EP2478226B1 - Fan for an internal combustion engine - Google Patents

Fan for an internal combustion engine Download PDF

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Publication number
EP2478226B1
EP2478226B1 EP10749878.4A EP10749878A EP2478226B1 EP 2478226 B1 EP2478226 B1 EP 2478226B1 EP 10749878 A EP10749878 A EP 10749878A EP 2478226 B1 EP2478226 B1 EP 2478226B1
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EP
European Patent Office
Prior art keywords
fan
fan blades
blades
ribs
different
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
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EP10749878.4A
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German (de)
French (fr)
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EP2478226A1 (en
Inventor
Ulrich Vollert
Dieter BÄCHNER
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Mahle Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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Publication of EP2478226A1 publication Critical patent/EP2478226A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/327—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with non identical blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/022—Units comprising pumps and their driving means comprising a yielding coupling, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/329—Details of the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Definitions

  • the invention relates to a fan according to the preamble of claim 1.
  • fans are known, with identical fan blades and identical fan blade connection geometries for all fan blades, ie a regularly repeated over the circumference of a fan housing geometry are configured.
  • a fan for an internal combustion engine which is drivable by means of a fluid friction clutch of an internal combustion engine via a drive shaft or a belt drive, wherein the fan has a fan housing with a plurality of fan blades formed thereon, and wherein the fan is designed such that it has different natural frequencies at least over a partial area.
  • the detuning of at least areas of the fan or the distribution of the natural frequencies caused by a corresponding design of the fan causes the reaction forces to be distributed over a broad frequency spectrum. This in turn causes the maximum component loads are reduced, so that the component costs can be reduced. Particularly distributive here is that cheaper bearings can be used.
  • At least two of the plurality of fan blades are designed such that they have different natural frequencies.
  • the reaction forces are advantageously minimized, so that in a structurally simple way, the cost, in particular the cost of the bearings can be reduced.
  • each of the plurality of fan blades is formed to have a natural frequency different from the other fan blades.
  • ribs are provided on each of the plurality of fan blades, the ribs being formed differently on at least two of the plurality of fan blades, particularly each of the plurality of fan blades.
  • a different number of ribs may be provided underneath each fan blade.
  • the ribs may be arranged differently with respect to their position and orientation.
  • the ribs are cooling fins.
  • the ribs are preferably arranged in the region of a hub of the fan.
  • At least two of the plurality of fan blades, in particular each of the plurality of fan blades, are formed with a different profile.
  • At least two of the plurality of fan blades, in particular each of the plurality of fan blades, have a different profile thickness distribution.
  • At least one of the plurality of fan blades is designed as a circular arc profile.
  • the maximum sheet thickness of at least one of the plurality of fan blades is shifted with respect to the center of the profile.
  • At least one of the plurality of fan blades has a local mass accumulation.
  • the local mass accumulation is provided in a blade tip region of the at least one of the plurality of fan blades. Also, a detuning of the fan blades can be achieved by material injections in a simple and thus cost-effective manner.
  • the fan has a flange, which is designed asymmetrically.
  • the flange ring is an insertion flange, which has a local weakening.
  • Fig. 1 shows a front view of a fan 1 in the air flow direction seen in the prior art, which is the promotion of cooling air through the radiator of a motor vehicle.
  • the fan 1 is designed as an axial fan and has eight axial blades or fan blades 2, which are arranged on a hub 4.
  • a fluid coupling 3 is provided, which has on its front side radially extending ribs 5, which serve as cooling ribs.
  • the fan 1 is connected in a manner not shown here with the output side of the fluid coupling.
  • the fluid coupling 3 is also driven via a central drive shaft 7.
  • the fluid coupling 3 ensures in a known manner that a fan blades 8 exhibiting fan blades 8 more or less fast depending on the cooling air temperature.
  • blade-shaped air guiding elements 6 are additionally arranged here, which serve to influence the air flow.
  • the direction of rotation of the fan is indicated by the arrow marked by A.
  • the fan blades 2 are arranged uniformly spaced around the circumference of the hub 4 and each have the same shape and size, d. H. All eight fan blades 2 are identical.
  • the cooling fins 5 are arranged uniformly or rotationally symmetrically about the axis of rotation of the drive shaft 7.
  • Fig. 2 is a sectional view of a profile of a single fan blade 2 according to the prior art.
  • This known profile of a Viscolmajers according to the prior art is designed as a circular arc profile, which has a thickness D 9 at a front edge 9 of the fan blade 2, which is identical to a thickness D 10 at a trailing edge 10 of the fan blade 2.
  • fan blade 2 is beyond the range of maximum thickness D max of the fan blade 2 in the middle M of the profile.
  • the natural frequency of the fan blade 2 can be easily changed. Also, a change in the natural frequency of the fan blade 2 can be caused by changing the thickness distribution of the profile. For example, it is possible to form the leading edge 9 with a different thickness D 9 than the thickness D 10 of the trailing edge 10 of the fan blade 2 to effect the change of the natural frequency of the fan blade 2.
  • Fig. 3 shows a front view of a portion in Lurtströmungsplatz a fan 1 according to an embodiment.
  • the fan 1 is provided with a plurality of fan blades 2, of which only a part is shown here, which on a hub 4 and a fan housing 12, in which also the fluid coupling 3 is received, are arranged.
  • the individual fan blades 2 differ in the embodiment in that they have different mass distributions from each other.
  • the fan blade 2 ' has a mass accumulation in a blade tip region 11.
  • the individual fan blades 2, 2 ' also have a different rigidity or material injections of different types.
  • Each of the already enumerated changes of the fan blades 2, 2 ' is suitable for causing a change in their natural frequency.

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

Description

Die Erfindung betrifft einen Lüfter gemäß, dem Oberbegriff des Anspruchs 1.The invention relates to a fan according to the preamble of claim 1.

Für die Kühlung von Nutzkraftfahrzeugen (NKW's) werden im Stand der Technik meist Lüfter eingesetzt, die über eine sogenannte Viscokupplung von einem Verbrennungsmotor angetrieben werden. Der Antrieb erfolgt wahlweise direkt über die Kurbelwelle oder über einen Riementrieb bzw. einen zahnradgetriebenen Nebenabtrieb des Motors. Dadurch wirken die Schwingbewegungen des Motors bzw. der Kurbelwelle stets auf den Lüfter. Dieser wiederum verursacht Reaktionskräfte auf diese Erregung, die über die Viscokupplung und deren Anbindung aufgenommen werden müssen. Entsprechend sind diese Bauteile so auszulegen, dass sie dieser starken Beanspruchung dauerhaft standhalten.For the cooling of commercial vehicles (commercial vehicles) fans are usually used in the prior art, which are driven by a so-called viscous coupling of an internal combustion engine. The drive is either directly via the crankshaft or via a belt drive or a gear-driven power take-off of the engine. As a result, the oscillating movements of the engine or the crankshaft always act on the fan. This in turn causes reaction forces to this excitation, which must be absorbed via the viscous coupling and their connection. Accordingly, these components are to be designed so that they can withstand such heavy use permanently.

Insbesondere bedingt durch neue Abgasnormen ist die Schwingungserregung der Motoren angestiegen, so dass die Anforderungen an die einzelnen Komponenten und damit auch deren Kosten ansteigen.In particular, due to new emission standards, the vibration excitation of the motors has increased, so that the demands on the individual components and thus their costs increase.

Im Stand der Technik sind Lüfter bekannt, die mit identischen Lüfterblättern und identischen Lüfterblattanbindungsgeometrien für alle Lüfterblätter, d. h. eine sich über dem Umfang eines Lüftergehäuses regelmäßig wiederholende Geometrie, konfiguriert sind.In the prior art fans are known, with identical fan blades and identical fan blade connection geometries for all fan blades, ie a regularly repeated over the circumference of a fan housing geometry are configured.

In DE 199 29 978 B4 ist ein Lüfter für eine Brennkraftmaschine mit Axialschaufeln beschrieben. Dabei sind auf einer Lüfternabe acht Axialschaufeln befestigt, und im inneren Bereich des Lüfters ist eine Flüssigkeitsreibungskupplung angeordnet, die auf ihrer Frontseite radial verlaufende Kühlrippen aufweist. Sowohl die acht Axialschaufeln als auch die Kühlrippen sind jeweils identisch zueinander aufgebaut und gleichmäßig bzw. regelmäßig beabstandet an dem Lüftergehäuse angeordnet.In DE 199 29 978 B4 is a fan for an internal combustion engine with axial blades described. In this case, eight axial blades are mounted on a fan hub, and in the inner region of the fan, a fluid friction clutch is arranged, which has on its front side radially extending cooling fins. Both the eight axial blades and the cooling fins are each constructed identically to one another and arranged uniformly or regularly spaced on the fan housing.

Nachteilig bei einem derartigen Aufbau ist jedoch, dass durch die Symmetrie der Lüfterblälter und ihrer identischen Geometrie die Eigenfrequenzen der einzelnen Lüfterblätter identisch sind. Somit treten die Resonanzen mit den damit verbundenen Reaktionskräften auch gleichzeitig auf und summieren sich entsprechend an den Anbauteilen, wie z. B. an der Viscokupplung, dem Lagerbock und der Anbindung. Dies verursacht hohe Kosten, das die Herstellung der Komponenten bzw. die zu verwendenden Materialien teuer sind.The disadvantage of such a construction, however, is that the natural frequencies of the individual fan blades are identical due to the symmetry of the fan blades and their identical geometry. Thus, the resonances occur with the associated reaction forces at the same time and add up accordingly to the attachments such. B. on the viscous coupling, the bearing block and the connection. This causes high costs, which are expensive to manufacture the components or the materials to be used.

Daher ist es die Aufgabe der vorliegenden Erfindung, einen Lüfter vorzusehen, bei dem sich die Eigenfrequenzen der einzelnen Lüfterblätter nicht an den Anbauteilen summieren, so dass die Material- und Herstellungskosten für diese Anbauteile reduziert werden können.Therefore, it is the object of the present invention to provide a fan in which the natural frequencies of the individual fan blades do not add up to the attachments, so that the material and manufacturing costs for these attachments can be reduced.

Die Aufgabe der vorliegenden Erfindung wird durch einen Lüfter mit den Merkmalen gemäß Anspruch 1 gelöst. Vorteilhafte Weiterbildungen der vorliegenden Erfindung sind in den Unteransprüchen definiert.The object of the present invention is achieved by a fan having the features according to claim 1. Advantageous developments of the present invention are defined in the subclaims.

Erfindungsgemäß wird ein Lüfter für eine Brennkraftmaschine vorgesehen, welcher mittels einer Flüssigkeitsreibungskupplung von einer Brennkraftmaschine über eine Antriebswelle oder einen Riementrieb antreibbar ist, wobei der Lüfter ein Lüftergehäuse mit einer daran ausgebildeten Vielzahl von Lüfterblättern aufweist, und wobei der Lüfter derartig ausgebildet ist, dass er zumindest über einen Teilbereich unterschiedliche Eigenfrequenzen aufweist. Durch das durch eine entsprechende Gestaltung des Lüfters bewirkte Verstimmen zumindest von Bereichen des Lüfters bzw. das Verteilen der Eigenfrequenzen wird bewirkt, dass sich auch die Reaktionskräfte auf ein breites Frequenzspektrum verteilen. Dies bewirkt wiederum, dass die maximalen Bauteilbelastungen reduziert werden, so dass sich die Bauteilkosten reduzieren lassen. Besonders verteilhaft ist hierbei, dass günstigere Lager eingesetzt werden können.According to the invention, a fan for an internal combustion engine is provided, which is drivable by means of a fluid friction clutch of an internal combustion engine via a drive shaft or a belt drive, wherein the fan has a fan housing with a plurality of fan blades formed thereon, and wherein the fan is designed such that it has different natural frequencies at least over a partial area. The detuning of at least areas of the fan or the distribution of the natural frequencies caused by a corresponding design of the fan causes the reaction forces to be distributed over a broad frequency spectrum. This in turn causes the maximum component loads are reduced, so that the component costs can be reduced. Particularly distributive here is that cheaper bearings can be used.

Gemäß einer bevorzugten Ausführungsform sind zumindest zwei der Vielzahl von Lüfterblättern derartig ausgebildet, dass sie unterschiedliche Eigenfrequenzen aufweisen. Durch Verstimmen der Lüfterblätter werden vorteilhafterweise die Reaktionskräfte minimiert, so dass auf konstruktiv einfache Art und Weise die Kosten, insbesondere die Kosten der Lager, reduziert werden können.According to a preferred embodiment, at least two of the plurality of fan blades are designed such that they have different natural frequencies. By detuning the fan blades, the reaction forces are advantageously minimized, so that in a structurally simple way, the cost, in particular the cost of the bearings can be reduced.

Gemäß noch einer bevorzugten Ausführungsform ist jedes von der Vielzahl von Lüfterblättern ausgebildet, um eine von den anderen Lüfterblättern unterschiedliche Eigenfrequenz aufzuweisen.According to another preferred embodiment, each of the plurality of fan blades is formed to have a natural frequency different from the other fan blades.

Gemäß noch einer weiteren bevorzugten Ausführungsform sind an jedem von der Vielzahl von Lüfterblättern Rippen vorgesehen, wobei die Rippen bei zumindest zweien von der Vielzahl von Lüfterblättern, insbesondere bei jedem von der Vielzahl von Lüfterblättern, unterschiedlich ausgebildet sind. Insbesondere kann eine unterschiedliche Anzahl von Rippen unterhalb eines jeden Lüfterblatts vorgesehen sein. Auch können die Rippen bezüglich ihrer Position und Ausrichtung unterschiedlich angeordnet sein. Vorzugsweise sind die Rippen Kühlrippen.According to still another preferred embodiment, ribs are provided on each of the plurality of fan blades, the ribs being formed differently on at least two of the plurality of fan blades, particularly each of the plurality of fan blades. In particular, a different number of ribs may be provided underneath each fan blade. Also, the ribs may be arranged differently with respect to their position and orientation. Preferably, the ribs are cooling fins.

Vorzugsweise sind die Rippen darüber hinaus im Bereich einer Nabe des Lüfters angeordnet.In addition, the ribs are preferably arranged in the region of a hub of the fan.

Noch bevorzugter ist es, wenn zumindest zwei von der Vielzahl von Lüfterblättern, insbesondere jedes von der Vielzahl von Lüfterblättern, mit einem unterschiedlichen Profil ausgebildet ist.It is even more preferable if at least two of the plurality of fan blades, in particular each of the plurality of fan blades, are formed with a different profile.

Es ist darüber hinaus bevorzugt, wenn zumindest zwei von der Vielzahl von Lüfterblättern, insbesondere jedes von der Vielzahl von Lüfterblättern, eine unterschiedliche Profildickenverteilung aufweist.It is also preferred if at least two of the plurality of fan blades, in particular each of the plurality of fan blades, have a different profile thickness distribution.

Gemäß einer weiteren bevorzugten Ausführungsform ist zumindest eines von der Vielzahl von Lüfterblättern als Kreisbogenprofil ausgebildet.According to a further preferred embodiment, at least one of the plurality of fan blades is designed as a circular arc profile.

In einer weiteren bevorzugten Ausführungsform ist die maximale Blattdicke von zumindest einem von der Vielzahl von Lüfterblättern bezüglich der Profilmitte verschoben.In another preferred embodiment, the maximum sheet thickness of at least one of the plurality of fan blades is shifted with respect to the center of the profile.

Vorzugsweise weist zumindest eines von der Vielzahl von Lüfterblättern eine lokale Massenanhäufung auf.Preferably, at least one of the plurality of fan blades has a local mass accumulation.

Es ist besonders bevorzugt, wenn die lokale Massenanhäufung in einem Blattspitzenbereich des zumindest einen von der Vielzahl von Lüfterblätter vorgesehen ist. Auch kann eine Verstimmung der Lüfterbläter durch Materialeinspritzungen auf einfache und somit kostengünstige Art und Weise erzielt werden.It is particularly preferred if the local mass accumulation is provided in a blade tip region of the at least one of the plurality of fan blades. Also, a detuning of the fan blades can be achieved by material injections in a simple and thus cost-effective manner.

Gemäß noch einer bevorzugten Ausführungsform weisen zumindest zwei von der Vielzahl von Lüfterblättern eine unterschiedliche Steifigkeit auf. Gemäß noch einer weiteren bevorzugten Ausführungsform weist der Lüfter einen Flanschring auf, welcher asymmetrisch ausgestaltet ist.According to yet another preferred embodiment, at least two of the plurality of fan blades have different stiffness. According to yet another preferred embodiment, the fan has a flange, which is designed asymmetrically.

Vorzugsweise ist der Flanschring ein Einlegeflansch, welcher eine lokale Schwächung aufweist.Preferably, the flange ring is an insertion flange, which has a local weakening.

Im Folgenden wird die Erfindung anhand eines Ausführungsbeispiels unter Bezugnahme auf die Zeichnung detailliert erläutert. In der Zeichnung zeigen:

Fig. 1
eine Vorderansicht eines Lüfters gemäß dem Stand der Technik;
Fig. 2
eine Schnittansicht eines Profils eines Lüfterblatts gemäß dem Stand der Technik.
Fig. 3
eine Vorderansicht eines Abschnitts eines Lüfters gemäß einer Ausführungsform.
In the following the invention will be explained in detail by means of an embodiment with reference to the drawing. In the drawing show:
Fig. 1
a front view of a fan according to the prior art;
Fig. 2
a sectional view of a profile of a fan blade according to the prior art.
Fig. 3
a front view of a portion of a fan according to an embodiment.

Fig. 1 zeigt eine Vorderansicht eines Lüfters 1 in Luftströmungsrichtung gesehen gemäß dem Stand der Technik, welcher der Förderung von Kühlluft durch den Kühler eines Kraftfahrzeugs dient. Der Lüfter 1 ist als Axiallüfter ausgebildet und weist acht Axialschaufeln bzw. Lüfterblätter 2 auf, die auf einer Nabe 4 angeordnet sind. Im radial inneren Bereich des Lüfters 1 ist eine Flüssigkeitskupplung 3 vorgesehen, die auf ihrer Frontseite radial verlaufende Rippen 5, die als Kühlrippen dienen, aufweist. Der Lüfter 1 ist in hier nicht dargestellter Weise mit der Abtriebsseite der Flüssigkeitskupplung verbunden. Die Flüssigkeitskupplung 3 wird darüber hinaus über eine zentrale Antriebswelle 7 angetrieben. Die Flüssigkeitskupplung 3 sorgt in bekannter Weise dafür, dass sich ein die Lüfterblätter 2 aufweisendes Lüfterrad 8 abhängig von der Kühllufttemperatur mehr oder weniger schnellt. Fig. 1 shows a front view of a fan 1 in the air flow direction seen in the prior art, which is the promotion of cooling air through the radiator of a motor vehicle. The fan 1 is designed as an axial fan and has eight axial blades or fan blades 2, which are arranged on a hub 4. In the radially inner region of the fan 1, a fluid coupling 3 is provided, which has on its front side radially extending ribs 5, which serve as cooling ribs. The fan 1 is connected in a manner not shown here with the output side of the fluid coupling. The fluid coupling 3 is also driven via a central drive shaft 7. The fluid coupling 3 ensures in a known manner that a fan blades 8 exhibiting fan blades 8 more or less fast depending on the cooling air temperature.

Im Bereich der Wurzeln der Lüfterblätter 2 sind hier zusätzlich schaufelförrnige Luftleitelemente 6 angeordnet, die der Beeinflussung der Luftströmung dienen. Zusätzlich ist in der Figur die Drehrichtung des Lüfters durch den durch A gekennzeichneten Pfeil angebeben. Die Lüfterblätter 2 sind um den Umfang der Nabe 4 gleichmäßig beabstandet angeordnet und weisen jeweils die gleiche Form und Größe auf, d. h. alle acht Lüfterblätter 2 sind identisch ausgebildet. Auch die Kühlrippen 5 sind gleichmäßig bzw. um die Drehachse der Antriebswelle 7 herum rotationssymmetrisch angeordnet.In the area of the roots of the fan blades 2, blade-shaped air guiding elements 6 are additionally arranged here, which serve to influence the air flow. In addition, in the figure, the direction of rotation of the fan is indicated by the arrow marked by A. The fan blades 2 are arranged uniformly spaced around the circumference of the hub 4 and each have the same shape and size, d. H. All eight fan blades 2 are identical. The cooling fins 5 are arranged uniformly or rotationally symmetrically about the axis of rotation of the drive shaft 7.

Fig. 2 ist eine Schnittansicht eines Profils eines einzelnen Lüfterblatts 2 gemäß dem Stand der Technik. Dieses bekannte Profil eines Viscolüfters gemäß dem Stand der Technik ist als Kreisbogenprofil ausgebildet, welches an einer Vorderkante 9 des Lüfterblatts 2 eine Dicke D9 aufweist, welche identisch mit einer Dicke D10 an einer Hinterkante 10 des Lüfterblatts 2 ist. Bei diesem aus dem Stand der Technik bekannten Lüfterblatt 2 liegt darüber hinaus der Bereich von maximaler Dicke Dmax des Lüfterblatts 2 in der Mitte M des Profils. Fig. 2 is a sectional view of a profile of a single fan blade 2 according to the prior art. This known profile of a Viscolüfters according to the prior art is designed as a circular arc profile, which has a thickness D 9 at a front edge 9 of the fan blade 2, which is identical to a thickness D 10 at a trailing edge 10 of the fan blade 2. In this known from the prior art fan blade 2 is beyond the range of maximum thickness D max of the fan blade 2 in the middle M of the profile.

Durch eine Verschiebung der Position der maximalen Blattdicke Dmax aus der mittleren Position M heraus, z. B. nach rechts oder nach links, kann die Eigenfrequenz des Lüfterblatts 2 auf einfache Weise verändert werden. Auch kann eine Änderung der Eigenfrequenz des Lüfterblatts 2 durch Veränderung der Dickenverteilung des Profils hervorgerufen werden. Beispielsweise ist es möglich, die Vorderkante 9 mit einer anderen Dicke D9 als die Dicke D10 der Hinterkante 10 des Lüfterblatts 2 auszubilden, um die Änderung der Eigenfrequenz des Lüfterblatts 2 zu bewirken.By shifting the position of the maximum sheet thickness D max out of the middle position M, e.g. B. to the right or to the left, the natural frequency of the fan blade 2 can be easily changed. Also, a change in the natural frequency of the fan blade 2 can be caused by changing the thickness distribution of the profile. For example, it is possible to form the leading edge 9 with a different thickness D 9 than the thickness D 10 of the trailing edge 10 of the fan blade 2 to effect the change of the natural frequency of the fan blade 2.

Fig. 3 zeigt eine Vorderansicht eines Abschnitts in Lurtströmungsrichtung eines Lüfters 1 gemäß einer Ausführungsform. Der Lüfter 1 ist mit einer Vielzahl von Lüfterblättern 2 versehen, von welchen hier nur ein Teil dargestellt ist, welche auf einer Nabe 4 bzw. einem Lüftergehäuse 12, in welchem auch die Flüssigkeitskupplung 3 aufgenommen ist, angeordnet sind. Die einzelnen Lüfterblätter 2 unterscheiden sich in der Ausführungsform dadurch, dass sie voneinander unterschiedliche Massenverteilungen aufweisen. Zum Beispiel weist das Lüfterblatt 2' eine Massenanhäufung in einem Blattspitzenbereich 11 auf. Alternativ können die einzelnen Lüfterblätter 2, 2' auch eine unterschiedliche Steifigkeit oder Materialeinspritzungen unterschiedlicher Art aufweisen. Jede der bereits aufgezählten Veränderungen der Lüfterblätter 2, 2' ist geeignet, um eine Änderung ihrer Eigenfrequenz zu verursachen. Es ist dabei auch möglich, einzelne Lüfterblätter 2 unterschiedlich auszugestalten, oder aber auch die Lüfterblätter 2 gruppenweise unterschiedlich auszugestalten, z. B. in Gruppen von jeweils 2, 3 oder 4 Lüfterblättern 2. Alternativ oder zusätzlich ist es möglich, die Rippen 5, 5' welche im Bereich der Nabe 4 angeordnet sind, unterschiedlich zu gestalten. Hier kann eine Variation der Eigenfrequenz des Lüfters 1 erzielt werden, wenn beispielsweise einzelne Rippen 5 im Bereich der Nabe 4 weggelassen werden, oder es werden Rippen 5' zusätzlich vorgesehen. Eine weitere Möglichkeit, um eine Änderung der Eigenfrequenz des Lüfters 1 zumindest in einem Bereich zu verursachen, ist durch die gestrichelte und durch das Bezugszeichen 13 gekennzeichnete Linie angedeutet. Hierbei wird ein Flanschring 14, der hier als Einlegeflansch ausgebildet ist, lokal geschwächt durch Entfernen des Materials in einem Bereich bzw, in der Zeichnung links von der gestrichelten Linie 13. Fig. 3 shows a front view of a portion in Lurtströmungsrichtung a fan 1 according to an embodiment. The fan 1 is provided with a plurality of fan blades 2, of which only a part is shown here, which on a hub 4 and a fan housing 12, in which also the fluid coupling 3 is received, are arranged. The individual fan blades 2 differ in the embodiment in that they have different mass distributions from each other. For example, the fan blade 2 'has a mass accumulation in a blade tip region 11. Alternatively, the individual fan blades 2, 2 'also have a different rigidity or material injections of different types. Each of the already enumerated changes of the fan blades 2, 2 'is suitable for causing a change in their natural frequency. It is also possible to design individual fan blades 2 different, or even the fan blades 2 groups differently designed, z. B. in groups of 2, 3 or 4 fan blades 2. Alternatively or additionally, it is possible, the ribs 5, 5 'which are arranged in the region of the hub 4, to make different. Here, a variation of the natural frequency of the fan 1 can be achieved, for example, if individual ribs 5 are omitted in the region of the hub 4, or ribs 5 'are additionally provided. Another possibility for causing a change in the natural frequency of the fan 1, at least in one area, is indicated by the dashed line indicated by the reference numeral 13. Here, a flange 14, which is designed here as an insert flange, weakened locally by removing the material in an area or, in the drawing, left of the dashed line 13th

Insgesamt betrachtet kann mit dem so ausgestalteten Lüfter 1 eine erhebliche Kostenersparnis erzielt werden, insbesondere im Hinblick auf die Komponenten der Flüssigkeitsreibungskupplung 3 und eines Lagerbocks.Overall, can be achieved with the so-designed fan 1 a significant cost savings, especially with regard to the components of the fluid friction clutch 3 and a bearing block.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
LüfterFan
22
Lüfterblätterfan blades
33
Flüssigkeitskupplungfluid coupling
44
Nabehub
55
Rippenribs
66
Luftleitelementeair guide elements
77
Antriebswelledrive shaft
88th
Lüfterradfan
99
Vorderkanteleading edge
1010
Hinterkantetrailing edge
1111
BlatlspitzenbereichBlatlspitzenbereich
1212
Lüftergehäusefan housing
1313
gestrichelte Liniedashed line
1414
Flanschringflange

Claims (15)

  1. A fan (1) for an internal combustion engine that can be driven by means of a fluid friction clutch (3) of an internal combustion engine via a drive shaft or a belt drive, wherein the fan (1) has a fan housing (12) with a plurality of fan blades (2, 2') formed thereon, wherein the fan (1) is designed such that it has different natural frequencies, at least over a portion, characterised in that ribs (5) are provided on each of the plurality of fan blades (2, 2'), wherein the ribs (5, 5') are provided differently on at least two of the plurality of fan blades (2, 2').
  2. The fan according to claim 1, characterised in that the ribs are provided differently on each of the plurality of fan blades (2, 2').
  3. The fan according to claim 1 or 2, characterised in that the ribs are provided in different numbers.
  4. The fan (1) according to claim 1, 2 or 3, characterised in that at least two of the plurality of fan blades (2, 2') are designed such that they have different natural frequencies.
  5. The fan (1) according to one of the preceding claims 1 to 4, characterised in that each of the plurality of fan blades (2, 2') is designed to have a natural frequency different from the one of the other fan blades (2, 2').
  6. The fan (1) according to one or more of the claims 1 to 5, characterised in that the ribs (5, 5') are arranged in the area of a hub (4) of the fan (1).
  7. The fan (1) according to one or more of the claims 1 to 6, characterised in that at least two of the plurality of fan blades (2, 2'), in particular each of the plurality of fan blades (2, 2'), are designed with a different profile.
  8. The fan (1) according to one of the claims 1 to 7, characterised in that at least two of the plurality of fan blades (2, 2'), in particular each of the plurality of fan blades (2, 2'), have a different profile thickness distribution.
  9. The fan (1) according to claim 8, characterised in that at least one of the plurality of fan blades (2, 2')is formed as an arcuate profile.
  10. The fan (1) according to one or more of the claims 1 to 9, characterised in that the maximum blade thickness Dmax of at least one of the plurality of fan blades (2, 2') is shifted with regard to the centre of the profile (M).
  11. The fan (1) according to one or more of the claims 1 to 10, characterised in that at least one of the plurality of fan blades (2, 2') has a local mass accumulation.
  12. The fan (1) according to claim 11, characterised in that the local mass accumulation is provided in a blade tip area (11) of the at least one of the plurality of fan blades (2, 2').
  13. The fan (1) according to one or more of the claims 1 to 12, characterised in that at least two of the plurality of fan blades (2, 2') have a different stiffness.
  14. The fan (1) according to one or more of the claims 1 to 13, characterised in that the fan has a flange ring (14) which is asymmetrically designed.
  15. The fan (1) according to claim 14, characterised in that the flange ring (14) is an insertion flange having a local weakening.
EP10749878.4A 2009-09-17 2010-09-08 Fan for an internal combustion engine Not-in-force EP2478226B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910041616 DE102009041616A1 (en) 2009-09-17 2009-09-17 Fan for an internal combustion engine
PCT/EP2010/063166 WO2011032867A1 (en) 2009-09-17 2010-09-08 Fan for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2478226A1 EP2478226A1 (en) 2012-07-25
EP2478226B1 true EP2478226B1 (en) 2016-02-10

Family

ID=43066520

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10749878.4A Not-in-force EP2478226B1 (en) 2009-09-17 2010-09-08 Fan for an internal combustion engine

Country Status (3)

Country Link
EP (1) EP2478226B1 (en)
DE (1) DE102009041616A1 (en)
WO (1) WO2011032867A1 (en)

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JP6234589B2 (en) * 2014-08-07 2017-11-22 三菱電機株式会社 Axial flow fan and air conditioner having the axial flow fan
USD860427S1 (en) 2017-09-18 2019-09-17 Horton, Inc. Ring fan

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DE3716326A1 (en) * 1987-05-15 1988-12-01 Schempp Hirth Gmbh & Co Kg Propeller
DE3832026A1 (en) * 1988-09-21 1990-03-22 Bosch Gmbh Robert FAN WHEEL
DE4020742A1 (en) * 1990-06-29 1992-01-02 Behr Gmbh & Co IMPELLER FOR A FAN
DE4140987A1 (en) * 1991-12-12 1993-06-17 Behr Gmbh & Co AXIAL FAN
DE29614608U1 (en) * 1996-08-22 1996-12-12 Georg Kick Fa Wheel
US6073593A (en) * 1997-12-08 2000-06-13 Harvard Industries, Inc. Plastic fan and thermal clutch drive
FR2772830B1 (en) * 1997-12-23 2000-11-24 Valeo Thermique Moteur Sa FAN FOR A HEAT EXCHANGER, PARTICULARLY FOR A MOTOR VEHICLE
DE19929978B4 (en) 1999-06-30 2006-02-09 Behr Gmbh & Co. Kg Fan with axial blades
DE10100064A1 (en) * 1999-06-30 2002-07-04 Behr Gmbh & Co Fan with axial blades, particularly for read vehicle radiator, has axial blades fixed to nave, with air guide components arranged in nave area and on suction side of axial blades, air guide components being formed as fin-type stabilizers
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Also Published As

Publication number Publication date
EP2478226A1 (en) 2012-07-25
WO2011032867A1 (en) 2011-03-24
DE102009041616A1 (en) 2011-03-24

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