EP1276994A1 - Blower especially for ventilating electronic devices - Google Patents

Blower especially for ventilating electronic devices

Info

Publication number
EP1276994A1
EP1276994A1 EP01938021A EP01938021A EP1276994A1 EP 1276994 A1 EP1276994 A1 EP 1276994A1 EP 01938021 A EP01938021 A EP 01938021A EP 01938021 A EP01938021 A EP 01938021A EP 1276994 A1 EP1276994 A1 EP 1276994A1
Authority
EP
European Patent Office
Prior art keywords
hub
blade
fan according
guide surface
flow channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01938021A
Other languages
German (de)
French (fr)
Other versions
EP1276994B1 (en
Inventor
Thomas MÄRLÄNDER
Christof Huonker
Andreas Kienzler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Verax Ventilatoren GmbH
Original Assignee
Verax Ventilatoren GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Verax Ventilatoren GmbH filed Critical Verax Ventilatoren GmbH
Publication of EP1276994A1 publication Critical patent/EP1276994A1/en
Application granted granted Critical
Publication of EP1276994B1 publication Critical patent/EP1276994B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/06—Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the invention relates to a fan, in particular for ventilation or cooling of electronic devices such as personal computers.
  • flat axial fans are usually used, which have a cylindrical annular space as a flow channel and inclined blades.
  • the flow thus runs axially through the impeller.
  • a high volume flow can thus be achieved at low pressure differences.
  • radial fans are known, for example, for use in hair dryers, which can overcome a higher flow resistance by building up larger pressure differences.
  • radial fans are rather unsuitable for installation in PC housings because of the radial or tangential air flow.
  • Mixed forms are also known, in particular as so-called semi-axial fans, which have a diagonal flow component in the case of regionally overlapping, inclined blades. Such fans also have noise disadvantages in computer applications.
  • the object of the invention is to provide a fan which avoids the disadvantages mentioned above and achieves a high degree of efficiency with regard to efficient ventilation and cooling with little noise.
  • the design should be well suited for installation in computer housings and match the typical system characteristics.
  • the invention is based on the idea of using a fan with a radial flow through the radial wheel in order to achieve a wide, favorable working range. Accordingly, a fan with the following features is proposed according to the invention:
  • a fan housing delimiting a flow channel on the outside by a guide surface
  • an impeller which is mounted in the fan housing so as to be rotatable about an axis of rotation and with its hub which is arranged concentrically with the guide surface and delimits the flow channel on the inside,
  • the blades of the impeller which are preferably distributed unevenly over the circumference of the hub, lie in cylindrical surfaces which run parallel to the axis of rotation and are curved backwards counter to the direction of rotation, -
  • the guide surface and the hub are designed to widen conically or slightly curved in the direction of flow between the blade inlet edge and the blade outlet edge , whereby the clear flow area of the flow channel remains constant or decreases.
  • a radial working principle is thus achieved with a compact axial design.
  • the blow-out direction is only slightly changed compared to axial fans, while a significant increase in pressure is achieved with a comparable volume flow.
  • the special routing of the flow channel diagonally through the impeller leads to a constant throttle curve and thus enables the working point to be optimized over a wide range.
  • the guide surface in the blade area should be axially steeper than the hub. It is further advantageous if the guide surface in the blade area has essentially the shape of a truncated cone with a cone angle between 20 ° and 60 °, preferably 40 °, and if the hub in the blade area essentially has the shape of a truncated cone with a cone angle between 80 ° and 110 °, preferably 95 °.
  • the hub is parabolic, at least in its apex area. It is also expedient if the inlet area of the guide surface is rounded outwards via an inlet radius.
  • the inlet and outlet openings of the flow channel advantageously have a mutual radial overlap.
  • the blade exit edge toward the blade end is set at an acute angle of attack against the flow direction relative to the plane of the outlet opening of the flow channel. It should be ensured that the angle of attack is between 10 ° and 20 °, preferably 15 °. This ensures that turbulence on the downstream side and correspondingly also the noise development are minimized. A further improvement is achieved in that the free blade end edges run along the guide surface while maintaining a tolerance gap.
  • the blade inlet edges extend axially beyond the hub towards the inlet opening.
  • the blade leading edge has a radius of curvature of 1% to 4% and a profile thickness of 2% to 8% of the length of the free blade edge.
  • An electric motor designed as an external rotor and arranged in a recess in the hub is advantageously used for rotating the impeller.
  • Figure 1 shows a fan for PC devices in the upstream side view.
  • Fig. 2 shows the fan of Fig. 1 with a simplified contoured blading shown in axial section.
  • the fan shown in the drawing essentially consists of a housing 10, an impeller 18 rotatably mounted therein about an axis of rotation 12, having a hub 14 and blades 16 formed thereon, and a rotary drive 20 for the impeller 18.
  • the housing 10 comprises an inner jacket as a guide surface 22, a flow channel 24 on the outside, while the concentric to the Guide surface 16 arranged hub 14 limits the flow channel 24 on the inside.
  • the guide surface 22 has the shape of a truncated cone which widens in the direction of flow - downwards in FIG. 2, the cone angle being approximately 40 °.
  • the inlet section 26 is rounded to the outside by delimiting the inlet opening 28 of the flow channel 24 over an inlet radius. This radius should be kept as large as possible to avoid the occurrence of turbulence on the inlet side. In principle, it is also possible for the guide surface to be slightly curved as a truncated paraboloid of revolution.
  • the hub 14 is frustoconical in the base region 30 of the blades 16, the cone angle being 95 ° in the embodiment shown. In its apex region 32 facing the inlet opening 28, the hub 14 is parabolically shaped in order to avoid turbulence. It is also conceivable that the hub 14 has the overall shape of a paraboloid, possibly with a rounded trailing edge. In any case, it should be ensured that the guide surface 22 in the blade region, that is to say between the blade inlet edge 34 and the blade outlet edge 36, has a greater slope in the direction of the axis of rotation 12 than the hub 14, so that the mean diameter of the annular flow channel 24 there is constant or slightly decreasing clear flow area is constantly expanding. There is a radial overlap between the inlet opening 28 and outlet opening 38 of the flow channel 24, so that an annular region 40 is axially continuously open.
  • the blades 16 are distributed asymmetrically over the circumference of the hub 14 and lie as pure radial blades in parallel to the axis of rotation 12, counter-clockwise (counterclockwise in Fig. 1) backward curved cylinder surfaces.
  • the blade inlet edges 34 extend axially beyond the apex region 32 of the hub 14 to the inlet opening 28 and have a radius of curvature of 1% to 4% and a profile thickness of 2% to 8% of the length of the free blade end edges 42, which keep a tolerance gap free the guide surface 22 run.
  • the blade exit edges 36 are set toward the blade end opposite the plane of the outlet opening 38 at an acute angle of attack against the flow direction, the angle of attack being approximately 15 ° in the embodiment shown.
  • the entire fan wheel 18 is preferably produced as a one-piece injection-molded part made of plastic. It is favorable with regard to the demolding that the blades 16 do not overlap in the direction of rotation.
  • the rotary drive 20 is formed by an electric motor designed as an external rotor, which is arranged in a cylindrical recess 44 in the hub 14.
  • the rotor 46 is fixedly connected to the hub 14, while stator 52, which is seated on the rotor shaft 50 via roller bearings 48, is fixed on the outlet side on the outlet side by means of an annular flange 54 and frame webs 56 projecting radially therefrom.
  • the invention relates to a fan, in particular for personal computers, in which the following combination of features is proposed in order to minimize noise: - An impeller (18) mounted in the fan housing (10) so as to be rotatable about an axis of rotation (12) and with its hub (14) which delimits the flow channel (24) on the inside,
  • the blades (16) of the impeller (18) distributed asymmetrically over the circumference of the hub (14) are designed as radial blades
  • the guide surface 22 and the hub 14 are designed to widen conically or slightly curved in the direction of flow in the blade area between blade inlet edge 34 and blade outlet edge 36, the clear flow surface of the flow channel 24 remaining constant or decreasing.

Abstract

The invention relates to a blower, especially for a personal computer. The air of the invention is to reduce the noise produces by such a blower. To this end, the inventive blower comprises: a) a blower housing (10) including a guide surface (22) that defines the exterior limits of a flow channel (24); b) a hub (14) that is mounted in the blower housing (10) so as to be rotatable about an axis of rotation (12) and having a hub surface (18) that defines the interior limits of the flow channel (24); c) a rotary drive (20) for the hub (18) which is disposed within the hub (14); d) the blades (16) of the hub (18) are asymmetrically distributed about the periphery of the hub (14) and are configured as radial blades; and e) the guide surface (22) and the hub (14), in the blade zone between the leading edge (34) of the blade and the trailing edge (36) of the blade, when looked at in the direction of flow, have a generally conical or slightly curved and widening shape, and the area of cross-section of flow along the flow channel (24) remains constant or is reduced.

Description

Lüfter insbesondere zur Belüftung von elektronischen GerätenFans, in particular for ventilating electronic devices
Beschreibungdescription
Die Erfindung betrifft einen Lüfter insbesondere zur Belüftung bzw. Kühlung von elektronischen Geräten wie Personalcomputern.The invention relates to a fan, in particular for ventilation or cooling of electronic devices such as personal computers.
Zu diesem Zweck werden üblicherweise flach gebaute Axiallüfter eingesetzt, welche einen zylindrischen Ringraum als Strömungskanal und schräg ange- stellte Schaufeln aufweisen. Die Strömung verläuft somit axial durch das Laufrad. Damit kann bei geringen Druckdifferenzen ein hoher Volumenstrom erzielt werden. Im Übergangsbereich zu höheren Druckdifferenzen treten jedoch Unstetigkeiten auf, die zu starken Verwirbelungen und damit einhergehend zu ungünstigem Geräuschverhalten führen.For this purpose, flat axial fans are usually used, which have a cylindrical annular space as a flow channel and inclined blades. The flow thus runs axially through the impeller. A high volume flow can thus be achieved at low pressure differences. In the transition area to higher pressure differences, however, there are discontinuities that lead to strong turbulence and the associated unfavorable noise behavior.
Daneben sind Radiallüfter beispielsweise zum Einsatz in Haartrocknern bekannt, die unter Aufbau größerer Druckdifferenzen einen höheren Strömungswiderstand überwinden können. Solche Lüfter sind jedoch abgesehen von ihrem geringen Fördervolumen wegen der radialen bzw. tangentialen Luftführung für den Einbau in PC-Gehäuse eher ungeeignet. Weiter bekannt sind Mischformen insbesondere als sogenannte Halbaxial-Lüfter, die eine diagonale Strömungskomponente bei sich bereichsweise überdeckenden, schräg angestellten Schaufeln aufweisen. Auch solche Lüfter weisen bei Computerapplikationen Geräuschnachteile auf.In addition, radial fans are known, for example, for use in hair dryers, which can overcome a higher flow resistance by building up larger pressure differences. However, apart from their low delivery volume, such fans are rather unsuitable for installation in PC housings because of the radial or tangential air flow. Mixed forms are also known, in particular as so-called semi-axial fans, which have a diagonal flow component in the case of regionally overlapping, inclined blades. Such fans also have noise disadvantages in computer applications.
Ausgehend hiervon liegt der Erfindung die Aufgabe zugrunde, einen Lüfter anzugeben, der die zuvor genannten Nachteile vermeidet und bei geringer Geräuschentwicklung einen hohen Wirkungsgrad im Hinblick auf eine effiziente Belüftung und Kühlung erreicht. Daneben soll die Bauform für den Ein- bau in Computergehäuse gut geeignet und auf die typischen Systemkennlinien abgestimmt sein. Zur Lösung dieser Aufgabe wird die im Patentanspruch 1 angegebene Merkmalskombination vorgeschlagen. Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den abhängigen Ansprü- chen.Proceeding from this, the object of the invention is to provide a fan which avoids the disadvantages mentioned above and achieves a high degree of efficiency with regard to efficient ventilation and cooling with little noise. In addition, the design should be well suited for installation in computer housings and match the typical system characteristics. To achieve this object, the combination of features specified in claim 1 is proposed. Advantageous refinements and developments of the invention result from the dependent claims.
Die Erfindung geht von dem Gedanken aus, einen Lüfter mit diagonal durch- strömtem Radialrad einzusetzen, um einen breiten günstigen Arbeitsbereich zu erreichen. Dementsprechend wird erfindungsgemäß ein Lüfter mit folgen- den Merkmalen vorgeschlagen:The invention is based on the idea of using a fan with a radial flow through the radial wheel in order to achieve a wide, favorable working range. Accordingly, a fan with the following features is proposed according to the invention:
- einem einen Strömungskanal außenseitig durch eine Leitfläche begrenzenden Lüftergehäuse,a fan housing delimiting a flow channel on the outside by a guide surface,
- einem in dem Lüftergehäuse um eine Drehachse drehbar gelagerten, mit seiner konzentrisch zu der Leitfläche angeordneten Nabe den Strömungs- kanal innenseitig begrenzenden Laufrad,an impeller which is mounted in the fan housing so as to be rotatable about an axis of rotation and with its hub which is arranged concentrically with the guide surface and delimits the flow channel on the inside,
- einem in der Nabe angeordneten Drehantrieb für das Laufrad,a rotary drive for the impeller arranged in the hub,
- die über den Umfang der Nabe vorzugsweise ungleichmäßig verteilten Schaufeln des Laufrads liegen in parallel zur Drehachse verlaufenden, entgegen der Drehrichtung rückwärts gekrümmten Zylinderflächen, - die Leitfläche und die Nabe sind im Schaufelbereich zwischen Schaufeleintrittskante und Schaufelaustrittskante in Durchströmrichtung gesehen konisch oder schwach gekrümmt sich erweiternd ausgebildet, wobei die lichte Durchströmfläche des Strömungskanals konstant bleibt oder sich verringert. Damit wird bei kompakter axialer Bauform ein radiales Arbeitsprinzip erreicht. Gegenüber Axiallüftern wird die Ausblasrichtung nur geringfügig verändert, während bei vergleichbarem Volumenstrom eine deutliche Druckerhöhung erreicht wird. Die besondere Führung des Strömungskanals diagonal durch das Laufrad führt zu einer stetigen Drosselkurve und ermöglicht damit eine Optimierung des Arbeitspunktes über einen weiten Bereich. Insbesondere treten aufgrund der geringen Umfangsgeschwindigkeitsunterschiede geräuscherzeugende Störungen der Strömung bzw. ein Strömungsabriß erst bei hohen Drücken im oberen Bereich der Drosselkurve ein. Die Systemkennlinien von PC's liegen üblicherweise nicht in diesem Bereich. In diesem Sinne wirkt sich auch der längere Strömungsweg positiv aus.- The blades of the impeller, which are preferably distributed unevenly over the circumference of the hub, lie in cylindrical surfaces which run parallel to the axis of rotation and are curved backwards counter to the direction of rotation, - The guide surface and the hub are designed to widen conically or slightly curved in the direction of flow between the blade inlet edge and the blade outlet edge , whereby the clear flow area of the flow channel remains constant or decreases. A radial working principle is thus achieved with a compact axial design. The blow-out direction is only slightly changed compared to axial fans, while a significant increase in pressure is achieved with a comparable volume flow. The special routing of the flow channel diagonally through the impeller leads to a constant throttle curve and thus enables the working point to be optimized over a wide range. In particular, due to the low peripheral speed differences noise-producing disturbances of the flow or a stall only at high pressures in the upper region of the throttle curve. The system characteristics of PC's are usually not in this range. In this sense, the longer flow path also has a positive effect.
Um den Strömungsquerschnitt etwa konstant zu halten, sollte die Leitfläche im Schaufelbereich axial steiler als die Nabe verlaufen. Dabei ist es weiter von Vorteil, wenn die Leitfläche im Schaufelbereich im wesentlichen die Form eines Kegelstumpfes mit einem Kegelwinkel zwischen 20° und 60°, vorzugsweise 40° aufweist, und wenn die Nabe im Schaufelbereich im wesentlichen die Form eines Kegelstumpfes mit einem Kegelwinkel zwischen 80° und 110°, vorzugsweise 95° aufweist.In order to keep the flow cross-section approximately constant, the guide surface in the blade area should be axially steeper than the hub. It is further advantageous if the guide surface in the blade area has essentially the shape of a truncated cone with a cone angle between 20 ° and 60 °, preferably 40 °, and if the hub in the blade area essentially has the shape of a truncated cone with a cone angle between 80 ° and 110 °, preferably 95 °.
Zur weiteren Reduzierung der Geräuschentwicklung ist es von Vorteil, wenn die Nabe zumindest in ihrem Scheitelbereich parabolisch ausgebildet ist. Günstig ist es auch, wenn die Eintrittspartie der Leitfläche über einen Einlaufradius nach außen abgerundet ist.To further reduce noise, it is advantageous if the hub is parabolic, at least in its apex area. It is also expedient if the inlet area of the guide surface is rounded outwards via an inlet radius.
Vorteilhafterweise besitzen die Ein- und Austrittsöffnung des Strömungska- nals eine gegenseitige radiale Überdeckung.The inlet and outlet openings of the flow channel advantageously have a mutual radial overlap.
Gemäß einer weiteren besonders vorteilhaften Ausgestaltung der Erfindung sind die Schaufelaustrittskante zum Schaufelende hin gegenüber der Ebene der Austrittsöffnung des Strömungskanals unter einem spitzen Anstellwinkel entgegen der Durchströmrichtung angestellt. Dabei sollte gewährleistet sein, daß der Anstellwinkel zwischen 10° und 20°, vorzugsweise 15° beträgt. Damit wird erreicht, daß abströmseitige Verwirbelungen und entsprechend auch die Geräuschentwicklung minimiert werden. Eine weitere Verbesserung wird dadurch erzielt, daß die freien Schaufelendkanten unter Freihaltung eines Toleranzspalts entlang der Leitfläche verlaufen.According to a further particularly advantageous embodiment of the invention, the blade exit edge toward the blade end is set at an acute angle of attack against the flow direction relative to the plane of the outlet opening of the flow channel. It should be ensured that the angle of attack is between 10 ° and 20 °, preferably 15 °. This ensures that turbulence on the downstream side and correspondingly also the noise development are minimized. A further improvement is achieved in that the free blade end edges run along the guide surface while maintaining a tolerance gap.
Zur Erhöhung des Einlaßquerschnitts zwischen den Schaufeln ist es vorteilhaft, wenn die Schaufeleintrittskanten sich axial über die Nabe hinaus zu der Eintrittsöffnung hin erstrecken.To increase the inlet cross-section between the blades, it is advantageous if the blade inlet edges extend axially beyond the hub towards the inlet opening.
Eine weitere aerodynamisch günstige Ausführung sieht vor, daß die Schau- feleintrittskante einen Rundungsradius von 1% bis 4% sowie eine Profildicke von 2% bis 8% der Länge der freien Schaufelendkante aufweist.Another aerodynamically favorable embodiment provides that the blade leading edge has a radius of curvature of 1% to 4% and a profile thickness of 2% to 8% of the length of the free blade edge.
Zum Drehantrieb des Laufrads wird vorteilhafterweise ein als Außenläufer ausgebildeter, in einer Ausnehmung der Nabe angeordneter Elektromotor eingesetzt.An electric motor designed as an external rotor and arranged in a recess in the hub is advantageously used for rotating the impeller.
Im folgenden wird die Erfindung anhand eines in der Zeichnung in schemati- scher Weise dargestellten Ausführungsbeispiels näher erläutert. Es zeigenThe invention is explained in more detail below on the basis of an exemplary embodiment shown schematically in the drawing. Show it
Fig. 1 einen Lüfter für PC-Geräte in einströmseitiger Draufsicht;Figure 1 shows a fan for PC devices in the upstream side view.
Fig. 2 den Lüfter nach Fig. 1 mit vereinfacht konturiert dargestellter Beschaufelung im Axialschnitt.Fig. 2 shows the fan of Fig. 1 with a simplified contoured blading shown in axial section.
Der in der Zeichnung dargestellte Lüfter besteht im wesentlichen aus einem Gehäuse 10, einem darin um eine Drehachse 12 drehbar gelagerten, eine Nabe 14 sowie daran angeformte Schaufeln 16 aufweisenden Laufrad 18 und einem Drehantrieb 20 für das Laufrad 18.The fan shown in the drawing essentially consists of a housing 10, an impeller 18 rotatably mounted therein about an axis of rotation 12, having a hub 14 and blades 16 formed thereon, and a rotary drive 20 for the impeller 18.
Das Gehäuse 10 umfaßt mit einem Innenmantel als Leitfläche 22 einen Strömungskanal 24 an dessen Außenseite, während die konzentrisch zu der Leitfläche 16 angeordnete Nabe 14 den Strömungskanal 24 innenseitig begrenzt.The housing 10 comprises an inner jacket as a guide surface 22, a flow channel 24 on the outside, while the concentric to the Guide surface 16 arranged hub 14 limits the flow channel 24 on the inside.
Wie aus Fig. 2 ersichtlich, weist die Leitfläche 22 mit Ausnahme ihrer Ein- trittspartie 26 die Form eines sich in Durchströmrichtung - in Fig. 2 nach unten - erweiternden Kegelstumpfes auf, wobei der Kegelwinkel etwa 40° beträgt. Die Eintrittspartie 26 ist unter Begrenzung der Eintrittsöffnung 28 des Strömungskanals 24 über einen Einlaufradius nach außen abgerundet ist. Dieser Radius sollte möglichst groß gehalten werden, um das Entstehen von eintrittsseitigen Turbulenzen zu vermeiden. Grundsätzlich ist es auch möglich, daß die Leitfläche als abgestumpftes Rotationsparaboloid schwach gekrümmt ist.As can be seen from FIG. 2, the guide surface 22, with the exception of its inlet section 26, has the shape of a truncated cone which widens in the direction of flow - downwards in FIG. 2, the cone angle being approximately 40 °. The inlet section 26 is rounded to the outside by delimiting the inlet opening 28 of the flow channel 24 over an inlet radius. This radius should be kept as large as possible to avoid the occurrence of turbulence on the inlet side. In principle, it is also possible for the guide surface to be slightly curved as a truncated paraboloid of revolution.
Die Nabe 14 ist im Fußbereich 30 der Schaufeln 16 kegelstumpfförmig aus- gebildet, wobei der Kegelwinkei in der gezeigten Ausführungsform 95° beträgt. In ihrem der Eintrittsöffnung 28 zugewandten Scheitelbereich 32 ist die Nabe 14 parabolisch geformt, um Turbulenzen zu vermeiden. Denkbar ist es auch, daß die Nabe 14 insgesamt die Form eines Paraboloids aufweist, gegebenenfalls mit abgerundeter Abströmkante. In jedem Fall sollte gewährlei- stet sein, daß die Leitfläche 22 im Schaufelbereich, also zwischen der Schaufeleintrittskante 34 und der Schaufelaustrittskante 36 eine größere Steigung in Richtung der Drehachse 12 aufweist als die Nabe 14, so daß der Mitteldurchmesser des dort kreisringförmigen Strömungskanals 24 bei konstanter oder geringfügig abnehmender lichter Durchströmfläche sich stetig erweitert. Dabei besteht zwischen Eintrittsöffnung 28 und Austrittsöffnung 38 des Strömungskanals 24 eine radiale Überdeckung, so daß ein Ringbereich 40 axial durchgängig offen ist.The hub 14 is frustoconical in the base region 30 of the blades 16, the cone angle being 95 ° in the embodiment shown. In its apex region 32 facing the inlet opening 28, the hub 14 is parabolically shaped in order to avoid turbulence. It is also conceivable that the hub 14 has the overall shape of a paraboloid, possibly with a rounded trailing edge. In any case, it should be ensured that the guide surface 22 in the blade region, that is to say between the blade inlet edge 34 and the blade outlet edge 36, has a greater slope in the direction of the axis of rotation 12 than the hub 14, so that the mean diameter of the annular flow channel 24 there is constant or slightly decreasing clear flow area is constantly expanding. There is a radial overlap between the inlet opening 28 and outlet opening 38 of the flow channel 24, so that an annular region 40 is axially continuously open.
Die Schaufeln 16 sind zur Vermeidung von Resonanzen über den Umfang der Nabe 14 asymmetrisch verteilt und liegen als reine Radialschaufeln in parallel zur Drehachse 12 verlaufenden, entgegen der Drehrichtung (Gegenuhrzeigersinn in Fig. 1) rückwärts gekrümmten Zylinderflächen.To avoid resonance, the blades 16 are distributed asymmetrically over the circumference of the hub 14 and lie as pure radial blades in parallel to the axis of rotation 12, counter-clockwise (counterclockwise in Fig. 1) backward curved cylinder surfaces.
Die Schaufeleintrittskanten 34 erstrecken sich axial über den Scheitelbereich 32 der Nabe 14 hinaus zu der Eintrittsöffnung 28 und besitzen einen Rundungsradius von 1% bis 4% sowie eine Profildicke von 2% bis 8% der Länge der freien Schaufelendkanten 42, welche unter Freihaltung eines Toleranzspalts entlang der Leitfläche 22 verlaufen. Zur Geräuschminderung sind die Schaufelaustrittskanten 36 zum Schaufelende hin gegenüber der Ebene der Austrittsöffnung 38 unter einem spitzen Anstellwinkel entgegen der Durchströmrichtung angestellt, wobei der Anstellwinkel in der gezeigten Ausführungsform etwa 15° beträgt.The blade inlet edges 34 extend axially beyond the apex region 32 of the hub 14 to the inlet opening 28 and have a radius of curvature of 1% to 4% and a profile thickness of 2% to 8% of the length of the free blade end edges 42, which keep a tolerance gap free the guide surface 22 run. In order to reduce noise, the blade exit edges 36 are set toward the blade end opposite the plane of the outlet opening 38 at an acute angle of attack against the flow direction, the angle of attack being approximately 15 ° in the embodiment shown.
Das gesamte Lüfterrad 18 ist vorzugsweise als einstückiges Spritzgußform- teil aus Kunststoff hergestellt. Dabei ist es hinsichtlich der Entformung günstig, daß die Schaufeln 16 in Drehrichtung nicht überlappen.The entire fan wheel 18 is preferably produced as a one-piece injection-molded part made of plastic. It is favorable with regard to the demolding that the blades 16 do not overlap in the direction of rotation.
Der Drehantrieb 20 ist durch einen als Außenläufer ausgebildeten Elektromotor gebildet, welcher in einer zylindrischen Ausnehmung 44 der Nabe 14 angeordnet ist. Der Rotor 46 ist dabei fest mit der Nabe 14 verbunden, während über Wälzlager 48 auf der Rotorwelle 50 sitzende Stator 52 mittels Ringflansch 54 und davon radial abstehenden Rahmenstegen 56 austritts- seitig gehäusefest befestigt ist.The rotary drive 20 is formed by an electric motor designed as an external rotor, which is arranged in a cylindrical recess 44 in the hub 14. The rotor 46 is fixedly connected to the hub 14, while stator 52, which is seated on the rotor shaft 50 via roller bearings 48, is fixed on the outlet side on the outlet side by means of an annular flange 54 and frame webs 56 projecting radially therefrom.
Zusammenfassend ist folgendes festzuhalten: Die Erfindung betrifft einen Lüfter insbesondere für Personalcomputer, bei dem zur Geräuschminimie- rung folgende Merkmalskombination vorgeschlagen wird: - einem einen Strömungskanal (24) außenseitig durch eine Leitfläche (22) begrenzenden Lüftergehäuse (10), - einem in dem Lüftergehäuse (10) um eine Drehachse (12) drehbar gelagerten, mit seiner Nabe (14) den Strömungskanal (24) innenseitig begrenzenden Laufrad (18),In summary, the following can be stated: The invention relates to a fan, in particular for personal computers, in which the following combination of features is proposed in order to minimize noise: - An impeller (18) mounted in the fan housing (10) so as to be rotatable about an axis of rotation (12) and with its hub (14) which delimits the flow channel (24) on the inside,
- einem in der Nabe (14) angeordneten Drehantrieb (20) für das Laufrad (18),- A rotary drive (20) arranged in the hub (14) for the impeller (18),
- die über den Umfang der Nabe (14) asymmetrisch verteilten Schaufeln (16) des Laufrads (18) sind als Radialschaufeln ausgebildet,- The blades (16) of the impeller (18) distributed asymmetrically over the circumference of the hub (14) are designed as radial blades,
- die Leitfläche 22 und die Nabe 14 sind im Schaufelbereich zwischen Schaufeleintrittskante 34 und Schaufelaustrittskante 36 in Durchström- richtung gesehen konisch oder schwach gekrümmt sich erweiternd ausgebildet, wobei die lichte Durchströmfläche des Strömungskanals 24 konstant bleibt oder sich verringert. - The guide surface 22 and the hub 14 are designed to widen conically or slightly curved in the direction of flow in the blade area between blade inlet edge 34 and blade outlet edge 36, the clear flow surface of the flow channel 24 remaining constant or decreasing.

Claims

Patentansprüche claims
1. Lüfter insbesondere zur Belüftung von elektronischen Geräten wie Personalcomputern mit folgenden Merkmalen: a) einem einen Strömungskanal (24) außenseitig durch eine Leitfläche (22) begrenzenden Lüftergehäuse (10), b) einem in dem Lüftergehäuse (10) um eine Drehachse (12) drehbar gelagerten, mit seiner konzentrisch zu der Leitfläche (22) angeordneten Nabe (14) den Strömungskanal (24) innenseitig begrenzenden Laufrad (18), c) einem in der Nabe (14) angeordneten Drehantrieb (20) für das Laufrad (18), d) die über den Umfang der Nabe (14) vorzugsweise ungleichmäßig verteilten Schaufeln (16) des Laufrads (18) liegen in parallel zur Drehachse (12) verlaufenden, entgegen der Drehrichtung rückwärts gekrümmten Zylinderflächen, e) die Leitfläche (22) und die Nabe (14) sind im Schaufelbereich zwischen Schaufeleintrittskante (34) und Schaufelaustrittskante (36) in Durchströmrichtung gesehen konisch oder schwach ge- krümmt sich erweiternd ausgebildet, wobei die lichte Durchströmfläche des Strömungskanals (24) konstant bleibt oder sich verringert.1. Fan, in particular for ventilation of electronic devices such as personal computers, with the following features: a) a fan housing (10) that delimits a flow channel (24) on the outside through a guide surface (22), b) in the fan housing (10) about an axis of rotation (12 ) rotatably mounted impeller (18) with its hub (14) arranged concentrically to the guide surface (22) on the inside of the flow channel (24), c) a rotary drive (20) for the impeller (18) arranged in the hub (14) , d) the blades (16) of the impeller (18), which are preferably distributed unevenly over the circumference of the hub (14), lie in cylindrical surfaces which run parallel to the axis of rotation (12) and are curved backwards counter to the direction of rotation, e) the guide surface (22) and the Hubs (14) are formed in the blade area between blade inlet edge (34) and blade outlet edge (36) as seen in the flow direction, with a conical or slightly curved shape, the clear diameter hströmfläche the flow channel (24) remains constant or reduced.
2. Lüfter nach Anspruch 1 , dadurch gekennzeichnet, daß die Leitfläche (22) im Schaufelbereich axial steiler als die Nabe (14) verläuft.2. Fan according to claim 1, characterized in that the guide surface (22) in the blade area extends axially steeper than the hub (14).
3. Lüfter nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Leitfläche (22) im Schaufelbereich im wesentlichen die Form eines Kegelstumpfes mit einem Kegelwinkel zwischen 20° und 60°, vor- zugsweise 40° aufweist. 3. Fan according to claim 1 or 2, characterized in that the guide surface (22) in the blade region essentially has the shape of a truncated cone with a cone angle between 20 ° and 60 °, preferably 40 °.
4. Lüfter nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Nabe (14) im Schaufelbereich im wesentlichen die Form eines Kegelstumpfes mit einem Kegelwinkel zwischen 80° und 110°, vorzugsweise 95° aufweist.4. Fan according to one of claims 1 to 3, characterized in that the hub (14) in the blade region essentially has the shape of a truncated cone with a cone angle between 80 ° and 110 °, preferably 95 °.
5. Lüfter nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Nabe (14) zumindest in ihrem Scheitelbereich (32) parabolisch ausgebildet ist.5. Fan according to one of claims 1 to 4, characterized in that the hub (14) is parabolic at least in its apex region (32).
6. Lüfter nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Eintrittspartie (26) der Leitfläche (22) über einen Einlaufradius nach außen abgerundet ist.6. Fan according to one of claims 1 to 5, characterized in that the inlet part (26) of the guide surface (22) is rounded out over an inlet radius.
7. Lüfter nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Ein- und Austrittsöffnung (28,38) des Strömungskanals (24) eine gegenseitige radiale Überdeckung (40) besitzen.7. Fan according to one of claims 1 to 6, characterized in that the inlet and outlet opening (28,38) of the flow channel (24) have a mutual radial overlap (40).
8. Lüfter nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Schaufelaustrittskanten (36) zum Schaufelende hin gegen- über der Ebene der Austrittsöffnung (38) des Strömungskanals (24) unter einem spitzen Anstellwinkel entgegen der Durchströmrichtung angestellt sind.8. Fan according to one of claims 1 to 7, characterized in that the blade outlet edges (36) towards the blade end towards the plane of the outlet opening (38) of the flow channel (24) are set at an acute angle of attack against the flow direction.
9. Lüfter nach Anspruch 8, dadurch gekennzeichnet, daß der Anstell- Winkel zwischen 10° und 20°, vorzugsweise 15° beträgt.9. Fan according to claim 8, characterized in that the angle of attack is between 10 ° and 20 °, preferably 15 °.
10. Lüfter nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die freien Schaufelendkanten (42) unter Freihaltung eines Toleranzspalts entlang der Leitfläche (22) verlaufen. 10. Fan according to one of claims 1 to 9, characterized in that the free blade end edges (42) while keeping a tolerance gap along the guide surface (22).
11. Lüfter nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Schaufeleintrittskanten (34) sich axial über die Nabe (14) hinaus zu der Eintrittsöffnung (28) hin erstrecken.11. Fan according to one of claims 1 to 10, characterized in that the blade inlet edges (34) extend axially beyond the hub (14) to the inlet opening (28).
12. Lüfter nach einem der Ansprüche 1 bis 11 , dadurch gekennzeichnet, daß die Schaufeleintrittskanten (34) einen Rundungsradius von 1% bis 4% sowie eine Profildicke von 2% bis 8% der Länge der freien Schaufelendkanten (42) aufweisen.12. Fan according to one of claims 1 to 11, characterized in that the blade leading edges (34) have a radius of curvature of 1% to 4% and a profile thickness of 2% to 8% of the length of the free blade end edges (42).
13. Lüfter nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Drehantrieb (20) durch einen als Außenläufer ausgebildeten, in einer Ausnehmung (44) der Nabe (14) angeordneten Elektromotor gebildet ist. 13. Fan according to one of claims 1 to 3, characterized in that the rotary drive (20) is formed by an external motor, in a recess (44) of the hub (14) arranged electric motor.
EP01938021A 2000-04-28 2001-03-15 Blower especially for ventilating electronic devices Expired - Lifetime EP1276994B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10020878A DE10020878C2 (en) 2000-04-28 2000-04-28 Fans, in particular for ventilating electronic devices
DE10020878 2000-04-28
PCT/EP2001/002943 WO2001083994A1 (en) 2000-04-28 2001-03-15 Blower especially for ventilating electronic devices

Publications (2)

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EP1276994A1 true EP1276994A1 (en) 2003-01-22
EP1276994B1 EP1276994B1 (en) 2005-10-19

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US (1) US6814542B2 (en)
EP (1) EP1276994B1 (en)
JP (1) JP2003532026A (en)
CN (1) CN1180184C (en)
AT (1) ATE307294T1 (en)
DE (2) DE10020878C2 (en)
WO (1) WO2001083994A1 (en)

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US6814542B2 (en) 2004-11-09
DE10020878A1 (en) 2001-11-15
CN1426511A (en) 2003-06-25
EP1276994B1 (en) 2005-10-19
CN1180184C (en) 2004-12-15
DE10020878C2 (en) 2002-05-02
WO2001083994A1 (en) 2001-11-08
DE50107752D1 (en) 2006-03-02
US20030077175A1 (en) 2003-04-24
ATE307294T1 (en) 2005-11-15
JP2003532026A (en) 2003-10-28

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