of the radius of the radially inner region.

It is also advantageous, if this proportion is about one third, about a quarter or preferably less than about one-fifth of the radius of the inner region of the trailing edge.

It can be understood therefore that three regions are present, the outer portion and the inner portion, said inner area is divided into a so-called intermediate region and the innermost region in turn. According to the invention it is therefore advantageous if the trailing edge outside the hub ramp identifies in the outer region radially a profile which substantially continues over the radial position of the hub ramp away radially inwards in the so-called intermediate region of the inner region unchanged and in the radially innermost area toward the hub runs. In this case, curved or angled out as this bleed to the hub etc. mean.

The fan blade advantageously has in the inner region is substantially the same chord length as in the outer region, ie, in particular, that the sheet trailing edge from the outer portion substantially passes straight into the inner portion, so that a straight rear edge to the blade root area overall. In this case, a certain curvature of the leading edge does not harm that was half straight assumed in this discussion for simplicity as, wherein an odd curved leading edge would also be permissible.

Compared to the fan of the older patent application, the blade chord and the blade width in the region inside of the hub ramp are thus advantageously increased.

The terms fan blade and fan blade used in the present application as synonyms. The term chordal the axial extent of the fan blade is understood. The blade depth is the pro- jection of the sheet width in the circumferential direction, wherein the sheet width, the distance between the blade leading edge and blade trailing edge, measured in the direction of the tendon.

According to a preferred embodiment, the trailing edge is rounded in the innermost region. This allows a voltage reduced transfer of the sheet trailing edge in the hub area.

According to a further preferred embodiment, the blade trailing edge is in its innermost region - over a fillet - in the free edge of the hub ramp over. In order to increase the strength in the blade root area for connecting the fan blade is achieved at the hub. Moreover, results in a favorable flow channel between the suction side and the pressure side in the Schaufelfuß- and hub ramp area. Under the free edge of the hub ramp facing away from the fan blade and protruding from the fan blade edge of the hub ramp is understood.

According to a further preferred embodiment of the fan blades stabilizers are arranged on the suction side, which are preferably located radially inwardly of the hub ramp. The downstream region of the stabilizer thus opens into the inner portion of the blade trailing edge. By the stabilizers further stabilization of the flow is achieved in the blade in conjunction with the hub ramps between the two blades.

According to another preferred embodiment, the hub as the hub ring is formed having a substantially smaller axial dimension than the fan blades. So a cylindrical hub in the traditional sense is no longer present. The axial extent of the fan blades is - as mentioned above - referred to as chord length, which is a projection of the leaf width in the circumferential direction. The fan blades extend with both their front and with its rear edge over the end faces of the hub ring addition. Insofar as the straight line up to the innermost portion extending trailing edge forms an axial projection of the fan blade relative to the hub ring.

According to a further preferred embodiment, the axial fan has a hub ratio Dj / D a greater than 42%, wherein the boss ratio is the ratio of hub diameter and outer diameter of the fan blades is. The axial projection of the blade trailing edge in the inner area has a particularly beneficial in fans having a relatively large hub ratio, since this has an unfavorable effect on the efficiency and supported by the fan volume flow - in so far as there is here a compensation. The larger hub ratio can be, due to a smaller outside diameter result if the fan blades are reduced due to performance graduation. According to a further preferred embodiment of the axial-flow fan via its hub ring with a liquid friction clutch is fixedly connected, which in turn is driven by the internal combustion engine and drives the fan at a controlled output speed. At higher powers, the diameter of the fluid friction clutch and the hub diameter, which can lead to a larger hub ratio is growing. Here affects the leaf supernatant invention, which leads to an increase in efficiency and the volume flow, particularly positive.

According to a further preferred embodiment, the fan blades have a bend in the area of ​​Blattwurzei, resulting in the shape of a blade for the fan blade. Advantageously, in this case a low accumulation of material in the region of the connection of the fan blade and hub ring as well as an increased strength are.

Embodiments of the invention are shown in the drawings and will be described in more detail in the following, may result from the description and / or the drawing Additional features and / or advantages. Show it

Fig. 1 shows a fan blade configuration according to the prior art,

Fig. 2 shows a fan blade design of the invention with a stabilized flow,

Fig. 3 shows a detail of a fan according to the invention in SD representation,

Fig. 4 is a radial section through the fan hub,

Fig. 5 is a partial view of the axial fan with a sectional plane VI-VI, and

Fig. 6 shows the sectional view according to section plane VI-VI in Fig. 5.

Fig. 1 shows an arrangement of fan blades 1, 2 of an axial fan according to the prior art. The direction of rotation of the fan is indicated by an arrow D. The fan blades 1, 2 each have their pressure side hub ramps 3, 4 and sheet rear edges 1a, 2a. The trailing edge or trailing edges 1 a, 2a mentioned, have, in their radially inner region, d, h. inside the hub ramp 3, 4 respectively recesses or grooves 5, 6, such grooves and shortening of the fan blade width have been made in the prior art, because they on the one hand mean a saving in weight and it was felt on the other hand that the fan blade is of no more performance gain in root blade portion , Be disadvantageous, however, a transverse and / or Rückströ- mung has been found, which is indicated by arrows W. Due to the environmental flow of the blade trailing edge in the region of the groove 5, a vortex, represented by arrows W, which results to. a reduction of the fan efficiency, a reduction of the volume flow and an increased noise leads. Fig. 2 schematically shows an inventive configuration of fan blades 7, 8 and the blade trailing edges 7a, 8a. The direction of rotation of the axial fan is again indicated by an arrow D. To the pressure sides of the blades 7, 8 hub ramps 9, 10 are arranged, the soft blade trailing edges 7a, divided into a radially outer and a radially in- Neren portion 8a. According to the invention the radially inner region of the blade trailing edge 7 is substantially straight, that is to say the transition from the outer region to the inner region of a substantially straight course takes place. In other words, the blade width of the fan blade 7 is enlarged with respect to the blade width of the fan blade 1 according to the prior art in the radially inner portion so that no recess takes place.

This enlarged area is lifted hervor- by a boldface contour 7b. The effect of the increased blade width in the region 7b is a suppression of the lossy transverse shown in Fig. 1 and / or backflow. In particular, the flow shown by arrows S is radially largely undisturbed outside the hub ramp 10 on the fan blade. 8 On the other hand, is also formed below the hub ramp 10 and a relatively stable vortex-free flow, indicated by arrows P, from. The exten- sion of the blade trailing edge in the radially inner portion 7b, that is the magnification of the blade width brings a significant increase of the flow rate and efficiency and a reduction in noise.

By the terms blade width or sheet width, the distance between leading edge and trailing edge or the length of the chord of the blade or of the blade is to be understood. As a depth of the blade (blade chord) is understood as the projection of the blade width in the circumferential direction.

Fig. 3 shows a detail of an axial fan 11 according to the invention in 3D representation. The figure shows a hub ring 12, attached to which fan blades 13, 14, 15, that are molded integrally. The fan blades 13, 14, 15 each have their pressure sides hub ramps 13a, 14a, 15a which rise opposite the direction indicated by an arrow D direction of rotation. The hub ramps 13a, 14a, 5a are made strength strength keitsgründen with the hub ring at its bottom ribbed. The fan blades 13, 14, 15 each have rear edges 16, 17, 18, and trailing edges 16, 17, called 18, which extend substantially linearly from radially outside to radially inside. Through the downstream end of the hub ramps 13a, 14a, 15a, the rear edges 16, 17 are divided 18 into two sections, namely in radially outer portions or areas 16a, 17a, 18a, as well as in radially inner portions or areas 16b, 17b, 18b. The internal portions 16b, 17b, 18b of the blade trailing edges 16, 17, 18 go over a radius or fillet R in the free edges of the hub ramps 13a, 14a, 15a through, wherein the reference lines of the reference pay 13a, 14a, 15a of the free edges out. Thus, an optimized with respect to the strength of the fan structure is provided which is ge in the laser, the take during operation of the fan forces that occur, in particular centrifugal forces. The suction sides of the blades have fin-like stabilizers on the 19th Fig. 4 shows a radial section (section in a radial plane) through the hub ring 12 of the axial fan 1 1, wherein for identical parts the same reference numerals as in Fig. 3 are used. The air flow direction is indicated by an arrow L. The hub ring 12 has an axial extension a and the fan blade 14 has a depth t which - is defined as the projection of the blade width in the circumferential direction - as mentioned above. From the drawing it is clear that the blade depth t is substantially greater than the axial extent of the hub ring a 12th The blade depth t is in a preferred embodiment is approximately twice as large as the axial extension a of the hub ring 12. The trailing edge 17 of the fan blade 14 extends substantially in the radial direction linearly with the innermost portion of the trailing edge is rounded 17th The hub appears as a ramp-sectional area which is denoted by 14a.

Fig. 5 shows a view of an axial fan 20 is incomplete shown with a view towards the front side or the suction side of the fan blades 21, on which air guide elements 22 are arranged. The axial flow fan 20 includes fully a metallic support ring 23, which is connected both to the plastic hub of the axial fan 20 and a Flüssigkeitstreibungskupplung can be fastened on the other hand to a not-shown clutch, preferably. The fan blades designated by the reference numerals 21a, 21b, 21c are cut off in the section plane VI-VI.

Fig. 6 shows a sectional view of the axial fan 20 according to section plane VI-VI. The figure shows different sectional areas of the fan blades 21 a, 21b, 21c. As the sectional plane VI-VI indicated in FIG. 5, the fan blades 21 a, 21 b, 21c, cut in relation to its radial center line in different planes, with the sectional plane as the middle sheet 21b may be regarded as tangential and radial lies within the hub ramp, the cut surface of the blade 21c in Fig. 6 is located above the hub ramp "the designated here by the reference numeral 24 and not äst seen in Fig. 5 since it is arranged on the rear of the fan blades 21. 21b of the sectional area of ​​the central fan blade, the blade width b, ie, the distance between leading and trailing edges, are removed. The projection of the blade width b in the circumferential direction results in the (not illustrated) blade depth t, which is approximately constant over the entire radial region, namely at approximately rectilinear blade trailing edge.

Further features and preferred embodiments result from the above-mentioned earlier patent application of the applicant with the offi- borrowed file number 10 2010 042 325.4 - this older patent application is fully incorporated into the disclosure of the present application. Thereafter, it may be advantageous to kinking the fan blades in the direction of their blade roots, and to pull down the angled, inner region of the hub ring. The angled a shovel-like shape of the fan blade and a voltage-optimized transition between the fan blade and the hub ring can be achieved.

Claims

P atentanspr ü che
1. axial fan for conveying cooling air, in particular for an internal combustion engine of a motor vehicle, comprising on a hub (12) fixed, a pressure and a suction side, a trailing edge (16, 17, 18) and a blade chord (t) having fan blades (13, (14, 15), on the respective pressure side opposite to the rotational direction (D) of the axial fan 1: 1) increasing hub ramp (13a, 14a, 15a), said trailing edge (16, 17, 18) includes a radially (outside the hub ramp 13a, 14a, 15a) lying outer portion (16a, 17a, 18a) and a radially (within the hub ramp 13a, 14a, 15a) located inner region (16b, 17b, 18b), characterized in that the rear edge in the outer region radially outside the hub ramp identifies a profile which substantially continues over the radial position of the hub ramp away radially inwards in the inner region and extends unchanged in the radially innermost area toward the hub.
2. Axial fan according to claim 1, characterized in that the radially innermost area is the radially inner portion of the radius of the radially inner Beriechs.
3. Axial fan according to claim 2, characterized in that the proportion of about one third, about a quarter or preferably less than about one-fifth of the radius of the inner region of the trailing edge.
4. Axial fan according to one of the preceding claims, characterized in that the blade depth (t) in the inner area (16b, 17b, 18b) of the blade depth (t) in the outer region (16a, 17a, 8a) corresponds.
5. Axial fan according to one of the preceding claims, characterized in that the trailing edge (16, 17, 18) in the outer and in the inner region (16a, 16b, 17a, 17b, 18a, 18b) but not the innermost area is substantially as straight edge is formed.
6. Axial fan according to one of the preceding claims, characterized in that the trailing edge (16, 17, 18) is rounded in the innermost region and in the hub (12) merges
7. Axial fan according to one of the preceding claims, characterized in that the trailing edge (16, 17, 18) in its radially innermost portion through a rounded portion (R) in a free edge of the hub ramp (14a, 15a) passes.
8. Axial fan according to one of claims 1 to 7, characterized in that on the suction side of the fan blades (21) formed as stabilizers air guide elements (22) are arranged,
9. Axial fan according to claim 8, characterized in that the stabilizers (22) into the inner area (16b, 17b, 18b) extend to the trailing edges (16, 17, 18).
10. Axial fan according to one of claims 1 to 9, characterized in that the hub as the hub ring (2) having an axial extension (a) is formed, which is substantially smaller than the fan blade depth (t),
11. Axial fan according to one of claims 1 to 10, characterized in that the .Axiallüfter (11) has a hub ratio Dj / D a greater than 42%, where D is the outer diameter of the hub (12) and D a is the outside diameter of the fan blades (14).
12. Axial fan according to one of claims 1 to 11, characterized in that a fluid friction clutch disposed within the hub ring (12) and is fixedly connected to the hub ring (12). Axiaflüfter according to any one of the preceding claims, characterized in that the fan blades {13,14,15} are angled in the direction of its blade root, wherein the angled portion of the fan blade (13,14,15) at least partially on the hub, respectively, the hub ring (12 ) is pulled down,
PCT/EP2011/071579 2010-12-01 2011-12-01 Axial fan WO2012072779A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE102010062301.6 2010-12-01
DE201010062301 DE102010062301A1 (en) 2010-12-01 2010-12-01 Axial

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
EP20110790627 EP2646695B1 (en) 2010-12-01 2011-12-01 Axial fan
RU2013129920A RU2608800C2 (en) 2010-12-01 2011-12-01 Axial fan
KR20137017038A KR20140002690A (en) 2010-12-01 2011-12-01 Axial fan
US13991188 US20130323072A1 (en) 2010-12-01 2011-12-01 Axial fan
JP2013541366A JP6245437B2 (en) 2010-12-01 2011-12-01 Axial flow fan
CN 201180057601 CN103270311B (en) 2010-12-01 2011-12-01 Axial fan

Publications (1)

Publication Number Publication Date
WO2012072779A1 true true WO2012072779A1 (en) 2012-06-07

Family

ID=45065912

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/071579 WO2012072779A1 (en) 2010-12-01 2011-12-01 Axial fan

Country Status (8)

Country Link
US (1) US20130323072A1 (en)
EP (1) EP2646695B1 (en)
JP (1) JP6245437B2 (en)
KR (1) KR20140002690A (en)
CN (1) CN103270311B (en)
DE (1) DE102010062301A1 (en)
RU (1) RU2608800C2 (en)
WO (1) WO2012072779A1 (en)

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DE102014204043A1 (en) 2014-03-05 2015-09-10 MAHLE Behr GmbH & Co. KG Impeller of an axial fan

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CN103953567A (en) * 2014-05-16 2014-07-30 佟宝义 Carbon fiber fan blade for large and medium diesel engine radiator
US9869190B2 (en) 2014-05-30 2018-01-16 General Electric Company Variable-pitch rotor with remote counterweights
DE102014219023A1 (en) 2014-09-22 2016-03-24 Mahle International Gmbh Axial fan for conveying cooling air, in particular for an internal combustion engine of a motor vehicle
USD809121S1 (en) * 2016-04-26 2018-01-30 Parker-Hannifin Corporation Fan with integral airflow guide

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EP0515839A1 (en) 1991-05-27 1992-12-02 Behr GmbH & Co. Rotor for a mixed flow fan
DE19929978A1 (en) * 1999-06-30 2001-01-04 Behr Gmbh & Co Fan with axial blades, with air guide elements in entry-side region of hub and on induction side of blades
DE19929978B4 (en) 1999-06-30 2006-02-09 Behr Gmbh & Co. Kg Fan with axial blades
EP1219837A2 (en) * 2001-01-02 2002-07-03 Behr GmbH & Co. Fan with axial blades
DE112008001022T5 (en) * 2007-05-10 2010-06-10 Borgwarner Inc., Auburn Hills Synergistic vane and hub structure for cooling fan
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DE102014204043A1 (en) 2014-03-05 2015-09-10 MAHLE Behr GmbH & Co. KG Impeller of an axial fan
WO2015132077A1 (en) * 2014-03-05 2015-09-11 MAHLE Behr GmbH & Co. KG Fan wheel of an axial fan

Also Published As

Publication number Publication date Type
CN103270311B (en) 2017-05-31 grant
RU2013129920A (en) 2015-01-10 application
CN103270311A (en) 2013-08-28 application
EP2646695A1 (en) 2013-10-09 application
JP2013544337A (en) 2013-12-12 application
EP2646695B1 (en) 2017-07-12 grant
JP6245437B2 (en) 2017-12-13 grant
DE102010062301A1 (en) 2012-06-06 application
KR20140002690A (en) 2014-01-08 application
US20130323072A1 (en) 2013-12-05 application
RU2608800C2 (en) 2017-01-24 grant

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