EP3405679B1 - Diagonal fan - Google Patents

Diagonal fan Download PDF

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Publication number
EP3405679B1
EP3405679B1 EP17781458.9A EP17781458A EP3405679B1 EP 3405679 B1 EP3405679 B1 EP 3405679B1 EP 17781458 A EP17781458 A EP 17781458A EP 3405679 B1 EP3405679 B1 EP 3405679B1
Authority
EP
European Patent Office
Prior art keywords
impeller
diagonal fan
fan
rotor
diagonal
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.)
Active
Application number
EP17781458.9A
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German (de)
French (fr)
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EP3405679A1 (en
Inventor
Daniel Gebert
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.)
Ebm Papst Mulfingen GmbH and Co KG
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Ebm Papst Mulfingen GmbH and Co KG
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Publication of EP3405679A1 publication Critical patent/EP3405679A1/en
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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/165—Axial entry and discharge
    • 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
    • F04D25/064—Details of the rotor
    • 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
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • 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
    • F04D25/0646—Details of the 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4253—Fan casings with axial entry and discharge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • 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
    • 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
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F05B2240/12—Fluid guiding means, e.g. vanes
    • 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
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F05B2240/14—Casings, housings, nacelles, gondels or the like, protecting or supporting assemblies there within
    • 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
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise

Definitions

  • the invention relates to a diagonal fan of improved compact design with high power density and low noise development.
  • Diagonal fans and their use are generally known from the prior art, for example from DE 10 2014 210 373 A1 . Further printed prior art from the present technical field is from the publications DE 10 2004 058 003 A1 and U.S. 2009/246017 A1 known.
  • Diagonal fans are used in applications with high demands Air capacity used with higher back pressure and little installation space, for example in cooling technology or in extractor hoods. Due to the large motor diameter of the axially centrally arranged motor in relation to the installation space in diagonal fans, the exhaust surface at the exhaust opening is relatively small, which results in high outlet losses in the flow due to high dynamic pressure at the outlet of the diagonal fan.
  • the invention is therefore based on the object of providing a diagonal fan in a compact design with a high power density and good noise characteristics.
  • a diagonal fan with a fan housing within which an external rotor motor and an impeller are accommodated, the external rotor motor having a stator and a rotor at least partially enclosing the stator.
  • An axial flow channel runs between the fan housing and the external rotor motor up to an outlet opening of the diagonal fan surrounding the external rotor motor, air sucked in via the impeller being sucked in through the flow channel during operation of the diagonal fan and being conveyable to the outlet opening.
  • the impeller is integrated into the rotor.
  • the integration of the impeller into the rotor is provided by the fact that the rotor and impeller are designed in one piece. The number of parts and the axial Installation space is therefore minimized. As an alternative to the one-piece design, the integral design can also be achieved in that parts of the impeller, such as B. the impeller blades are mounted on the rotor.
  • the diagonal fan has, in a blow-out section adjoining the blow-out opening, an air-guiding device with a plurality of air-guiding blades distributed in the circumferential direction.
  • the air guide vanes extend in the axial direction at least in an overlapping section over the rotor and are each spaced apart from the rotor by a radial air gap.
  • the rotor rotates relative to the airfoil vanes.
  • the size of the air gap corresponds to a maximum of 5%, preferably a maximum of 1.5%, of a maximum radial installation space of the diagonal fan.
  • the maximum radial installation space is determined by the outermost enveloping contour of the entire diagonal fan. In the case of an imaginary cylindrical design, the maximum radial installation space would correspond to the maximum outer diameter.
  • the diagonal fan in which the ratio of an axial length of the overlapping section of the air guide vanes to a non-overlapping section in which the air guide vanes do not overlap the rotor in the axial direction is in a range from 0.5 to 4.0 , preferably in a range from 1.5 to 2.5.
  • the air gap extends in the axial direction over the overlapping area, preferably with a constant size.
  • the air guide vanes are attached to the fan housing in sections in the axial direction.
  • the air guide vanes in the axially inwardly directed area on the fan housing adjoining the blow-out opening to be attached.
  • the impeller and/or the air guide vanes are geometrically designed in such a way that an axial distance between the air guide vanes and the impeller increases in the radial direction from a first distance to a second distance lying radially further outward.
  • the formation can take place, for example, by obliquely facing axial outer edges, via which the distance can be varied.
  • the air guide vanes have a straight axial edge, while the impeller blades are beveled radially outwards in the direction of the inlet opening, so that the distance between the air guide vanes in the exhaust area and the impeller blades increases radially outwards.
  • a radius of the impeller at a point of application of the first distance is greater than the first axial distance.
  • the point of attack is the point at which the first distance is measured.
  • the first distance can be set variably, the associated radius results accordingly. The same applies accordingly to the second distance and the second radius.
  • the fan housing is designed in several parts and has an inlet nozzle and a discharge part, the inlet nozzle comprising the suction opening and the discharge part comprising the outlet opening.
  • a two-part design is also favorable, in which the inlet nozzle is connected to the blow-out part directly adjacent in the axial direction.
  • the inlet nozzle and the outlet part are plugged into one another.
  • Also promoting a compact, axially short structure is a design of the diagonal fan, according to which the inlet nozzle equalizes the flow diameter reducing inlet section forming the inlet opening, which extends in the axial direction into the impeller.
  • an embodiment variant is advantageous for low noise development, in which the impeller has a cover disk, with the impeller blades extending from the rotor to the cover disk.
  • the cover disk can completely cover the impeller blades at their axial outer edges in the radial direction.
  • the cover disk can have a section which runs axially parallel and faces the inlet opening and into which the inlet nozzle extends.
  • the problem of the small exhaust surface can be improved in that the exhaust opening forms a non-rotationally symmetrical exhaust surface. This is made possible, for example, by the blow-out surface having a square cross-section.
  • the intake opening has an intake diameter which corresponds to 40 to 75%, preferably 50 to 60%, of the maximum radial installation space of the diagonal ventilator.
  • the size of the intake opening is reduced compared to axial fans in order to improve the inflow.
  • the diagonal fan is characterized in that the impeller has an impeller diameter that corresponds to 80 to 95% of a maximum radial installation space of the diagonal fan.
  • An embodiment is also advantageous in which the impeller is arranged directly adjacent to the flow channel and an air flow generated by the impeller is conveyed directly into the flow channel.
  • FIG. 1 to 3 an embodiment of a diagonal fan 1 is shown in different views.
  • figure 4 is an associated longitudinal sectional view for a more precise representation of the individual component elements and their arrangement in relation to one another.
  • the diagonal ventilator 1 comprises a two-part ventilator housing formed from the inlet nozzle 31 having the inlet opening 3 and the exhaust part 32 comprising the exhaust opening 5, on the axial ends of which flanges 21, 20 are formed.
  • the inlet nozzle 31 is inserted into the blow-out part 32 .
  • the external rotor motor with the stator 11 and the rotor 9 is provided centrally around the axis of rotation RA and encloses the stator 11 in sections in the axial direction.
  • the impeller of the diagonal fan 1 is formed from the rotor 9 , the impeller blades 8 arranged thereon and a cover plate 24 which completely covers the impeller blades in the radial direction and has an end section running axially straight in the direction of the inlet opening 3 .
  • the rotor 9 forms a bottom disk for the impeller.
  • the impeller is thus designed to be integrated into the rotor 9 .
  • the inlet nozzle 31 comprises an inlet section 7 that reduces the flow diameter and extends into the impeller in the axial direction, so that the axially parallel end section of the cover disk 24 and the inlet section 7 overlap.
  • the axial flow channel 19 extends between the exhaust part 32 of the fan housing and the rotor 9 of the external rotor motor up to the exhaust opening 5 surrounding the stator 11.
  • the air guide vanes 10 are connected to the stator 11 and to the blow-out part 32 adjacent to the blow-out opening 5 .
  • the air guide vanes 10 extend both in the axial direction and in the circumferential direction. They extend in the axial direction in the overlapping section Ly over the rotor 9 and spaced from it by a radial air gap S, the air gap S in the embodiment shown corresponding to 1% of the maximum radial installation space B of the diagonal fan 1 .
  • the size of the air gap S is constant over its axial extent.
  • the ratio of the axial length of the overlapping section Ly of the air guide vanes 10 to the axially adjacent non-overlapping section Lx has a value of 2.1 in the embodiment shown.
  • the distance between the mutually facing axial edges of the air guide vanes 10 and the impeller blades 8 increases from a first distance A1 to a second distance A2, with the axial edges of the air guide vanes 10 straight radially outwards, the impeller blades 8 running obliquely.
  • the position of the first and second distance can be freely selected, where it applies that the radius R1 of the impeller at the point of application of the first distance A1 is greater than the first distance A1. It also applies that the radius R2 of the impeller at the point of application of the second distance A2 is greater than the second distance A2.
  • the impeller has an impeller diameter DA that corresponds to 90% of the maximum radial installation space B of the diagonal fan 1 .

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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 Diagonalventilator in verbesserter Kompaktbauweise mit hoher Leistungsdichte und geringer Geräuschentwicklung.The invention relates to a diagonal fan of improved compact design with high power density and low noise development.

Allgemein sind Diagonalventilatoren und deren Einsatz aus dem Stand der Technik bekannt, beispielsweise aus der DE 10 2014 210 373 A1 . Weiterer druckschriftlicher Stand der Technik aus dem vorliegenden technischen Gebiet ist aus den Veröffentlichungen DE 10 2004 058 003 A1 und US 2009/246017 A1 bekannt.Diagonal fans and their use are generally known from the prior art, for example from DE 10 2014 210 373 A1 . Further printed prior art from the present technical field is from the publications DE 10 2004 058 003 A1 and U.S. 2009/246017 A1 known.

Diagonalventilatoren werden in Anwendungen mit hohen Anforderungen an Luftleistung bei höherem Gegendruck und geringem Einbauplatz eingesetzt, beispielsweise in der Kühltechnik oder bei Dunstabzugshauben. Durch den bei Diagonalventilatoren im Verhältnis zum Bauraum großen Motordurchmesser des axialzentral angeordneten Motors ist die Ausblasfläche an der Ausblasöffnung verhältnismäßig klein, wodurch es zu hohen Austrittsverlusten bei der Strömung durch hohen dynamischen Druck am Austritt des Diagonalventilators kommt.Diagonal fans are used in applications with high demands Air capacity used with higher back pressure and little installation space, for example in cooling technology or in extractor hoods. Due to the large motor diameter of the axially centrally arranged motor in relation to the installation space in diagonal fans, the exhaust surface at the exhaust opening is relatively small, which results in high outlet losses in the flow due to high dynamic pressure at the outlet of the diagonal fan.

Es ist stets ein Ziel, die Leistung des Ventilators zu erhöhen, währenddessen die Geräuschbildung unverändert bleibt oder sich sogar reduziert. Zudem sollen die Ventilatoren immer kompakter aufgebaut sein, um den Platzbedarf zu verringern.It is always a goal to increase the performance of the fan while the noise level remains the same or is even reduced. In addition, the fans should be built more and more compactly in order to reduce the space requirement.

Der Erfindung liegt deshalb die Aufgabe zugrunde, einen Diagonalventilator in kompakter Bauform mit hoher Leistungsdichte und gutem Geräuschverhalten bereit zu stellen.The invention is therefore based on the object of providing a diagonal fan in a compact design with a high power density and good noise characteristics.

Diese Aufgabe wird durch die Merkmalskombination gemäß Patentanspruch 1 gelöst.This object is achieved by the combination of features according to claim 1.

Erfindungsgemäß wird ein Diagonalventilator mit einem Ventilatorgehäuse vorgeschlagen, innerhalb dem ein Außenläufermotor und ein Laufrad aufgenommen sind, wobei der Außenläufermotor einen Stator und einen den Stator zumindest teilweise umschließenden Rotor aufweist. Zwischen dem Ventilatorgehäuse und dem Außenläufermotor verläuft ein axialer Strömungskanal bis zu einer den Außenläufermotor umgebenden Ausblasöffnung des Diagonalventilators, wobei durch den Strömungskanal im Betrieb des Diagonalventilators über das Laufrad angesaugte Luft zur Ausblasöffnung förderbar ist. Das Laufrad ist dabei in den Rotor integriert.According to the invention, a diagonal fan with a fan housing is proposed, within which an external rotor motor and an impeller are accommodated, the external rotor motor having a stator and a rotor at least partially enclosing the stator. An axial flow channel runs between the fan housing and the external rotor motor up to an outlet opening of the diagonal fan surrounding the external rotor motor, air sucked in via the impeller being sucked in through the flow channel during operation of the diagonal fan and being conveyable to the outlet opening. The impeller is integrated into the rotor.

Die Integration des Laufrads in den Rotor wird dadurch bereitgestellt, dass Rotor und Laufrad einteilig ausgebildet sind. Die Teilezahl und der axiale Bauraum werden mithin minimiert. Alternativ zur einteiligen Ausführung kann die integrale Ausführung auch dadurch erreicht werden, dass Teile des Laufrads, wie z. B. die Laufradschaufeln, auf dem Rotor befestigt werden.The integration of the impeller into the rotor is provided by the fact that the rotor and impeller are designed in one piece. The number of parts and the axial Installation space is therefore minimized. As an alternative to the one-piece design, the integral design can also be achieved in that parts of the impeller, such as B. the impeller blades are mounted on the rotor.

Der Diagonalventilator weist erfindungsgemäß in einem an die Ausblasöffnung angrenzenden Ausblasabschnitt eine Luftleiteinrichtung mit mehreren in Umfangsrichtung verteilten Luftleitschaufeln auf. Die Luftleitschaufeln erstrecken sich in axialer Richtung zumindest in einem Überdeckungsabschnitt über den Rotor hinweg und sind dabei jeweils zu dem Rotor mit einem radialen Luftspalt beabstandet. Somit rotiert der Rotor relativ zu den Luftleitschaufeln.According to the invention, the diagonal fan has, in a blow-out section adjoining the blow-out opening, an air-guiding device with a plurality of air-guiding blades distributed in the circumferential direction. The air guide vanes extend in the axial direction at least in an overlapping section over the rotor and are each spaced apart from the rotor by a radial air gap. Thus, the rotor rotates relative to the airfoil vanes.

Der Luftspalt weist in einer für die Geräuschentwicklung und Leistung des Diagonalventilators vorteilhaften Ausführung eine Größe auf, die maximal 5%, vorzugsweise maximal 1,5% eines maximalen radialen Bauraums des Diagonalventilators entspricht. Der maximale radiale Bauraum wird durch die äußerste Hüllkontur des gesamten Diagonalventilators bestimmt. Bei einer gedachten Ausführung in zylindrischer Form entspräche der maximale radiale Bauraum dem maximalen Außendurchmesser.In an embodiment that is advantageous for the noise development and performance of the diagonal fan, the size of the air gap corresponds to a maximum of 5%, preferably a maximum of 1.5%, of a maximum radial installation space of the diagonal fan. The maximum radial installation space is determined by the outermost enveloping contour of the entire diagonal fan. In the case of an imaginary cylindrical design, the maximum radial installation space would correspond to the maximum outer diameter.

Ebenfalls vorteilhaft zur Lösung der Aufgabe ist eine Ausführung des Diagonalventilators, bei der ein Verhältnis einer axialen Länge des Überdeckungsabschnitts der Luftleitschaufeln zu einem Nichtüberdeckungsabschnitt, in dem die Luftleitschaufeln den Rotor in axialer Richtung nicht überdecken, in einem Bereich von 0,5 bis 4,0, vorzugsweise in einem Bereich von 1,5 bis 2,5 liegt. Der Luftspalt erstreckt sich in axialer Richtung über den Überdeckungsbereich vorzugsweise in konstanter Größe.Also advantageous for solving the problem is an embodiment of the diagonal fan in which the ratio of an axial length of the overlapping section of the air guide vanes to a non-overlapping section in which the air guide vanes do not overlap the rotor in the axial direction is in a range from 0.5 to 4.0 , preferably in a range from 1.5 to 2.5. The air gap extends in the axial direction over the overlapping area, preferably with a constant size.

Ferner ist in einer Ausführung vorgesehen, dass die Luftleitschaufeln in axialer Richtung abschnittsweise an dem Ventilatorgehäuse befestigt sind. Insbesondere können die Luftleitschaufeln im sich an die Ausblasöffnung anschließenden nach axial innen gerichteten Bereich am Ventilatorgehäuse befestigt werden.Furthermore, in one embodiment it is provided that the air guide vanes are attached to the fan housing in sections in the axial direction. In particular, the air guide vanes in the axially inwardly directed area on the fan housing adjoining the blow-out opening to be attached.

In einer zur Lösung der Aufgabe günstigen Weiterbildung des Diagonalventilators sind das Laufrad und/oder die Luftleitschaufeln geometrisch so ausgebildet, dass sich ein axialer Abstand zwischen den Luftleitschaufeln und dem Laufrad in radialer Richtung von einem ersten Abstand auf einen zweiten radial weiter außen liegenden Abstand vergrößert. Die Ausbildung kann beispielsweise durch schräge zueinander weisende axiale Außenkanten erfolgen, über welche der Abstand variiert werden kann. In einer vorteilhaften Lösung weisen die Luftleitschaufeln eine gerade Axialkante auf, die Laufradschaufeln werden hingegen nach radial außen in Richtung Einlassöffnung abgeschrägt, so dass sich der Abstand zwischen den Luftleitschaufeln im Ausblasbereich und den Laufradschaufeln nach radial außen gesehen vergrößert. Ferner ist vorteilhaft, wenn ein Radius des Laufrads an einem Angriffspunkt des ersten Abstands größer ist als der erste axiale Abstand. Der Angriffspunkt ist der Punkt, an dem der erste Abstand gemessen wird. Der erste Abstand ist variabel festlegbar, der zugehörige Radius ergibt sich entsprechend daraus. Gleiches gilt entsprechend für den zweiten Abstand und den zweiten Radius.In a further development of the diagonal fan that is favorable for solving the task, the impeller and/or the air guide vanes are geometrically designed in such a way that an axial distance between the air guide vanes and the impeller increases in the radial direction from a first distance to a second distance lying radially further outward. The formation can take place, for example, by obliquely facing axial outer edges, via which the distance can be varied. In an advantageous solution, the air guide vanes have a straight axial edge, while the impeller blades are beveled radially outwards in the direction of the inlet opening, so that the distance between the air guide vanes in the exhaust area and the impeller blades increases radially outwards. It is also advantageous if a radius of the impeller at a point of application of the first distance is greater than the first axial distance. The point of attack is the point at which the first distance is measured. The first distance can be set variably, the associated radius results accordingly. The same applies accordingly to the second distance and the second radius.

Eine vorteilhafte Ausführungsform des Diagonalventilators sieht vor, dass das Ventilatorgehäuse mehrteilig ausgeführt ist und eine Einlaufdüse sowie ein Ausblasteil aufweist, wobei die Einlaufdüse die Ansaugöffnung und das Ausblasteil die Ausblasöffnung umfasst.An advantageous embodiment of the diagonal fan provides that the fan housing is designed in several parts and has an inlet nozzle and a discharge part, the inlet nozzle comprising the suction opening and the discharge part comprising the outlet opening.

In einer kompakten Ausführung ist ferner eine zweiteilige Ausführung günstig, bei der die Einlaufdüse in axialer Richtung unmittelbar angrenzend mit dem Ausblasteil verbunden ist. In einer kompakten Ausführung sind die Einlaufdüse und das Ausblasteil ineinander gesteckt.In a compact design, a two-part design is also favorable, in which the inlet nozzle is connected to the blow-out part directly adjacent in the axial direction. In a compact design, the inlet nozzle and the outlet part are plugged into one another.

Ebenfalls einen kompakten axial kurzen Aufbau fördernd ist eine Ausführung des Diagonalventilators, wonach die Einlaufdüse einen den Strömungsdurchmesser verringernden, die Einlassöffnung bildenden Einlaufabschnitt aufweist, der sich in axialer Richtung in das Laufrad hinein erstreckt.Also promoting a compact, axially short structure is a design of the diagonal fan, according to which the inlet nozzle equalizes the flow diameter reducing inlet section forming the inlet opening, which extends in the axial direction into the impeller.

Für die geringe Geräuschentwicklung ist eine Ausführungsvariante vorteilhaft, bei der das Laufrad eine Deckscheibe aufweist, wobei sich die Laufradschaufeln von dem Rotor zu der Deckscheibe erstrecken. Die Deckscheibe kann die Laufradschaufeln an ihren axialen Außenkanten in radialer Richtung vollständig überdecken. Zudem kann die Deckscheibe einen zu Einlassöffnung weisenden achsparallel verlaufenden Abschnitt aufweisen, in den die Einlaufdüse sich hinein erstreckt.An embodiment variant is advantageous for low noise development, in which the impeller has a cover disk, with the impeller blades extending from the rotor to the cover disk. The cover disk can completely cover the impeller blades at their axial outer edges in the radial direction. In addition, the cover disk can have a section which runs axially parallel and faces the inlet opening and into which the inlet nozzle extends.

Die Problematik der geringen Ausblasfläche kann dadurch verbessert werden, dass die Ausblasöffnung eine nicht-rotationssymmetrische Ausblasfläche bildet. Dies wird beispielsweise durch eine im Querschnitt quadratische Form der Ausblasfläche ermöglicht.The problem of the small exhaust surface can be improved in that the exhaust opening forms a non-rotationally symmetrical exhaust surface. This is made possible, for example, by the blow-out surface having a square cross-section.

Ebenfalls vorteilhaft wirkt sich bei dem Diagonalventilator auf die Geräuschbildung aus, wenn die Ansaugöffnung einen Ansaugdurchmesser aufweist, der 40 bis 75%, vorzugsweise 50 bis 60% des maximalen radialen Bauraums des Diagonalventilators entspricht. Die Größe der Ansaugöffnung wird gegenüber Axialventilatoren verringert, um die Zuströmung zu verbessern.In the case of the diagonal ventilator, noise generation is also advantageous if the intake opening has an intake diameter which corresponds to 40 to 75%, preferably 50 to 60%, of the maximum radial installation space of the diagonal ventilator. The size of the intake opening is reduced compared to axial fans in order to improve the inflow.

Der Diagonalventilator ist in einer Ausführung dadurch gekennzeichnet, dass das Laufrad einen Laufraddurchmesser aufweist, der 80 bis 95% eines maximalen radialen Bauraums des Diagonalventilators entspricht.In one embodiment, the diagonal fan is characterized in that the impeller has an impeller diameter that corresponds to 80 to 95% of a maximum radial installation space of the diagonal fan.

Auch ist eine Ausführung vorteilhaft, bei der das Laufrad unmittelbar angrenzend an den Strömungskanal angeordnet und ein von dem Laufrad erzeugter Luftstrom unmittelbar in den Strömungskanal gefördert wird.An embodiment is also advantageous in which the impeller is arranged directly adjacent to the flow channel and an air flow generated by the impeller is conveyed directly into the flow channel.

Andere vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet bzw. werden nachstehend zusammen mit der Beschreibung der bevorzugten Ausführung der Erfindung anhand der Figuren näher dargestellt. Es zeigen:

Fig. 1
eine perspektivische Ansicht eines Diagonalventilators;
Fig. 2
eine Vorderansicht auf die Ansaugseite des Diagonalventilators aus Fig. 1,
Fig. 3
eine Hinteransicht auf die Ansaugseite des Diagonalventilators aus Fig. 1,
Fig. 4
eine Schnittansicht der oberen Hälfte des Diagonalventilators aus Fig. 1.
Other advantageous developments of the invention are characterized in the dependent claims or are described below together with the description of the preferred embodiment of the invention with reference to the figures shown in more detail. Show it:
1
a perspective view of a diagonal fan;
2
a front view of the suction side of the diagonal fan 1 ,
3
a rear view of the intake side of the diagonal fan 1 ,
4
Figure 12 shows a sectional view of the upper half of the diagonal fan 1 .

In den Figuren 1 bis 3 ist ein Ausführungsbeispiel eines Diagonalventilators 1 in verschiedenen Ansichten gezeigt. Figur 4 ist eine zugehörige Längsschnittansicht zur genaueren Darstellung der einzelnen Bauteilelemente und deren Anordnung zueinander.In the Figures 1 to 3 an embodiment of a diagonal fan 1 is shown in different views. figure 4 is an associated longitudinal sectional view for a more precise representation of the individual component elements and their arrangement in relation to one another.

Der Diagonalventilator 1 umfasst ein zweiteiliges Ventilatorgehäuse gebildet aus der die Einlassöffnung 3 aufweisenden Einlaufdüse 31 und dem die Ausblasöffnung 5 umfassenden Ausblasteil 32, an deren axialen Enden jeweils Flansche 21, 20 ausgebildet sind. Die Einlaufdüse 31 ist in das Ausblasteil 32 eingesteckt. Zentral um die Rotationsachse RA ist der Außenläufermotor mit dem Stator 11 und dem Rotor 9 vorgesehen, der den Stator 11 in Axialrichtung abschnittsweise umschließt.The diagonal ventilator 1 comprises a two-part ventilator housing formed from the inlet nozzle 31 having the inlet opening 3 and the exhaust part 32 comprising the exhaust opening 5, on the axial ends of which flanges 21, 20 are formed. The inlet nozzle 31 is inserted into the blow-out part 32 . The external rotor motor with the stator 11 and the rotor 9 is provided centrally around the axis of rotation RA and encloses the stator 11 in sections in the axial direction.

Das Laufrad des Diagonalventilators 1 wird gebildet aus dem Rotor 9, den daran angeordneten Laufradschaufeln 8 sowie einer die Laufradschaufeln in radialer Richtung vollständig überdeckende Deckscheibe 24, die einen axial gerade in Richtung der Einlassöffnung 3 verlaufenden Endabschnitt aufweist.The impeller of the diagonal fan 1 is formed from the rotor 9 , the impeller blades 8 arranged thereon and a cover plate 24 which completely covers the impeller blades in the radial direction and has an end section running axially straight in the direction of the inlet opening 3 .

Der Rotor 9 bildet dabei eine Bodenscheibe für das Laufrad. Das Laufrad ist somit in den Rotor 9 integriert ausgebildet. Die Einlassdüse 31 umfasst einen den Strömungsdurchmesser verringernden Einlaufabschnitt 7, der sich in axialer Richtung in das Laufrad hinein erstreckt, so dass sich der achsparallele Endabschnitt der Deckscheibe 24 und der Einlaufabschnitt 7 überlappen.The rotor 9 forms a bottom disk for the impeller. The impeller is thus designed to be integrated into the rotor 9 . The inlet nozzle 31 comprises an inlet section 7 that reduces the flow diameter and extends into the impeller in the axial direction, so that the axially parallel end section of the cover disk 24 and the inlet section 7 overlap.

An das Laufrad axial angrenzend erstreckt sich zwischen dem Ausblasteil 32 des Ventilatorgehäuse und dem Rotor 9 des Außenläufermotors der axiale Strömungskanal 19 bis zu der den Stator 11 umgebenden Ausblasöffnung 5.Axially adjacent to the impeller, the axial flow channel 19 extends between the exhaust part 32 of the fan housing and the rotor 9 of the external rotor motor up to the exhaust opening 5 surrounding the stator 11.

In einem an die Ausblasöffnung 5 angrenzenden Ausblasabschnitt ist eine Luftleiteinrichtung mit mehreren in Umfangsrichtung verteilten Luftleitschaufeln 10 angeordnet, die auch in Figur 3 gut zu erkennen sind. Angrenzend an die Ausblasöffnung 5 sind die Luftleitschaufeln 10 mit dem Stator 11 und mit dem Ausblasteil 32 verbunden. Die Luftleitschaufeln 10 erstrecken sich sowohl in axialer Richtung als auch in Umfangsrichtung. Dabei erstrecken sie sich in axialer Richtung in dem Überdeckungsabschnitt Ly über den Rotor 9 hinweg und zu diesem mit einem radialen Luftspalt S beabstandet, wobei der Luftspalt S in der gezeigten Ausführung 1% des maximalen radialen Bauraums B des Diagonalventilators 1 entspricht. Die Größe des Luftspalts S ist über seine axiale Erstreckung konstant. Das Verhältnis der axialen Länge des Überdeckungsabschnitts Ly der Luftleitschaufeln 10 zu dem axial angrenzenden Nichtüberdeckungsabschnitt Lx liegt in der gezeigten Ausführung bei einem Wert von 2,1.In a blow-out section adjacent to the blow-out opening 5, there is an air-guiding device with a plurality of air-guiding blades 10 distributed in the circumferential direction, which are also shown in figure 3 are easy to recognize. The air guide vanes 10 are connected to the stator 11 and to the blow-out part 32 adjacent to the blow-out opening 5 . The air guide vanes 10 extend both in the axial direction and in the circumferential direction. They extend in the axial direction in the overlapping section Ly over the rotor 9 and spaced from it by a radial air gap S, the air gap S in the embodiment shown corresponding to 1% of the maximum radial installation space B of the diagonal fan 1 . The size of the air gap S is constant over its axial extent. The ratio of the axial length of the overlapping section Ly of the air guide vanes 10 to the axially adjacent non-overlapping section Lx has a value of 2.1 in the embodiment shown.

Bezugnehmend insbesondere auf Fig. 4 vergrößert sich in einer Richtung nach radial außen gesehen der Abstand zwischen den zueinander weisenden Axialkanten der Luftleitschaufeln 10 und der Laufradschaufeln 8 von einem ersten Abstand A1 auf einen zweiten Abstand A2, wobei die Axialkanten der Luftleitschaufeln 10 gerade radial auswärts, die Laufradschaufeln 8 schräg verlaufen. Die Position des ersten und zweiten Abstands ist frei wählbar, wobei gilt, dass der Radius R1 des Laufrads an dem Angriffspunkt des ersten Abstands A1 größer ist als der erste Abstand A1. Ferner gilt, dass der Radius R2 des Laufrads an dem Angriffspunkt des zweiten Abstands A2 größer ist als der zweite Abstand A2. Das Laufrad weist einen Laufraddurchmesser DA auf, der 90% des maximalen radialen Bauraums B des Diagonalventilators 1 entspricht.Referring in particular to 4 viewed in a radially outward direction, the distance between the mutually facing axial edges of the air guide vanes 10 and the impeller blades 8 increases from a first distance A1 to a second distance A2, with the axial edges of the air guide vanes 10 straight radially outwards, the impeller blades 8 running obliquely. The position of the first and second distance can be freely selected, where it applies that the radius R1 of the impeller at the point of application of the first distance A1 is greater than the first distance A1. It also applies that the radius R2 of the impeller at the point of application of the second distance A2 is greater than the second distance A2. The impeller has an impeller diameter DA that corresponds to 90% of the maximum radial installation space B of the diagonal fan 1 .

Claims (15)

  1. A diagonal fan (1) having a fan housing, within which an external-rotor motor and an impeller are accommodated, wherein the external-rotor motor has a stator (11) and a rotor (9) which at least partly surrounds the stator (11), and an axial flow duct (19) runs between the fan housing and the external-rotor motor as far as a discharge opening (5), surrounding the external-rotor motor, of the diagonal fan, through which duct, during operation, air which is drawn in by means of the impeller can be conveyed to the discharge opening (5), and wherein an air guide apparatus having several air guide vanes (10) distributed in the circumferential direction is arranged in a discharge portion adjacent to the discharge opening (5), characterized in that the impeller is integrated in the rotor, by the rotor (9) and the impeller being designed as a single piece, and in that the air guide vanes (10) extend in the axial direction at least in an overlap portion (Ly) beyond the rotor (9) and are spaced apart from it with a radial air gap (S).
  2. The diagonal fan as claimed in claim 1, characterized in that a ratio of the axial length of the overlap portion (Ly) of the air guide vanes (10) to a nonoverlapping portion (Lx) in which the air guide vanes (10) do not overlap the rotor (9) in the axial direction lies in a range of 0.5 to 4.0, especially in a range of 1.5 to 2.5.
  3. The diagonal fan as claimed in claim 1 or 2, characterized in that the air guide vanes (10) are fastened for a portion to the fan housing in the axial direction.
  4. The diagonal fan as claimed in one of claims 1 to 3, characterized in that the air gap (S) corresponds at most to 5%, especially at most to 1.5% of a maximum radial installation space of the diagonal fan (1).
  5. The diagonal fan as claimed in one of the preceding claims, characterized in that the impeller and/or the air guide vanes (10) are designed such that an axial spacing between the air guide vanes (10) and the impeller increases in the radial direction from a first spacing (A1) to a second spacing (A2).
  6. The diagonal fan as claimed in claim 5, characterized in that a radius (R1) of the impeller at a point of attack of the first spacing (A1) is larger than the first spacing (A1).
  7. The diagonal fan as claimed in one of the preceding claims, characterized in that the fan housing is multiple-piece and comprises an inlet nozzle (31) and a discharge piece (32), while the inlet nozzle (31) has an intake opening and the discharge piece (32) comprises the discharge opening (5).
  8. The diagonal fan as claimed in claim 7, characterized in that the inlet nozzle (31) is connected to the discharge piece (32) bordering directly on it in the axial direction.
  9. The diagonal fan as claimed in one of claims 7 to 8, characterized in that the inlet nozzle (31) comprises an inlet portion (7) reducing the flow diameter, which extends in the axial direction into the impeller.
  10. The diagonal fan as claimed in one of the preceding claims, characterized in that the impeller comprises impeller vanes and a cover disk (24), while the impeller vanes extend from the rotor (9) to the cover disk (24).
  11. The diagonal fan as claimed in claim 10, characterized in that the cover disk (24) completely overlaps the impeller vanes in the radial direction.
  12. The diagonal fan as claimed in one of the preceding claims, characterized in that the discharge opening (5) forms a discharge surface which does not have rotational symmetry.
  13. The diagonal fan as claimed in one of claims 7 to 12, characterized in that the intake opening has an intake diameter corresponding to 40 to 75%, especially 50 to 60% of a maximum radial installation space of the diagonal fan (1).
  14. The diagonal fan as claimed in one of the preceding claims, characterized in that the impeller has an impeller diameter which corresponds to 80 to 95% of a maximum radial installation space of the diagonal fan (1).
  15. The diagonal fan as claimed in one of the preceding claims, characterized in that the impeller is situated bordering directly on the flow duct (19) and an air flow generated by the impeller can be delivered directly into the flow duct (19).
EP17781458.9A 2016-11-22 2017-10-04 Diagonal fan Active EP3405679B1 (en)

Applications Claiming Priority (2)

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DE102016122533.9A DE102016122533A1 (en) 2016-11-22 2016-11-22 Diagonal fan
PCT/EP2017/075261 WO2018095633A1 (en) 2016-11-22 2017-10-04 Diagonal fan

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EP3405679A1 EP3405679A1 (en) 2018-11-28
EP3405679B1 true EP3405679B1 (en) 2023-05-03

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US (1) US10851792B2 (en)
EP (1) EP3405679B1 (en)
CN (1) CN206468550U (en)
DE (1) DE102016122533A1 (en)
PL (1) PL3405679T3 (en)
WO (1) WO2018095633A1 (en)

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CA2952411C (en) * 2016-12-19 2022-03-22 S3 Manufacturing Inc. Mixed air flow fan for aerating an agricultural storage bin
USD894367S1 (en) * 2017-12-13 2020-08-25 Ebm-Papst Mulfingen Gmbh & Co. Kg Vent frame
DE102018128820A1 (en) 2018-11-16 2020-05-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonal fan with optimized housing
DE102018128823A1 (en) * 2018-11-16 2020-05-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonal fan with heating element
DE102018128813A1 (en) 2018-11-16 2020-05-20 Ebm-Papst Mulfingen Gmbh & Co. Kg Diagonal fan with swirl reduction on the diagonal impeller
DE102021209606A1 (en) 2021-09-01 2023-03-02 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Inlet nozzle for a radial fan

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DE4127134B4 (en) 1991-08-15 2004-07-08 Papst Licensing Gmbh & Co. Kg diagonal fan
AU2001269822A1 (en) * 2000-06-15 2001-12-24 Greenheck Fan Corporation In-line centrifugal fan
TWI305486B (en) 2004-08-27 2009-01-11 Delta Electronics Inc Heat-dissipating fan and its housing
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TWI377004B (en) * 2008-03-28 2012-11-11 Delta Electronics Inc Fan and fan frame thereof
JP6155544B2 (en) 2012-03-12 2017-07-05 日本電産株式会社 Centrifugal fan
DE102012106411A1 (en) * 2012-07-17 2014-01-23 Ruck Ventilatoren Gmbh Diagonal impeller for a diagonal fan and diagonal fan
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DE102015207800A1 (en) * 2015-04-28 2016-11-03 Ziehl-Abegg Se Diagonal or centrifugal fan, guide for such a fan and system with such a fan or with several such fans

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US10851792B2 (en) 2020-12-01
DE102016122533A1 (en) 2018-05-24
WO2018095633A1 (en) 2018-05-31
US20190101122A1 (en) 2019-04-04
CN206468550U (en) 2017-09-05
PL3405679T3 (en) 2023-08-14
EP3405679A1 (en) 2018-11-28

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