EP1250531B1 - Radial turbo-blower - Google Patents

Radial turbo-blower Download PDF

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Publication number
EP1250531B1
EP1250531B1 EP01901200A EP01901200A EP1250531B1 EP 1250531 B1 EP1250531 B1 EP 1250531B1 EP 01901200 A EP01901200 A EP 01901200A EP 01901200 A EP01901200 A EP 01901200A EP 1250531 B1 EP1250531 B1 EP 1250531B1
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EP
European Patent Office
Prior art keywords
rotor
bearing
stator
cavity
radial turbo
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.)
Expired - Lifetime
Application number
EP01901200A
Other languages
German (de)
French (fr)
Other versions
EP1250531A1 (en
Inventor
Josef Hodapp
Karl-Heinz Ronthaler
Hans Kriechel
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.)
Leybold GmbH
Original Assignee
Leybold Vakuum GmbH
Leybold Vacuum GmbH
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Publication date
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Publication of EP1250531A1 publication Critical patent/EP1250531A1/en
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Publication of EP1250531B1 publication Critical patent/EP1250531B1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • 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
    • 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
    • F04D25/0653—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the motor having a plane air gap, e.g. disc-type
    • 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
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps

Definitions

  • the invention relates to a turbo radial fan with a rotatable mounted impeller and a motor driving the impeller like it e.g. is shown in WO 9908363A.
  • Turbo radial blowers in vacuum technology are both in single stage as in a two-stage version usually like this built that impeller, motor and bearing spatially one behind the other are arranged, the impeller between the Storage is located or can be stored on the fly.
  • the Bearing lubrication is carried out using oil, which is carried out by a Oil production facility is promoted to the bearings.
  • Such Turbo radial fans have a large axial length and a large number of components. They require complicated balancing processes. There is also a risk of contamination of the Impeller area with the one intended for bearing lubrication Oil.
  • the motor is in a vacuum, which makes it complex Winding insulation is required, with the consequence worse Heat transfers and a sealed cable duct for the power lines.
  • the invention has for its object a turbo radial fan to create that has a compact design and out few components can be manufactured inexpensively.
  • the bearing assembly is lubricated with grease, whereby at least one fat chamber is provided in the cavity of the impeller is.
  • the bearing assembly is lubricated with grease, whereby at least one fat chamber is provided in the cavity of the impeller is.
  • magnetic bearings use, which are also maintenance-free. Is conceivable also the combination of magnetic bearings and grease-lubricated bearings.
  • the cavity of the impeller is preferably towards the rear open and at the rear end of the cavity is between the Impeller and the bearing mandrel formed a sealing gap.
  • This Sealing gap prevents grease and bearing components from being sucked in from the cavity into the pump room. It is also possible to use a seal at this point, however then abrasion from the seal could get into the pump chamber.
  • a heat-conducting spacer ring on the bearing mandrel Narrow heat transfer gap of at most 0.5 mm in width Dissipation of heat from the impeller is formed on the bearing mandrel.
  • a pressure-tight can be between the impeller and the stator coils be arranged magnetically permeable partition.
  • This partition can be made from a membrane, from a fiber composite material or a potting compound. It creates a vacuum seal between the pump room and the engine room, so the the stator contained in the engine compartment is on the atmosphere side and not in a vacuum room. This enables one easier and cheaper winding insulation of the stator windings.
  • the stator housing is not pressure-tight Power feed-through required. Rather, a simple one Terminal box can be used.
  • the cooling can also be done be significantly simplified by the fact that a cooling device is housed in the stator housing. This cooler cools both the stator and the bearing mandrel and causes heat dissipation from the impeller to the bearing mandrel transferred heat.
  • turbo radial fan according to the invention is particularly suitable for high-speed fans, for example for use in rapidly flowing CO 2 lasers.
  • the turbo radial fan has a stator housing 10 and Pump housing 11 on.
  • the pump housing 11 contains one Pump chamber 12, in which a rotatable impeller 13 is arranged, which has a hub 14 and projecting vanes 15.
  • the wings 15 have outer edges that correspond to the contour of the wall of the follow the pump housing 11 with a small gap. The pump sucks the fluid to be pumped axially and conveys it radially to the Outlets 16.
  • the hub 14 of the impeller 13 contains a carrier part 17 which consists of a pipe section 18 and a flange section 19.
  • the flange portion 19 forms the rear end wall of the impeller 13. It contains recesses in which permanent magnets 20 are arranged. These permanent magnets have one axial magnetic field alignment. This means that the North Pole N and the south pole S on a parallel to the impeller axis Line.
  • the carrier part 17 and the hub 14 are made made of non-magnetic material.
  • a partition 21 is adjacent to the permanent magnets 20 provided that the interior 22 of the stator 10 from the Pump room 12 separates.
  • the partition 21 consists of a magnetic permeable membrane, preferably made of composite fiber material, or a potting compound. It creates a vacuum seal between the stator chamber 22 and the pump chamber 12.
  • the impeller 13 has an inner cavity 23 which is at the front End is sealed with a cap 24.
  • a bearing mandrel 25 projects into this cavity 23, on which the Impeller 13 is mounted with a bearing arrangement 26.
  • To the Bearing arrangement include two rolling bearings, namely a front one Ball bearings 27 and a rear ball bearing 28. These ball bearings sit on the mandrel 25 and they support the pipe section 18 of the carrier part 17. At least each ball bearing borders a grease chamber 29 to the pasty grease for bearing lubrication contains. At least one of these camps can also be used as Magnetic bearings can be executed. In principle there is also one complete bearing design in magnetic bearings possible.
  • a cap 30 is fastened to the outer end of the bearing mandrel 25, which supports a plate spring assembly 31, which in turn presses against the front ball bearing 27 and thus the Bearing arrangement keeps axially compressed.
  • a spacer ring 32 made of a good heat-conducting material is in close contact with the mandrel 25.
  • a heat transfer gap 33 with a width of at most 0.5 mm, preferably of about 0.4 mm, to dissipate the heat from the impeller 13 via the spacer ring 32 to bearing pin 25.
  • a sealing gap 34 is formed between the rear end of the tube section 18 of the Carrier part 17 and the bearing mandrel 25. This sealing gap enables gas extraction from the Pump chamber 12 into the cavity 23. One of the cavities takes place Derivation through a hole (not shown) in the bearing mandrel 25.
  • the sealing gap 34 represents the only opening in the cavity 23 represents
  • stator 35 In the stator chamber 22 is the stator 35 with the Stator coils 36, which are embedded in an iron package 37.
  • the stator 35 forms, together with the permanent magnets 20 containing carrier part 17, the disc motor 44.
  • Die Stator coils 36 lie on the same circle on which the Move the permanent magnets 20 when the impeller 13 rotates.
  • On Electronic commutator creates in the stator windings 36 circulating current, so that the stator windings generate a rotating magnetic field.
  • the impeller 13 follows its permanent magnet 20 this magnetic field. It is about with the disc rotor motor almost a magnetic coupling for the contactless impeller drive.
  • the air gap between the Stator coils 36 and the permanent magnet 20 is of the Partition 21 penetrates.
  • This partition is sealing attached a base 38 which on a bottom wall 39 of the Stator housing 10 is fixed and part of Bearing mandrel 25 forms. Since the partition 21 of the stator 22 from separates the vacuum part, there is 22 atmospheric pressure in the stator space. There is one in the wall of the stator housing 10 Cable opening 40 for the passage of power cables. Further a pipe feed-through opening 41 is provided through which Pass pipes 42 which are part of one of Cooling water flows through the cooling coil, which is the cooling device 43 forms. The cooling device 43 cools both the Stator 35 and the bearing mandrel 25 and carries the heat from the entire fan housing.
  • the turbo radial fan consists of few individual parts and is inexpensive to manufacture. It is largely maintenance-free.

Abstract

The radial turbo-blower comprises a stator (35) that is housed in a stator housing (10) and a rotor (13) that rotates within a pump housing (11). The rotor (13) comprises a cavity (23) with a bearing arrangement (26) that is received by a protruding bearing pin (25). A pump chamber (12) is separated from a stator chamber (22) by a thin partition wall (21). Thereby, an atmospheric pressure is maintained in the stator chamber (22). The blower consists of few components and has a short structural length. It is substantially maintenance-free and the rotor area is protected from being contaminated by oil.

Description

Die Erfindung betrifft ein Turboradialgebläse mit einem drehbar gelagerten Laufrad und einem das Laufrad treibenden Motor, wie es z.B. in der WO 9908363A gezeigt wird.The invention relates to a turbo radial fan with a rotatable mounted impeller and a motor driving the impeller like it e.g. is shown in WO 9908363A.

Turboradialgebläse in der Vakuumtechnik sind sowohl in einstufiger wie auch in zweistufiger Ausführung üblicherweise so aufgebaut, dass Laufrad, Motor und Lagerung räumlich hintereinander angeordnet sind, wobei das Laufrad sich zwischen den Lagern befindet oder fliegend gelagert sein kann. Die Lagerschmierung erfolgt mittels Öl, das durch eine Ölfördereinrichtung zu den Lagern gefördert wird. Solche Turboradialgebläse haben eine große axiale Baulänge und eine große Zahl von Bauteilen. Sie erfordern komplizierte Auswuchtvorgänge. Ferner besteht die Gefahr der Kontamination des Laufradbereichs mit dem für die Lagerschmierung vorgesehenen Öl. Der Motor befindet sich im Vakuum, wodurch eine aufwendige Wicklungsisolation erforderlich ist, mit der Folge schlechter Wärmeübergänge und einer abgedichteten Leitungsdurchführung für die Stromleitungen. Turbo radial blowers in vacuum technology are both in single stage as in a two-stage version usually like this built that impeller, motor and bearing spatially one behind the other are arranged, the impeller between the Storage is located or can be stored on the fly. The Bearing lubrication is carried out using oil, which is carried out by a Oil production facility is promoted to the bearings. Such Turbo radial fans have a large axial length and a large number of components. They require complicated balancing processes. There is also a risk of contamination of the Impeller area with the one intended for bearing lubrication Oil. The motor is in a vacuum, which makes it complex Winding insulation is required, with the consequence worse Heat transfers and a sealed cable duct for the power lines.

Der Erfindung liegt die Aufgabe zugrunde, ein Turboradialgebläse zu schaffen, das eine kompakte Bauform hat und aus wenigen Komponenten kostengünstig hergestellt werden kann.The invention has for its object a turbo radial fan to create that has a compact design and out few components can be manufactured inexpensively.

Die Lösung dieser Aufgabe erfolgt erfindungsgemäß mit den im Patentanspruch 1 angegebenen Merkmalen. Hiernach ist der Motor ein permanenterregter Scheibenläufermotor, der an dem Laufrad befestigte Permamentmagnete mit axialer Magnetfeldausrichtung und ortsfeste Statorspulen aufweist. Der Motor ist somit teilweise in das Laufrad integriert und in unmittelbarer Laufradnähe angeordnet. Hierdurch wird die Baulänge des Gebläses verringert. Ferner ist das Laufrad mit einer Lageranordnung, welche in einem Hohlraum des Laufrades untergebracht ist, auf einem in den Hohlraum ragenden feststehenden Lagerdorn gelagert. Die Lagerung des Laufrades erfolgt also ausschließlich im Innern des Laufrades, wobei eine mitdrehende Welle nicht erforderlich ist. Vielmehr kann die Laufradnabe unmittelbar auf der auf dem Lagerdorn sitzenden Lageranordnung gelagert sein. Mit einer derartigen Lagerung werden auch Vibrationen des Laufrades vermieden. Es ergeben sich geringe Rotorverluste und dadurch eine Erhöhung des Wirkungsgrades. Der feststehende Lagerdorn erleichtert die Fertigung. Für den Motor kann eine einfache Wasserkühlung installiert werden.This object is achieved with the im Features specified claim 1. After that is the engine a permanently excited disc motor that is attached to the impeller fixed permanent magnet with axial magnetic field alignment and has stationary stator coils. The engine is therefore partial integrated into the impeller and in the immediate vicinity of the impeller arranged. As a result, the overall length of the fan is reduced. Furthermore, the impeller with a bearing arrangement, which is housed in a cavity of the impeller a fixed bearing mandrel protruding into the cavity. The impeller is therefore stored exclusively inside the impeller, whereby a rotating shaft is not required is. Rather, the impeller hub can be opened directly the bearing arrangement seated on the bearing mandrel. With such storage, vibrations of the Avoided impeller. There are low rotor losses and thereby an increase in efficiency. The fixed one Bearing mandrel makes production easier. For the engine one simple water cooling can be installed.

Vorzugsweise wird die Lageranordnung mit Fett geschmiert, wobei mindestens eine Fettkammer in dem Hohlraum des Laufrades vorgesehen ist. Alternativ hierzu besteht die Möglichkeit, Magnetlager einzusetzen, die ebenfalls wartungsfrei sind. Denkbar ist auch die Kombination Magnetlager und fettgeschmiertes Lager. Preferably, the bearing assembly is lubricated with grease, whereby at least one fat chamber is provided in the cavity of the impeller is. Alternatively, there is the option of magnetic bearings use, which are also maintenance-free. Is conceivable also the combination of magnetic bearings and grease-lubricated bearings.

Vorzugsweise ist der Hohlraum des Laufrades zur Rückseite hin offen und am rückwärtigen Ende des Hohlraumes ist zwischen dem Laufrad und dem Lagerdorn ein Dichtspalt ausgebildet. Dieser Dichtspalt verhindert das Einsaugen von Schmierfett und Lagerbestandteilen aus dem Hohlraum in den Pumpenraum. Es ist auch möglich, an dieser Stelle eine Dichtung einzusetzen, jedoch könnte dann Abrieb von der Dichtung in den Pumpenraum gelangen.The cavity of the impeller is preferably towards the rear open and at the rear end of the cavity is between the Impeller and the bearing mandrel formed a sealing gap. This Sealing gap prevents grease and bearing components from being sucked in from the cavity into the pump room. It is also possible to use a seal at this point, however then abrasion from the seal could get into the pump chamber.

Gemäß der Erfindung ist zwischen der den Hohlraum begrenzenden Wand und einem gut wärmeleitend auf dem Lagerdorn sitzenden Distanzring ein schmaler Wärmeübertragungsspalt von höchstens 0,5 mm Breite zur Ableitung von Wärme von dem Laufrad auf den Lagerdorn gebildet. Durch die Ausbildung eines schmalen Wärmeübertragungsspalts wird Wärme von dem Laufrad auf den gekühlten Lagerdorn abgeleitet.According to the invention between the wall defining the cavity and a good one a heat-conducting spacer ring on the bearing mandrel Narrow heat transfer gap of at most 0.5 mm in width Dissipation of heat from the impeller is formed on the bearing mandrel. By forming a narrow heat transfer gap heat is dissipated from the impeller to the cooled mandrel.

Zwischen dem Laufrad und den Statorspulen kann eine druckdichte magnetisch durchlässige Trennwand angeordnet sein. Diese Trennwand kann aus einer Membran, aus einem Faserverbundwerkstoff oder einer Vergußmasse bestehen. Sie bewirkt eine Vakuumdichtung zwischen dem Pumpenraum und dem Motorraum, so dass der im Motorraum enthaltene Stator sich auf der Atmosphärenseite befindet und nicht in einem Vakuumraum. Dies ermöglicht eine einfachere und billigere Wicklungsisolation der Statorwicklungen. Ferner ist an dem Statorgehäuse keine druckdichte Stromdurchführung erforderlich. Vielmehr kann ein einfacher Klemmenkasten benutzt werden.A pressure-tight can be between the impeller and the stator coils be arranged magnetically permeable partition. This partition can be made from a membrane, from a fiber composite material or a potting compound. It creates a vacuum seal between the pump room and the engine room, so the the stator contained in the engine compartment is on the atmosphere side and not in a vacuum room. This enables one easier and cheaper winding insulation of the stator windings. Furthermore, the stator housing is not pressure-tight Power feed-through required. Rather, a simple one Terminal box can be used.

Bei dem erfindungsgemäßen Turboradialgebläse kann auch die Kühlung wesentlich dadurch.vereinfacht werden, dass eine Kühlvorrichtung in dem Statorgehäuse untergebracht wird. Diese Kühlvorrichtung kühlt sowohl den Stator als auch den Lagerdorn und bewirkt eine Wärmeabfuhr der vom Laufrad auf den Lagerdorn übertragenen Wärme.In the turbo radial fan according to the invention, the cooling can also be done be significantly simplified by the fact that a cooling device is housed in the stator housing. This cooler cools both the stator and the bearing mandrel and causes heat dissipation from the impeller to the bearing mandrel transferred heat.

Wenn die Drehposition des Laufrades ermittelt werden soll, kann ein entsprechender Geber auf induktiver, kapazitiver oder optischer Basis vorgesehen sein, der im Stator angeordnet ist.If the rotational position of the impeller is to be determined, can a corresponding encoder on inductive, capacitive or optical Base should be provided, which is arranged in the stator.

Ein weiterer Vorteil der erfindungsgemäßen Ausführung des Motors als Scheibenläufermotor besteht darin, dass die Statorspulen den Rotor anziehen, so dass eine mechanische Aufbringung einer vorspannenden Axialkraft auf das Laufrad nicht erforderlich ist.Another advantage of the execution of the invention Motors as a disc rotor motor is that the stator coils tighten the rotor so that mechanical application a preloading axial force on the impeller is not required is.

Das erfindungsgemäße Turboradialgebläse eignet sich insbesondere für schnelllaufende Gebläse, beispielsweise für den Einsatz in schnellgeströmten CO2-Lasern.The turbo radial fan according to the invention is particularly suitable for high-speed fans, for example for use in rapidly flowing CO 2 lasers.

Im folgenden wird unter Bezugnahme auf die einzige Figur der Zeichnung ein Ausführungsbeispiel der Erfindung näher erläutert.In the following, with reference to the only figure of the Drawing an embodiment of the invention explained in more detail.

In der Zeichnung ist ein Turboradialgebläse im Längsschnitt dargestellt.In the drawing is a turbo radial fan in longitudinal section shown.

Das Turboradialgebläse weist ein Statorgehäuse 10 und ein Pumpengehäuse 11 auf. Das Pumpengehäuse 11 enthält einen Pumpenraum 12, in dem ein drehbares Laufrad 13 angeordnet ist, welches eine Nabe 14 und davon abstehende Flügel 15 aufweist. Die Flügel 15 haben Außenkanten, die der Kontur der Wand des Pumpengehäuses 11 mit geringem Spalt folgen. Die Pumpe saugt das zu pumpende Fluid axial an und fördert es radial zu den Auslässen 16.The turbo radial fan has a stator housing 10 and Pump housing 11 on. The pump housing 11 contains one Pump chamber 12, in which a rotatable impeller 13 is arranged, which has a hub 14 and projecting vanes 15. The wings 15 have outer edges that correspond to the contour of the wall of the Follow the pump housing 11 with a small gap. The pump sucks the fluid to be pumped axially and conveys it radially to the Outlets 16.

Die Nabe 14 des Laufrades 13 enthält ein Trägerteil 17, welches aus einem Rohrabschnitt 18 und einem Flanschabschnitt 19 besteht. Der Flanschabschnitt 19 bildet die rückwärtige Endwand des Laufrades 13. Er enthält Ausnehmungen, in denen Permanentmagnete 20 angeordnet sind. Diese Permanentmagnete haben eine axiale Magnetfeldausrichtung. Dies bedeutet, dass der Nordpol N und der Südpol S auf einer parallel zur Laufradachse verlaufenden Linie liegen. Das Trägerteil 17 und die Nabe 14 bestehen aus amagnetischen Material.The hub 14 of the impeller 13 contains a carrier part 17 which consists of a pipe section 18 and a flange section 19. The flange portion 19 forms the rear end wall of the impeller 13. It contains recesses in which permanent magnets 20 are arranged. These permanent magnets have one axial magnetic field alignment. This means that the North Pole N and the south pole S on a parallel to the impeller axis Line. The carrier part 17 and the hub 14 are made made of non-magnetic material.

Angrenzend an die Permanentmagnete 20 ist eine Trennwand 21 vorgesehen, die den Innenraum 22 des Statorgehäuses 10 von dem Pumpenraum 12 trennt. Die Trennwand 21 besteht aus einer magnetisch durchlässigen Membran, vorzugsweise aus Fasserverbundwerkstoff, oder einer Vergußmasse. Sie bewirkt eine Vakuumabdichtung zwischen dem Statorraum 22 und dem Pumpenraum 12.A partition 21 is adjacent to the permanent magnets 20 provided that the interior 22 of the stator 10 from the Pump room 12 separates. The partition 21 consists of a magnetic permeable membrane, preferably made of composite fiber material, or a potting compound. It creates a vacuum seal between the stator chamber 22 and the pump chamber 12.

Das Laufrad 13 weist einen inneren Hohlraum 23 auf, der am.vorderen Ende mit einer Kappe 24 abdichtend verschlossen ist. In diesen Hohlraum 23 ragt ein Lagerdorn 25 hinein, auf dem das Laufrad 13 mit einer Lageranordnung 26 gelagert ist. Zu der Lageranordnung gehören zwei Wälzlager, nämlich ein vorderes Kugellager 27 und ein rückwärtiges Kugellager 28. Diese Kugellager sitzen auf dem Lagerdorn 25 und sie lagern den Rohrabschnitt 18 des Trägerteils 17. An jedes Kugellager grenzt mindestens eine Fettkammer 29 an, die ein pastöses Fett zur Lagerschmierung enthält. Mindestens eines dieser Lager kann auch als Magnetlager ausgeführt sein. Prinzipiell ist auch eine komplette Lagerausführung in Magnetlager möglich.The impeller 13 has an inner cavity 23 which is at the front End is sealed with a cap 24. In a bearing mandrel 25 projects into this cavity 23, on which the Impeller 13 is mounted with a bearing arrangement 26. To the Bearing arrangement include two rolling bearings, namely a front one Ball bearings 27 and a rear ball bearing 28. These ball bearings sit on the mandrel 25 and they support the pipe section 18 of the carrier part 17. At least each ball bearing borders a grease chamber 29 to the pasty grease for bearing lubrication contains. At least one of these camps can also be used as Magnetic bearings can be executed. In principle there is also one complete bearing design in magnetic bearings possible.

Auf dem äußeren Ende des Lagerdorns 25 ist eine Kappe 30 befestigt, welche ein Tellerfederpaket 31 abstützt, das seinerseits gegen das vordere Kugellager 27 drückt und damit die Lageranordnung axial zusammengepresst hält.A cap 30 is fastened to the outer end of the bearing mandrel 25, which supports a plate spring assembly 31, which in turn presses against the front ball bearing 27 and thus the Bearing arrangement keeps axially compressed.

Zwischen den Kugellagern 27 und 28 befindet sich auf dem Lagerdorn 25 ein Distanzring 32 aus gut wärmeleitendem Material, der in engem Kontakt mit dem Lagerdorn 25 steht. Zwischen der den Hohlraum 23 begrenzenden Wand des rohrförmigen Teils 18 und dem Distanzring 32 befindet sich ein Wärmeübertragungsspalt 33 mit einer Breite von höchstens 0,5 mm, vorzugsweise von ca. 0,4 mm, zur Ableitung der Wärme von dem Laufrad 13 über den Distanzring 32 zum Lagerdorn 25.Between the ball bearings 27 and 28 is on the bearing mandrel 25 a spacer ring 32 made of a good heat-conducting material is in close contact with the mandrel 25. Between the Cavity 23 delimiting wall of the tubular part 18 and the Spacer ring 32 is a heat transfer gap 33 with a width of at most 0.5 mm, preferably of about 0.4 mm, to dissipate the heat from the impeller 13 via the spacer ring 32 to bearing pin 25.

Zwischen dem rückwärtigen Ende des Rohrabschnitts 18 des Trägerteils 17 und dem Lagerdorn 25 ist ein Dichtspalt 34 gebildet. Dieser Dichtspalt ermöglicht eine Gasabsaugung aus dem Pumpenraum 12 in den Hohlraum 23. Von dem Hohlraum erfolgt eine Ableitung durch eine (nicht dargestellte) Bohrung im Lagerdorn 25. Der Dichtspalt 34 stellt die einzige Öffnung des Hohlraumes 23 dar.Between the rear end of the tube section 18 of the Carrier part 17 and the bearing mandrel 25, a sealing gap 34 is formed. This sealing gap enables gas extraction from the Pump chamber 12 into the cavity 23. One of the cavities takes place Derivation through a hole (not shown) in the bearing mandrel 25. The sealing gap 34 represents the only opening in the cavity 23 represents

In dem Statorraum 22 befindet sich der Stator 35 mit den Statorspulen 36, die in ein Eisenpaket 37 eingelassen sind. Der Stator 35 bildet zusammen mit dem die Permanentmagnete 20 enthaltenden Trägerteil 17 den Scheibenläufermotor 44. Die Statorspulen 36 liegen auf demselben Kreis, auf dem sich die Permanentmagnete 20 bei Rotation des Laufrades 13 bewegen. Ein elektronischer Kommutator erzeugt in den Statorwicklungen 36 zyklisch umlaufend Strom, so dass die Statorwicklungen ein umlaufendes Magnetfeld erzeugen. Das Laufrad 13 folgt mit seinen Permanentmagneten 20 diesem Magnetfeld. Es handelt sich bei dem Scheibenläufermotor quasi um eine Magnetkupplung für den berührungslosen Laufradantrieb. Der Luftspalt zwischen den Statorspulen 36 und den Permanentmagneten 20 ist von der Trennwand 21 durchsetzt. Diese Trennwand ist abdichtend an einem Sockel 38 befestigt, der auf einer Bodenwand 39 des Statorgehäuses 10 fest montiert ist und einen Bestandteil des Lagerdorns 25 bildet. Da die Trennwand 21 den Statorraum 22 von dem Vakuumteil trennt, herrscht im Statorraum 22 Atmosphärendruck. In der Wand des Statorgehäuses 10 befindet sich eine Kabelöffnung 40 für die Durchführung von Stromkabeln. Ferner ist eine Rohrdurchführungsöffnung 41 vorgesehen, durch welche Rohrleitungen 42 hindurchführen, die Bestandteil einer von Kühlwasser durchströmten Kühlschlange ist, welche die Kühlvorrichtung 43 bildet. Die Kühlvorrichtung 43 kühlt sowohl den Stator 35 als auch den Lagerdorn 25 und führt die Wärme aus dem gesamten Gebläsegehäuse ab.In the stator chamber 22 is the stator 35 with the Stator coils 36, which are embedded in an iron package 37. The stator 35 forms, together with the permanent magnets 20 containing carrier part 17, the disc motor 44. Die Stator coils 36 lie on the same circle on which the Move the permanent magnets 20 when the impeller 13 rotates. On Electronic commutator creates in the stator windings 36 circulating current, so that the stator windings generate a rotating magnetic field. The impeller 13 follows its permanent magnet 20 this magnetic field. It is about with the disc rotor motor almost a magnetic coupling for the contactless impeller drive. The air gap between the Stator coils 36 and the permanent magnet 20 is of the Partition 21 penetrates. This partition is sealing attached a base 38 which on a bottom wall 39 of the Stator housing 10 is fixed and part of Bearing mandrel 25 forms. Since the partition 21 of the stator 22 from separates the vacuum part, there is 22 atmospheric pressure in the stator space. There is one in the wall of the stator housing 10 Cable opening 40 for the passage of power cables. Further a pipe feed-through opening 41 is provided through which Pass pipes 42 which are part of one of Cooling water flows through the cooling coil, which is the cooling device 43 forms. The cooling device 43 cools both the Stator 35 and the bearing mandrel 25 and carries the heat from the entire fan housing.

Das Turboradialgebläse besteht aus wenig Einzelteilen und ist kostengünstig herstellbar. Es ist weitgehend wartungsfrei.The turbo radial fan consists of few individual parts and is inexpensive to manufacture. It is largely maintenance-free.

Claims (8)

  1. A radial turbo-blower comprising a rotatably supported rotor (13) and a motor driving the rotor, the motor being a permanently excited disk armature motor (44) comprising permanent magnets (20) with an axial magnetic field orientation mounted to the rotor (13) and stationary stator coils (36), and that the rotor (13) is supported, by means of a bearing arrangement (26) housed in a cavity (23) of the rotor, on a stationary bearing pin (25) projecting into the cavity (23),
    characterized in that
    a narrow heat transmission gap (33) having a width of not more than 0.5 mm for carrying away heat from the rotor (13) to the bearing pin (25) is formed between the wall defining the cavity (23) and a spacer ring (32) seated on the bearing pin (25) in a well heat-conducting manner.
  2. The radial turbo-blower according to claim 1, characterized in that the bearing arrangement (26) comprises a grease lubrication with at least one grease chamber (29).
  3. The radial turbo-blower according to claim 1 or 2, characterized in that the cavity (23) of the rotor (13) is open only to the rear and that a sealing gap (34) is formed between the rotor (13) and the bearing pin (25) at the rear end of the cavity (23).
  4. The radial turbo-blower according to one of claims 1 to 3, characterized in that a pressure-tight magnetically permeable partition wall (21) is arranged between the rotor (13) and the stator coils (36).
  5. The radial turbo-blower according to claim 4, characterized in that the stator coils (36) are contained in a stator housing (10) under atmospheric pressure which contains a cooling device (43).
  6. The radial turbo-blower according to claim 5, characterized in that a portion (38) of the bearing pin (25) is in heat-conducting contact with the stator (35) and protrudes therefrom and is exposed to the effect of the cooling device (43) there.
  7. The radial turbo-blower according to claim 1, characterized in that one bearing is realized as a grease-lubricated bearing and one bearing, preferably the lower one, is realized as a passive magnetic bearing.
  8. The radial turbo-blower according to claim 1, characterized in that the bearing arrangement is realized with active magnetic bearings.
EP01901200A 2000-01-26 2001-01-24 Radial turbo-blower Expired - Lifetime EP1250531B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10003153 2000-01-26
DE10003153A DE10003153A1 (en) 2000-01-26 2000-01-26 Turbo radial fan
PCT/EP2001/000758 WO2001055598A1 (en) 2000-01-26 2001-01-24 Radial turbo-blower

Publications (2)

Publication Number Publication Date
EP1250531A1 EP1250531A1 (en) 2002-10-23
EP1250531B1 true EP1250531B1 (en) 2004-10-20

Family

ID=7628687

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01901200A Expired - Lifetime EP1250531B1 (en) 2000-01-26 2001-01-24 Radial turbo-blower

Country Status (8)

Country Link
US (1) US6682324B2 (en)
EP (1) EP1250531B1 (en)
JP (1) JP2003524730A (en)
KR (1) KR100635692B1 (en)
CN (1) CN1178005C (en)
AT (1) ATE280328T1 (en)
DE (2) DE10003153A1 (en)
WO (1) WO2001055598A1 (en)

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US11757330B2 (en) 2019-12-19 2023-09-12 Black & Decker, Inc. Canned outer-rotor brushless motor for a power tool

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US11757330B2 (en) 2019-12-19 2023-09-12 Black & Decker, Inc. Canned outer-rotor brushless motor for a power tool

Also Published As

Publication number Publication date
DE50104205D1 (en) 2004-11-25
KR100635692B1 (en) 2006-10-17
CN1440493A (en) 2003-09-03
CN1178005C (en) 2004-12-01
US6682324B2 (en) 2004-01-27
WO2001055598A1 (en) 2001-08-02
ATE280328T1 (en) 2004-11-15
EP1250531A1 (en) 2002-10-23
US20030118461A1 (en) 2003-06-26
DE10003153A1 (en) 2001-08-02
KR20030017466A (en) 2003-03-03
JP2003524730A (en) 2003-08-19

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