EP1851443B1 - Axial ventilator - Google Patents
Axial ventilator Download PDFInfo
- Publication number
- EP1851443B1 EP1851443B1 EP06706737A EP06706737A EP1851443B1 EP 1851443 B1 EP1851443 B1 EP 1851443B1 EP 06706737 A EP06706737 A EP 06706737A EP 06706737 A EP06706737 A EP 06706737A EP 1851443 B1 EP1851443 B1 EP 1851443B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fan
- axial
- air flow
- passage area
- hub
- 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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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
- F04D29/386—Skewed blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/10—Geometry two-dimensional
- F05B2250/16—Geometry two-dimensional parabolic
Definitions
- the invention relates to an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are fixed to the fan blades, which are bounded radially inwardly by an inner diameter and radially outside of an outer diameter.
- Such a fan has the task of providing a sufficient amount of cooling air when the wind is insufficient, for example, when driving slowly or when the vehicle is stationary.
- the required delivery volume of the fan is very different.
- the pressure build-up required to deliver the cooling air flow is provided by the fan.
- the fan obstructs the flow of air, increasing the dynamic pressure.
- an axial fan with a surrounding structure of the fan To form a labyrinth seal between the fan and the structure, the structure has radially inwardly a groove formed by wall portions.
- an impeller for a semi-axial fan is described with a hub which is provided with a hub ramp.
- the hub ramp is designed such that the hub radius is constant in the axial direction, but increases in the circumferential direction counter to the direction of rotation.
- the object of the invention is to provide an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are attached to the fan blades, which are bounded radially inward by an inner diameter and radially outward of an outer diameter, the compact is designed and designed so that it generates a large mass flow at high pressure during operation.
- an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are fixed to the fan blades, which are bounded radially inwardly by an inner diameter and radially outside of an outer diameter, achieved in that the ratio between the inner diameter and the outer diameter is greater than 40 percent.
- the dimensions of the enclosed between the inner and outer diameter fan passage area are adapted in conventional fans for the cooling of an internal combustion engine to the size of the radiator to ensure a sufficiently large air passage area even when driving fast and with the fan off.
- a fan is provided which is as small as possible, so that a venetian blind, which releases an additional air passage area during high-speed travel, can be as large as possible.
- the ratio between the inner diameter and the outer diameter of the fan passage area is referred to as hub ratio.
- the hub ratio according to the invention creates an axial fan with a high power density.
- a preferred embodiment of the axial fan is characterized in that the ratio of the projecting from the fan blades on the fan passage surface fan blade surfaces to the annular fan passage area is greater than 60 percent.
- the ratio of the fan blade areas projected from the fan blades to the fan passage area to the annular fan passage area is also referred to as the coverage ratio.
- the covering ratio according to the invention ensures that the fan generates sufficient airflow at normal speeds.
- Another preferred embodiment of the axial fan is characterized in that the fan blades are sown in a direction opposite to the air flow direction.
- the crescent-shaped design of the fan blades has proved to be particularly advantageous in the context of the present invention.
- a further preferred embodiment of the axial fan is characterized in that the front edge of the fan blades is a parabolfömigen History has.
- the parabolic formation of the leading edges of the fan blades has proven to be particularly advantageous in the context of the present invention.
- a further preferred exemplary embodiment of the axial fan is characterized in that the origin or apex of the parabola coincides with the intersection of the outside diameter of the fan passage area with the front edge of the associated fan blade.
- a further preferred embodiment of the axial fan is characterized in that the angle of attack at the front edge of the fan blades over the radius of the fan passage surface is greater than 20 degrees.
- An angle of attack is the angle enclosed between a radius and a tangent to the leading edge of a fan blade.
- Another preferred embodiment of the axial fan is characterized in that the profile length of the fan blades over the radius of the fan passage area is almost constant.
- the profile length is the extent of the fan blades in the air flow direction or in the axial direction.
- Another preferred exemplary embodiment of the axial fan is characterized in that the deviations of the profile length from a mean profile length are less than +/- 6 percent.
- a cooler for an internal combustion engine in particular of a motor vehicle, which is flowed through by a medium, in particular of coolant, which serves for example for cooling the internal combustion engine, and which has an air passage area
- a medium in particular of coolant, which serves for example for cooling the internal combustion engine, and which has an air passage area
- the first air flow path is traversed, which is closed by a shutter, and is flowed through in a so-called fan operation of an air flow along a second air flow path
- the above-stated object is achieved in that the second air flow path through a previously described Fan runs, which is arranged between the radiator and the internal combustion engine.
- FIG. 1 shows an axial fan 1, which includes a hub 2, are attached to the nine fan blades 11 to 19.
- the hub is driven clockwise by, for example, a fluid friction clutch or electric motor (not shown).
- the unit consisting of the axial fan 1 and the fluid friction clutch serves to convey cooling air through the radiator of a motor vehicle.
- the structure and function of a motor vehicle radiator are assumed to be known and not further explained here.
- the fan blades 11 to 19 have a common inner diameter Di and a common outer diameter Da on. Between the inner diameter Di and the outer diameter Da, the axial fan 1 has an annular passage area for air. When the hub 2 is rotated, then the fan blades 11 to 19 rotate in a clockwise direction, as indicated by an arrow 26. Each fan blade 11 to 19 has a front edge which is parabolic. The leading edge of the fan blade 11 is denoted by 28. The leading edge of the fan blade 12 is designated 29. At the front edge 28 of the fan blade 11 is a part of a Parabola 30 drawn whose vertex or origin 31 coincides with the intersection of the leading edge 28 and the outer diameter Da.
- the leading edge 29 of the fan blade 12 has an angle of attack ⁇ connected between a tangent to the leading edge and the associated radius. Between a tangent T1 and a radius R1 an angle of attack ⁇ 1 is included. Between a tangent T2 and a radius R2 an angle of attack ⁇ 2 is included. Between a tangent T3 and a radius R3 an angle of attack ⁇ 3 is included.
- the angles of attack ⁇ 1 to ⁇ 3 are each about 40 degrees.
- FIG. 2 is the axial fan 1 off FIG. 1 in the same view as in FIG. 1 illustrated, wherein the fan blades 11 to 19 in the provided between the outer diameter Da and the inner diameter Di ring surface projected fan blade surfaces are hatched.
- the ratio of the projected leaf areas to the annular area of the axial fan 1 is referred to as the coverage ratio.
- the blade width of the fan blades 11 to 19 is selected so that a coverage ratio of more than 60 percent results.
- the ratio of the inner diameter Di to the outer diameter Da is referred to as a hub ratio and is more than 40 percent in the axial fan 1 according to the invention.
- the fan blades 11 to 19 of the axial fan 1 are sown backwards.
- the angles ⁇ 1 to ⁇ 3 (see FIG. 1 ) between the leading edge 29 and the associated radius R1, R2, R3 is always greater than 20 degrees. According to an embodiment, not shown, the fan blades of the axial fan are sown forward.
- the flat front edges all follow a parabolic course, as illustrated by the front edge 28 of the fan blade 11.
- the origin of the parabola is at the junction between the leading edge of the blade 28 and the outside diameter Da, which is also referred to as a jacket.
- the profile lengths are almost constant over the radius. The deviations from the average profile length are less than + / 6 percent.
- the inventive design allows a very compact fan design. Due to the very compact axial fan 1, the shutter area of the radiator can be correspondingly large.
- hub ramps may be provided in the axial fan according to the invention, which may be provided on the hub of the fan.
- hub ramps may be provided on the pressure side of the fan, in each case opposite to the direction of rotation rising hub ramps can be provided, which are limited in each case to the outside by an outer surface.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft einen Axiallüfter für einen Kühler einer Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, mit einer drehbar angetriebenen Nabe, an der Lüfterblätter befestigt sind, die radial innen von einem Innendurchmesser und radial außen von einem Außendurchmesser begrenzt werden.The invention relates to an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are fixed to the fan blades, which are bounded radially inwardly by an inner diameter and radially outside of an outer diameter.
Ein derartiger Lüfter hat die Aufgabe, für eine ausreichende Kühlluftmenge zu sorgen, wenn der Fahrtwind nicht ausreicht, zum Beispiel bei langsamer Fahrt oder bei Stillstand des Fahrzeugs. Je nach Betriebszustand des Fahrzeugs ist das erforderliche Fördervolumen des Lüfters sehr unterschiedlich. Bei niedrigen Geschwindigkeiten wird der für die Förderung der Kühlluftströmung nötige Druckaufbau von dem Lüfter bereitgestellt. Bei hohen Geschwindigkeiten behindert der Lüfter die Luftströmung, wodurch der Staudruck ansteigt.Such a fan has the task of providing a sufficient amount of cooling air when the wind is insufficient, for example, when driving slowly or when the vehicle is stationary. Depending on the operating state of the vehicle, the required delivery volume of the fan is very different. At low speeds, the pressure build-up required to deliver the cooling air flow is provided by the fan. At high speeds, the fan obstructs the flow of air, increasing the dynamic pressure.
In der
In der
In der
Aufgabe der Erfindung ist es, einen Axiallüfter für einen Kühler einer Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, mit einer drehbar angetriebenen Nabe, an der Lüfterblätter befestigt sind, die radial innen von einem Innendurchmesser und radial außen von einem Außendurchmesser begrenzt werden, zu schaffen, der kompakt ausgebildet und so ausgelegt ist, dass er im Betrieb einen großen Massenstrom mit einem hohen Druck erzeugt.The object of the invention is to provide an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are attached to the fan blades, which are bounded radially inward by an inner diameter and radially outward of an outer diameter, the compact is designed and designed so that it generates a large mass flow at high pressure during operation.
Die Aufgabe ist bei einem Axiallüfter für einen Kühler einer Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, mit einer drehbar angetriebenen Nabe, an der Lüfterblätter befestigt sind, die radial innen von einem Innendurchmesser und radial außen von einem Außendurchmesser begrenzt werden, dadurch gelöst, dass das Verhältnis zwischen dem Innendurchmesser und dem Außendurchmesser größer als 40 Prozent ist. Die Abmessungen der zwischen dem Innen- und dem Außendurchmesser eingeschlossenen Lüfterdurchtrittsfläche werden bei herkömmlichen Lüftern für die Kühlung einer Brennkraftmaschine an die Größe des Kühlers angepasst, um auch bei Schnellfahrt und bei ausgeschaltetem Lüfter eine ausreichend große Luftdurchtrittsfläche zu gewährleisten. Gemäß der vorliegenden Erfindung wird ein Lüfter geschaffen, der möglichst klein ist, damit eine Jalousie, die bei Schnellfahrt eine zusätzliche Luftdurchtrittsfläche freigibt, möglichst groß sein kann. Das Verhältnis zwischen dem Innendurchmesser und dem Außendurchmesser der Lüfterdurchtrittsfläche wird als Nabenverhältnis bezeichnet. Durch das erfindungsgemäße Nabenverhältnis wird ein Axiallüfter mit einer hohen Leistungsdichte geschaffen.The object is achieved with an axial fan for a radiator of an internal combustion engine, in particular of a motor vehicle, with a rotatably driven hub, are fixed to the fan blades, which are bounded radially inwardly by an inner diameter and radially outside of an outer diameter, achieved in that the ratio between the inner diameter and the outer diameter is greater than 40 percent. The dimensions of the enclosed between the inner and outer diameter fan passage area are adapted in conventional fans for the cooling of an internal combustion engine to the size of the radiator to ensure a sufficiently large air passage area even when driving fast and with the fan off. According to the present invention, a fan is provided which is as small as possible, so that a venetian blind, which releases an additional air passage area during high-speed travel, can be as large as possible. The ratio between the inner diameter and the outer diameter of the fan passage area is referred to as hub ratio. The hub ratio according to the invention creates an axial fan with a high power density.
Ein bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass das Verhältnis der von den Lüfterblättern auf die Lüfterdurchtrittsfläche projizierten Lüfterblattflächen zu der ringförmigen Lüfterdurchtrittsfläche größer als 60 Prozent ist. Das Verhältnis der von den Lüfterblättern auf die Lüfterdurchtrittsfläche projizierten Lüfterblattflächen zu der ringförmigen Lüfterdurchtrittsfläche wird auch als Abdeckverhältnis bezeichnet. Durch das erfindungsgemäße Abdeckverhältnis wird sichergestellt, dass der Lüfter bei normalen Drehzahlen eine ausreichende Luftströmung erzeugt.A preferred embodiment of the axial fan is characterized in that the ratio of the projecting from the fan blades on the fan passage surface fan blade surfaces to the annular fan passage area is greater than 60 percent. The ratio of the fan blade areas projected from the fan blades to the fan passage area to the annular fan passage area is also referred to as the coverage ratio. The covering ratio according to the invention ensures that the fan generates sufficient airflow at normal speeds.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass die Lüfterblätter in einer der Luftdurchströmungsrichtung entgegengesetzten Richtung gesichelt sind. Die sichelförmige Ausbildung der Lüfterblätter hat sich im Rahmen der vorliegenden Erfindung als besonders vorteilhaft erwiesen.Another preferred embodiment of the axial fan is characterized in that the fan blades are sown in a direction opposite to the air flow direction. The crescent-shaped design of the fan blades has proved to be particularly advantageous in the context of the present invention.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass die Vorderkante der Lüfterblätter einen parabelfömigen Verlauf aufweist. Die parabelförmige Ausbildung der Vorderkanten der Lüfterblätter hat sich im Rahmen der vorliegenden Erfindung als besonders vorteilhaft erwiesen.A further preferred embodiment of the axial fan is characterized in that the front edge of the fan blades is a parabolfömigen History has. The parabolic formation of the leading edges of the fan blades has proven to be particularly advantageous in the context of the present invention.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass der Ursprung beziehungsweise Scheitelpunkt der Parabel mit dem Schnittpunkt des Außendurchmessers der Lüfterdurchtrittsfläche mit der Vorderkante des zugehörigen Lüfterblatts zusammenfällt.A further preferred exemplary embodiment of the axial fan is characterized in that the origin or apex of the parabola coincides with the intersection of the outside diameter of the fan passage area with the front edge of the associated fan blade.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass der Anstellwinkel an der Vorderkante der Lüfterblätter über den Radius der Lüfterdurchtrittsfläche größer als 20 Grad ist. Als Anstellwinkel wird der Winkel bezeichnet, der zwischen einem Radius und einer Tangente an die Vorderkante eines Lüfterblatts eingeschlossen ist.A further preferred embodiment of the axial fan is characterized in that the angle of attack at the front edge of the fan blades over the radius of the fan passage surface is greater than 20 degrees. An angle of attack is the angle enclosed between a radius and a tangent to the leading edge of a fan blade.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass die Profillänge der Lüfterblätter über den Radius der Lüfterdurchtrittsfläche nahezu konstant ist. Als Profillänge wird die Ausdehnung der Lüfterblätter in Luftdurchströmungsrichtung beziehungsweise in axialer Richtung bezeichnet.Another preferred embodiment of the axial fan is characterized in that the profile length of the fan blades over the radius of the fan passage area is almost constant. The profile length is the extent of the fan blades in the air flow direction or in the axial direction.
Ein weiteres bevorzugtes Ausführungsbeispiel des Axiallüfters ist dadurch gekennzeichnet, dass die Abweichungen der Profillänge von einer mittleren Profillänge kleiner als +/- 6 Prozent sind.Another preferred exemplary embodiment of the axial fan is characterized in that the deviations of the profile length from a mean profile length are less than +/- 6 percent.
Bei einem Kühler für eine Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, der von einem Medium, insbesondere von Kühlmittel, durchströmt wird, das zum Beispiel zur Kühlung der Brennkraftmaschine dient, und der eine Luftdurchtrittsfläche aufweist, die in einem so genannten Staudruckbetrieb, von einer Luftströmung entlang einem ersten Luftströmungspfad durchströmt wird, der durch eine Jalousie verschließbar ist, und der in einem so genannten Lüfterbetrieb von einer Luftströmung entlang einem zweiten Luftströmungspfad durchströmt wird, ist die vorab angegebene Aufgabe dadurch gelöst, dass der zweite Luftströmungspfad durch einen vorab beschriebenen Lüfter verläuft, der zwischen dem Kühler und der Brennkraftmaschine angeordnet ist.In a cooler for an internal combustion engine, in particular of a motor vehicle, which is flowed through by a medium, in particular of coolant, which serves for example for cooling the internal combustion engine, and which has an air passage area, in a so-called dynamic pressure operation of an air flow along a The first air flow path is traversed, which is closed by a shutter, and is flowed through in a so-called fan operation of an air flow along a second air flow path, the above-stated object is achieved in that the second air flow path through a previously described Fan runs, which is arranged between the radiator and the internal combustion engine.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung ein Ausführungsbeispiel im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. Es zeigen:
- Figur 1
- eine schematische Darstellung eines erfindungsgemäßen Axiallüfters in der Draufsicht und
Figur 2- den Axiallüfter aus
Figur 1 , wobei die von den Lüfterblättern auf die Lüfterdurchtrittsfläche projizierten Lüfterblattflächen schraffiert sind.
- FIG. 1
- a schematic representation of an axial fan according to the invention in plan view and
- FIG. 2
- the axial fan off
FIG. 1 wherein the fan blade surfaces projected from the fan blades onto the fan passage surface are hatched.
Die Lüfterblätter 11 bis 19 weisen einen gemeinsamen Innendurchmesser Di und einen gemeinsamen Außendurchmesser Da auf. Zwischen dem Innendurchmesser Di und dem Außendurchmesser Da weist der Axiallüfter 1 eine ringförmige Durchtrittsfläche für Luft auf. Wenn die Nabe 2 in Drehung versetzt wird, dann drehen sich die Lüfterblätter 11 bis 19 im Uhrzeigersinn, wie durch einen Pfeil 26 angedeutet ist. Jedes Lüfterblatt 11 bis 19 weist eine Vorderkante auf, die parabelfömig ausgebildet ist. Die Vorderkante des Lüfterblatts 11 ist mit 28 bezeichnet. Die Vorderkante des Lüfterblatts 12 ist mit 29 bezeichnet. An der Vorderkante 28 des Lüfterblatts 11 ist ein Teil einer Parabel 30 eingezeichnet, deren Scheitelpunkt oder Ursprung 31 mit dem Schnittpunkt der Vorderkante 28 und dem Außendurchmesser Da zusammenfällt.The
Die Vorderkante 29 des Lüfterblatts 12 weist einen Anstellwinkel α auf, der zwischen einer Tangente an die Vorderkante und dem zugehörigen Radius angeschlossen ist. Zwischen einer Tangente T1 und einem Radius R1 ist ein Anstellwinkel α1 eingeschlossen. Zwischen einer Tangente T2 und einem Radius R2 ist ein Anstellwinkel α2 eingeschlossen. Zwischen einer Tangente T3 und einem Radius R3 ist ein Anstellwinkel α3 eingeschlossen. Die Anstellwinkel α1 bis α3 betragen jeweils etwa 40 Grad.The leading
In
Die Plattvorderkanten folgen alle einem parabelförmigen Verlauf, wie anhand der Vorderkante 28 des Lüfterblatts 11 verdeutlicht ist. Der Ursprung der Parabel ist an der Verbindung zwischen der Blattvorderkante 28 und dem Außendurchmesser Da, der auch als Mantel bezeichnet wird. Die Profillängen sind nahezu konstant über dem Radius. Die Abweichungen von der mittleren Profillänge sind kleiner als +/ 6 Prozent. Durch die erfindungsgemäße Auslegung wird eine sehr kompakte Lüfterbauform ermöglicht. Durch den sehr kompakten Axiallüfter 1 kann die Jalousiefläche des Kühlers entsprechend groß ausfallen.The flat front edges all follow a parabolic course, as illustrated by the
Gemäß einem weiteren Ausführungsbeispiel können bei dem erfindungsgemäßen Axiallüfter Nabenrampen vorgesehen sein, die an der Nabe des Lüfters vorgesehen sein können. Vorzugsweise auf der Druckseite des Lüfters können jeweils entgegen der Drehrichtung ansteigende Nabenrampen vorgesehen sein, die jeweils nach außen von einer Außenfläche begrenzt sind. Diesbezüglich sei auf die
Claims (10)
- An axial fan for a radiator of an internal combustion engine, particularly of a motor vehicle, with a rotatably driven hub (2), to which fan blades (11-19) are fixed, which are limited radially inward by an inside diameter (Di) and radially outward by an outside diameter (Da), wherein the ratio of the inside diameter (Di) to the outside diameter (Da) is greater than 40 percent, characterised in that the ratio of the fan blade areas projected on a fan passage area enclosed between the inside diameter (Di) and the outside diameter (Da) by the fan blades (11-19) to the fan passage area is greater than 60 percent.
- The axial fan according to Claim 1, characterised in that the fan blades (11-19) are crescent-shaped in the direction ofthe air flow-through direction.
- The axial fan according to claim 1, characterised in that the fan blades (11-19) are crescent-shaped in a direction extending opposite to the air flow-through direction.
- The axial fan according to one of the preceding claims, characterised in that the front edge (28) of the fan blades (11-19) has a parabolic shape.
- The axial fan according to claim 4, characterised in that the origin or vertex of the parabola coincides with the intersecting point between the outside diameter (Da) of the fan passage area and the front edge (28) ofthe corresponding fan blade (11).
- The axial fan according to one of the preceding claims, characterised in that the blade angle (α1, α2, α3) on the front edge (29) of the fan blades (11-19) is greater than 20 degrees over the radius (R1, R2, R3) of the fan passage area.
- The axial fan according to one of the preceding claims, characterised in that the profile length of the fan blades (11-19) is nearly constant over the radius of the fan passage area.
- The axial fan according to claim 7, characterised in that the deviations of the profile length from an average profile length are smaller than +/- 6 percent.
- The axial fan according to at least one ofthe preceding claims, characterised in that hub ramps are provided, which are provided on the hub of the fan, which are preferably formed on the pressure side of the fan such that they respectively ascend, in particular, opposite to the rotating direction and are outwardly limited by an outside surface, wherein the hub radius preferably is essentially constant in the axial direction.
- A radiator for an internal combustion engine, particularly of a motor vehicle, through which a medium flows, particularly a cooling medium that serves, for example for cooling the internal combustion engine, and which radiator features a radiator air passage area, through which an air flow flows along a first air flow path that can be shut by means of a louvre in a so-called dynamic pressure mode and through which an air flow flows along a second air flow path in a so-called fan mode, wherein the second air flow path extends through a fan according to one of the preceding claims that is arranged between the radiator and the internal combustion engine.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005005977A DE102005005977A1 (en) | 2005-02-09 | 2005-02-09 | Axial |
PCT/EP2006/001095 WO2006084674A1 (en) | 2005-02-09 | 2006-02-08 | Axial ventilator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1851443A1 EP1851443A1 (en) | 2007-11-07 |
EP1851443B1 true EP1851443B1 (en) | 2010-04-28 |
Family
ID=36291948
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06706737A Not-in-force EP1851443B1 (en) | 2005-02-09 | 2006-02-08 | Axial ventilator |
Country Status (6)
Country | Link |
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US (1) | US20080156282A1 (en) |
EP (1) | EP1851443B1 (en) |
JP (1) | JP2008530414A (en) |
AT (1) | ATE466196T1 (en) |
DE (2) | DE102005005977A1 (en) |
WO (1) | WO2006084674A1 (en) |
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US10539157B2 (en) | 2015-04-08 | 2020-01-21 | Horton, Inc. | Fan blade surface features |
US11767761B2 (en) | 2018-08-02 | 2023-09-26 | Horton, Inc. | Low solidity vehicle cooling fan |
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TWD160896S (en) * | 2013-10-09 | 2014-06-01 | 訊凱國際股份有限公司 | Cooling fan (2) |
TWD160897S (en) * | 2013-10-09 | 2014-06-01 | 訊凱國際股份有限公司 | Cooling fan (1) |
US10093152B2 (en) | 2014-06-09 | 2018-10-09 | Dometic Sweden Ab | Shrouded roof vent for a vehicle |
USD765188S1 (en) * | 2015-04-20 | 2016-08-30 | Calogero A. LaRussa | Flying propeller |
US10400783B1 (en) * | 2015-07-01 | 2019-09-03 | Dometic Sweden Ab | Compact fan for a recreational vehicle |
USD787037S1 (en) | 2015-07-01 | 2017-05-16 | Dometic Sweden Ab | Fan |
USD832987S1 (en) | 2016-10-13 | 2018-11-06 | Dometic Sweden Ab | Roof fan shroud |
US11027595B2 (en) | 2016-10-13 | 2021-06-08 | Dometic Sweden Ab | Roof fan assembly |
USD860427S1 (en) | 2017-09-18 | 2019-09-17 | Horton, Inc. | Ring fan |
US11536279B1 (en) * | 2022-03-07 | 2022-12-27 | Stokes Technology Development Ltd. | Thin type counter-rotating axial air moving device |
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JP2003120588A (en) * | 2001-10-18 | 2003-04-23 | Denso Corp | Blower |
KR100484828B1 (en) * | 2002-11-27 | 2005-04-22 | 엘지전자 주식회사 | Refrigerator's cool air circulation axial flow fan |
KR100550529B1 (en) * | 2003-12-30 | 2006-02-10 | 엘지전자 주식회사 | Centrifugal fan of a refrigerator |
JP4679074B2 (en) * | 2004-05-19 | 2011-04-27 | アイシン化工株式会社 | cooling fan |
-
2005
- 2005-02-09 DE DE102005005977A patent/DE102005005977A1/en not_active Withdrawn
-
2006
- 2006-02-08 US US11/815,577 patent/US20080156282A1/en not_active Abandoned
- 2006-02-08 JP JP2007553569A patent/JP2008530414A/en active Pending
- 2006-02-08 DE DE502006006847T patent/DE502006006847D1/en active Active
- 2006-02-08 WO PCT/EP2006/001095 patent/WO2006084674A1/en active Application Filing
- 2006-02-08 EP EP06706737A patent/EP1851443B1/en not_active Not-in-force
- 2006-02-08 AT AT06706737T patent/ATE466196T1/en active
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10539157B2 (en) | 2015-04-08 | 2020-01-21 | Horton, Inc. | Fan blade surface features |
US10662975B2 (en) | 2015-04-08 | 2020-05-26 | Horton, Inc. | Fan blade surface features |
US11767761B2 (en) | 2018-08-02 | 2023-09-26 | Horton, Inc. | Low solidity vehicle cooling fan |
Also Published As
Publication number | Publication date |
---|---|
US20080156282A1 (en) | 2008-07-03 |
WO2006084674A1 (en) | 2006-08-17 |
ATE466196T1 (en) | 2010-05-15 |
EP1851443A1 (en) | 2007-11-07 |
JP2008530414A (en) | 2008-08-07 |
DE502006006847D1 (en) | 2010-06-10 |
DE102005005977A1 (en) | 2006-08-10 |
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