EP1880090B1 - Apparatus for the purification of gas while bleeding a crank housing - Google Patents

Apparatus for the purification of gas while bleeding a crank housing Download PDF

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Publication number
EP1880090B1
EP1880090B1 EP06724681.9A EP06724681A EP1880090B1 EP 1880090 B1 EP1880090 B1 EP 1880090B1 EP 06724681 A EP06724681 A EP 06724681A EP 1880090 B1 EP1880090 B1 EP 1880090B1
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EP
European Patent Office
Prior art keywords
chamber
housing
driving
rotor shaft
oil
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EP06724681.9A
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German (de)
French (fr)
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EP1880090A1 (en
Inventor
Serge Kup
Mats-Örjan POGEN
Ingvar HÄLLGREN
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Alfa Laval Corporate AB
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Alfa Laval Corporate AB
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/12—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/005—Centrifugal separators or filters for fluid circulation systems, e.g. for lubricant oil circulation systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
    • B04B9/06—Fluid drive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/12—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers
    • B04B2005/125—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers the rotors comprising separating walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
    • F01M2013/0422—Separating oil and gas with a centrifuge device
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S55/00—Gas separation
    • Y10S55/19—Crankcase ventilation

Definitions

  • the present invention relates to an apparatus for purifying gas in venting a crankcase, comprising a housing in which a deposition chamber is provided, a rotor assembly having a rotor shaft rotatably supported in the housing and a centrifugal rotor disposed in the deposition chamber and a fluidic drive means for driving the Rotor shaft by means of a drive fluid, wherein the drive means is arranged in a drive chamber which is separated by a housing separating wall of the separator chamber, wherein the rotor shaft extends through an opening in the housing partition and wherein in the region of the opening in the housing partition a labyrinth seal for sealing the Drive chamber is provided by the separator chamber.
  • Such a device is known from the prior art. This is how the document shows WO 2004/091799 A1 a corresponding device, are deposited with the oil particles of a coming of an internal combustion engine oil-air mixture by means of a centrifugal rotor.
  • the centrifugal rotor has a group of stacked, frusto-conical separator plates, which are arranged at regular intervals on the rotor shaft and non-rotatably coupled thereto. In their central area, the separator plates are provided with mutually aligned openings. Between the Abscheiderblechen conically extending outflow areas form, which open into a radially outer region of the Abscheiderhunt.
  • the rotor shaft and thus the centrifugal rotor are driven by a turbine wheel, which is arranged in the drive chamber and there is acted upon in operation with an oil jet. Due to the rotational movement of the centrifugal rotor and introduced in the central region of the engine oil-gas mixture is set in rotation and conveyed radially outward. It flows through the conical outflow areas. In this case, oil particles contained in the oil-gas mixture are deposited on the separator plates. Further, by the resulting in the central region of the centrifugal rotor Vacuum further oil-gas mixture sucked by the internal combustion engine.
  • the deposited on the Abscheiderblechen oil is also promoted because of their rotational movement and the resulting centrifugal forces radially outward and finally hurled from the radially outer edge of the Abscheiderbleche to the separator chamber limiting housing wall. From this, the separated oil flows due to gravity down into a collection channel and is returned via an outlet opening to the oil circuit of the engine.
  • a sealing ring for a centrifugal separator is off US 6,676,131 known. This has advantages in terms of installation and a good fixation in a groove receiving the sealing ring.
  • the drive chamber is accommodated in the lower chamber and separated from the flowing into the lower chamber of the oil-gas mixture.
  • the gap between the partition wall and the facing end wall of the separator must not be too large.
  • a labyrinth seal may be provided at this point, but this is not necessary and not desirable for a needs-based dimensioning of the intermediate gap between partition and facing end wall of the separation device, since the supply of the oil-gas mixture can be hindered.
  • a bearing bush of the housing partition has a pipe socket which projects to the drive chamber and serves to realize the labyrinth seal.
  • a bearing in particular a ball bearing, is accommodated for supporting the rotor shaft in the bearing bush of the housing partition wall.
  • the bearing bush is integrated in the housing partition.
  • the pipe socket is used advantageously for the realization of the labyrinth seal.
  • the labyrinth seal has a sealing disc with a circumferential axial groove and that a free end of the pipe socket in the axial groove, preferably non-contact, engages.
  • the sealing disc is rotationally coupled to the rotor shaft.
  • the labyrinth seal is thus formed in this embodiment of the invention between the housing-fixed pipe socket and the rotating rotor shaft. The invention thus avoids sealing parts that rotate with one another in operation with a contact seal that is prone to wear.
  • the drive device has a drive wheel which can be driven fluidly, preferably a fluidically impinged turbine wheel, which is mounted in a rotationally fixed manner on the rotor shaft and coupled to the sealing disk.
  • the sealing washer between the drive wheel and bearing is arranged.
  • the sealing disc has a radial region of greater thickness, which contacts an inner ring of the bearing. As a result, the sealing disc can be used at the same time for bracing the bearing.
  • the invention further relates to a sealing arrangement in a device of the type described above, comprising a labyrinth seal which seals non-contact the separator chamber of the drive chamber.
  • a centrifugal separating device is shown in a section containing the longitudinal axis A and generally designated 10.
  • the separator 10 includes a housing 12 enclosing a separator chamber 14.
  • the housing 12 is formed open at the bottom and closed by a bottom-side housing partition 16.
  • the housing is provided with an inlet nozzle 18, which defines an inlet 20 opening into the separator chamber 14.
  • the housing 12 further has an outlet, not shown.
  • the housing 12 holding webs 22 and 24 which receive a bearing cup 26 and hold in the housing 12.
  • the bearing cup 26 is stepped and includes apertures 28 such that the inlet 20 is fluidly connected to the separator chamber 14.
  • a ball bearing 30 is rotatably received with its outer ring.
  • the inner ring of the ball bearing 30 is pressed onto a rotor shaft 32.
  • the rotor shaft 32 is also mounted via a further ball bearing 34 in the housing partition 16.
  • the housing partition 16 has a central opening which is surrounded by an integrally formed tubular extension 36.
  • the ball bearing 34 is pressed with its outer ring in the inner peripheral surface of the pipe socket 36 and is held at the lower end by a diameter constriction on the neck 36.
  • the inner ring of the ball bearing 34 sits on the rotor shaft 32nd
  • a plurality of frustoconical Abscheiderbleche 38 are arranged at regular intervals and rotatably mounted on the rotor shaft 32.
  • the separator plates 38 also have openings 40 in their horizontally extending central area. The rotor shaft 32 and the separator plates 38 together form a centrifugal rotor 39.
  • a bottom part 42 is further arranged with a collecting channel 44 integrally formed therein.
  • the collecting channel 44 is bounded radially on the inside by a circumferential channel wall 46 formed on the funnel bottom 42.
  • an oil sump 48 is formed between the bottom part 42 and the housing partition wall 16 so an oil sump 48 is formed.
  • the collecting duct 44 is connected to the oil collecting basin 48 via bottom-side drainage slots 50, which are distributed uniformly in the circumferential direction.
  • a discharge opening 52 is provided for oil discharge.
  • a drive chamber 60 is arranged below the housing partition wall 16, which is only partially shown.
  • the rotor shaft 16 extends through the tube extension 36 in the drive chamber 60.
  • a drive wheel designed as a turbine wheel 64 is mounted rotationally fixed.
  • the turbine wheel 64 has at its upper end turbine blades 66, which via an in Fig. 1 and 2 No nozzle can be acted upon with an oil jet, so that the oil impinging on the turbine blades 66, the turbine wheel 64 and thus the rotor shaft 16 together with the separator plates attached thereto 38 in rotation about the axis A. Details of the arrangement in the region of the lower ball bearing 34 also go out Fig. 2 out.
  • a sealing washer 70 made of steel or another dimensionally stable material is used.
  • the sealing washer 70 is in a single part illustration in Fig. 3 shown. It has a central opening 72, which is bordered by a raised radial area 74. The raised radial region 74 serves to rest on the inner ring of the ball bearing 36.
  • the underside of the sealing disc 70 is essentially planar. Furthermore, the sealing disc 70 has a circumferential groove 76 whose width B exceeds the wall thickness b of the lower free end of the tube extension 36.
  • the lower free end of the pipe socket 36 protrudes contactlessly into the groove 76, so that a labyrinthine gap between the lower free end of the pipe socket 36 and the groove 76 is formed.
  • the gap width is, for example, in the range of 0.01 mm to 0.20 mm.
  • the turbine blades 66 of the turbine wheel 64 are under pressure with a fluid, preferably engine oil, so that the turbine wheel 64 is rotated and drives the rotor shaft 32.
  • the separator plates 38 rotate with the rotor shaft 32. They set the air in the central region of the centrifugal rotor 39 consisting of the rotor shaft 32 and separator plates 38 to rotate, so that it flows outwards due to the centrifugal action. This results in a negative pressure in the central region and an intake effect (see arrow P), so that an oil-air mixture is sucked in via the inlet port 18 from a crankcase of an internal combustion engine.
  • the oil-air mixture contains oil particles that are to be separated from the air.
  • the oil-air mixture passes through the openings 28 to the separator plates 38 and is rotated there. Part of the oil-air mixture flows through the apertures 40 down, the other part of the oil-air mixture moves due to centrifugal force radially outward and impinges on the conical regions of Abscheiderbleche 38. In this case, the divide in the oil-air Mixed oil droplets from the air and stick to the separator plates. The separated oil is conveyed by the centrifugal force on the Abscheiderblechen 38 radially outwardly and finally thrown off at the radially outer edge, as in Fig. 1 shown at 54. On the side wall 56 of the housing, an oil film 58 is formed which, due to gravity, flows downwards and collects in the collecting duct 44.
  • the separated oil can flow via the drainage slots 50 into the fluid collection basin 48 and be led back into the oil circuit of the engine.
  • the purified air separated from the oil particles flows out of the separator chamber 14 via the outlet, not shown, and can be discharged to the atmosphere.
  • the sealing washer 70 is provided for the formation of the labyrinth seal. It has been found that the inventive use of the sealing disc 70 with the groove 76 and a resulting non-contact labyrinth seal has significant advantages over contacting seals, such as in the WO 2004/091799 A1 shown. On the one hand, contact seals are subject to ever-increasing wear as the operating time increases, which can even lead to seal failure.
  • Labyrinth seal according to the invention without contact and is therefore not subject to any friction due to wear. Furthermore, in certain operating situations, in particular in a high-performance operation of the internal combustion engine, relatively high pressures or pressure peaks may occur in the separator chamber, which must be reduced in the short term. In this case, a pressure reduction via the drain slots 50 and the discharge opening 52 is to be avoided, because otherwise the oil drainage process would be interrupted and under certain circumstances too much oil would remain in the separator chamber 14. This would result in a deterioration of the separator effect.
  • the invention now offers the advantage that a pressure reduction to the drive chamber 60 can take place via the labyrinth seal between the sealing washer 70 and the tube extension 36. Nevertheless, the labyrinth seal ensures a sufficiently good sealing of the separator chamber 14 from the drive chamber 60, so that in the drive chamber 60 existing oil droplets can not enter the separator chamber 14.

Landscapes

  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
  • Centrifugal Separators (AREA)

Abstract

The invention relates to an apparatus (10) for purifying gas while bleeding a crank housing, said apparatus (10) comprising a housing (12) inside which a separator chamber (14) is provided, a rotor arrangement with a rotor shaft (32) that is rotatably mounted in the housing and a centrifugal rotor (39) located in the separator chamber (14), and a fluid driving device (64) for driving the rotor shaft (32) by means of a driving fluid, the driving device (64) being disposed in a driving chamber (60) that is separated from the separator chamber (14) by means of a housing partition (16), and the rotor shaft (32) extending through a breakthrough in the housing partition (16). In the case of this device, it is provided that a labyrinth-type seal (70) is provided in the zone of the breakthrough in order to seal the driving chamber (60) from the separator chamber (14).

Description

Fachgebiet der ErfindungField of the invention

Die vorliegende Erfindung betrifft eine Vorrichtung zum Reinigen von Gas beim Entlüften eines Kurbelgehäuses, umfassend ein Gehäuse, in dem eine Abscheiderkammer vorgesehen ist, eine Rotoranordnung mit einer in dem Gehäuse drehbar gelagerten Rotorwelle und einem in der Abscheiderkammer angeordneten Zentrifugalrotor und eine fluidische Antriebseinrichtung zum Antreiben der Rotorwelle mittels eines Antriebsfluids, wobei die Antriebseinrichtung in einer Antriebskammer angeordnet ist, die durch eine Gehäusetrennwand von der Abscheiderkammer getrennt ist, wobei sich die Rotorwelle durch einen Durchbruch in der Gehäusetrennwand hindurch erstreckt und wobei im Bereich des Durchbruchs in der Gehäusetrennwand eine Labyrinthdichtung zum Abdichten der Antriebskammer von der Abscheiderkammer vorgesehen ist.The present invention relates to an apparatus for purifying gas in venting a crankcase, comprising a housing in which a deposition chamber is provided, a rotor assembly having a rotor shaft rotatably supported in the housing and a centrifugal rotor disposed in the deposition chamber and a fluidic drive means for driving the Rotor shaft by means of a drive fluid, wherein the drive means is arranged in a drive chamber which is separated by a housing separating wall of the separator chamber, wherein the rotor shaft extends through an opening in the housing partition and wherein in the region of the opening in the housing partition a labyrinth seal for sealing the Drive chamber is provided by the separator chamber.

Stand der TechnikState of the art

Eine derartige Vorrichtung ist aus dem Stand der Technik bekannt. So zeigt das Dokument WO 2004/091799 A1 eine entsprechende Vorrichtung, mit der Ölpartikel eines von einem Verbrennungsmotor kommenden Öl-Luft-Gemischs mittels eines Zentrifugalrotors abgeschieden werden. Der Zentrifugalrotor weist eine Gruppe von stapelartig angeordneten, kegelstumpfförmig ausgebildeten Abscheiderblechen auf, die in regelmäßigen Abständen auf der Rotorwelle angeordnet und drehfest mit dieser gekoppelt sind. In ihrem zentralen Bereich sind die Abscheiderbleche mit zueinander fluchtenden Durchbrüchen versehen. Zwischen den Abscheiderblechen bilden sich konisch verlaufende Ausströmbereiche aus, die in einen radial äußeren Bereich der Abscheiderkammer münden. Die Rotorwelle und damit der Zentrifugalrotor werden über ein Turbinenrad angetrieben, das in der Antriebskammer angeordnet ist und dort im Betriebsfall mit einem Ölstrahl beaufschlagt wird. Aufgrund der Drehbewegung des Zentrifugalrotors wird auch das in dessen zentralen Bereich vom Verbrennungsmotor eingeleitete Öl-Gas-Gemisch in Rotation versetzt und nach radial außen gefördert. Es strömt durch die konisch verlaufenden Ausströmbereiche. Dabei scheiden sich in dem Öl-Gas-Gemisch enthaltene Ölpartikel an den Abscheiderblechen ab. Ferner wird durch den im zentralen Bereich des Zentrifugalrotors entstehenden Unterdruck weiteres Öl-Gas-Gemisch vom Verbrennungsmotor angesaugt. Das an den Abscheiderblechen abgeschiedene Öl wird wegen deren Drehbewegung und den daraus resultierenden Zentrifugalkräften ebenfalls nach radial außen gefördert und schließlich von dem radial äußeren Rand der Abscheiderbleche an die die Abscheiderkammer begrenzende Gehäusewand geschleudert. Von dieser fließt das abgeschiedene Öl schwerkraftbedingt nach unten in einen Sammelkanal und wird über eine Austrittsöffnung wieder dem Ölkreislauf des Verbrennungsmotors zugeführt.Such a device is known from the prior art. This is how the document shows WO 2004/091799 A1 a corresponding device, are deposited with the oil particles of a coming of an internal combustion engine oil-air mixture by means of a centrifugal rotor. The centrifugal rotor has a group of stacked, frusto-conical separator plates, which are arranged at regular intervals on the rotor shaft and non-rotatably coupled thereto. In their central area, the separator plates are provided with mutually aligned openings. Between the Abscheiderblechen conically extending outflow areas form, which open into a radially outer region of the Abscheiderkammer. The rotor shaft and thus the centrifugal rotor are driven by a turbine wheel, which is arranged in the drive chamber and there is acted upon in operation with an oil jet. Due to the rotational movement of the centrifugal rotor and introduced in the central region of the engine oil-gas mixture is set in rotation and conveyed radially outward. It flows through the conical outflow areas. In this case, oil particles contained in the oil-gas mixture are deposited on the separator plates. Further, by the resulting in the central region of the centrifugal rotor Vacuum further oil-gas mixture sucked by the internal combustion engine. The deposited on the Abscheiderblechen oil is also promoted because of their rotational movement and the resulting centrifugal forces radially outward and finally hurled from the radially outer edge of the Abscheiderbleche to the separator chamber limiting housing wall. From this, the separated oil flows due to gravity down into a collection channel and is returned via an outlet opening to the oil circuit of the engine.

Im vorstehenden Stand der Technik ist das Erfordernis erläutert, dass die Abscheiderkammer von der Antriebskammer möglichst dicht abgetrennt werden muss. Insbesondere soll vermieden werden, dass beim Antreiben des Turbinenrads in der Antriebskammer entstehende Öltröpfchen in die Abscheiderkammer eintreten und dort die bereits von den Ölpartikeln befreite Luft wieder kontaminieren. Hierzu ist vorgesehen, ein Lager, das in der Gehäusetrennwand aufgenommen ist und das die Rotorwelle drehbar lagert, durch eine kontaktierende Scheibendichtung möglichst fluid- und gasdicht zu gestalten. Allerdings hat sich gezeigt, dass die die Scheibendichtung mit zunehmender Betriebsdauer einem gewissen Verschleiß unterliegt und dadurch ihre Dichtwirkung nachlässt. Darüber hinaus sieht dieser Stand der Technik vor, dass zwischen der Abscheiderkammer und der Antriebskammer eine Ölsammelkammer vorgesehen ist. Allerdings kann es in bestimmten Betriebssituationen zu einem starken Druckanstieg in der Abscheiderkammer kommen, wobei der Druck aufgrund der zwischengeschalteten Ölsammelkammer und der kontaktierenden Dichtungsscheibe nicht zur Antriebskammer hin abgebaut werden kann. Als Folge davon weicht Öl-Gas-Gemisch über die Austrittsöffnung aus der Abscheiderkammer in die Ölsammelkammer, so dass vorübergehend kein abgeschiedenes Öl mehr aus der Abscheiderkammer abfließen kann. Dadurch wird die Funktionsweise der Vorrichtung beeinträchtigt.In the above prior art, the requirement is explained that the separator chamber must be separated as tightly as possible from the drive chamber. In particular, it should be avoided that occur during driving of the turbine wheel in the drive chamber resulting oil droplets in the deposition chamber and there contaminate the already freed from the oil particles air again. For this purpose, it is provided that a bearing which is accommodated in the housing separating wall and which rotatably supports the rotor shaft can be made as fluid-tight and gastight as possible by a contacting disk seal. However, it has been shown that the disk seal is subject to a certain wear with increasing service life and thereby decreases its sealing effect. In addition, this prior art provides that an oil collection chamber is provided between the separator chamber and the drive chamber. However, in certain operating situations, a strong increase in pressure may occur in the separator chamber, whereby the pressure due to the intermediate oil collection chamber and the contacting sealing washer can not be reduced to the drive chamber. As a result, oil-gas mixture on the outlet opening from the separator chamber in the oil collection chamber, so that temporarily no separated oil can flow out of the separator chamber. This affects the operation of the device.

Ein Dichtungsring für eine Zentrifugaltrennvorrichtung ist aus US 6,676,131 bekannt. Dieser besitzt Vorteile hinsichtlich der Montage und einer guten Fixierung in einer den Dichtungsring aufnehmenden Nut.A sealing ring for a centrifugal separator is off US 6,676,131 known. This has advantages in terms of installation and a good fixation in a groove receiving the sealing ring.

Eine weitere Trennvorrichtung ist aus US 2004/0107681 A1 bekannt. Auch bei diesem Stand der Technik wird der Zentrifugalrotor über ein Turbinenrad mit einem Ölstrahl angetrieben. Das Turbinenrad ist jedoch unmittelbar in der Abscheiderkammer vorgesehen, so dass die beim Auftreffen des Ölstrahls auf das Turbinenrad entstehenden Öltröpfchen das zu reinigende Öl-Gas-Gemisch zusätzlich verunreinigen. Aus WO 03/061838 ist ferner eine Trennvorrichtung bekannt, bei der eine Dichtmittel, wie eine Labyrinthdichtung, vorgesehen sein kann. Die Vorrichtung ist in der oberen Kammer eines durch eine Trennwand zweigeteilten Gehäuse aufgenommen. Das Öl-Gas-Gemisch wird über eine Öffnung in der unteren Kammer des Gehäuses zugeführt und durch erreicht die obere Kammer und die Trennvorrichtung über eine zentrale Öffnung in der Gehäusetrennwand. Die Antriebskammer ist in der unteren Kammer aufgenommen und gegenüber dem in die untere Kammer einströmenden Öl-Gas-Gemisch abgetrennt. Um eine gewünschte Ansaugwirkung an der Öffnung der Gehäusetrennwand zu erreichen und auf diese Weise das Öl-Gas-Gemisch in die Abscheiderkammer der Trennvorrichtung zu befördern, darf der Zwischenraum zwischen der Trennwand und der zugewandten Endwand der Trennvorrichtung nicht zu groß sein. Aus diesem Grunde kann an dieser Stelle zusätzlich eine Labyrinthdichtung vorgesehen sein, was jedoch bei einer bedarfsgerechten Dimensionierung des Zwischenspaltes zwischen Trennwand und zugewandter Endwand der Trennvorrichtung nicht nötig und nicht wünschenswert ist, da die Zuführung des Öl-Gas-Gemischs dadurch behindert werden kann.Another separator is off US 2004/0107681 A1 known. Also in this prior art, the centrifugal rotor is driven by a turbine wheel with an oil jet. However, the turbine wheel is provided directly in the separator chamber, so that the oil droplets which are formed on the turbine wheel when the oil jet impinges additionally contaminate the oil-gas mixture to be cleaned. Out WO 03/061838 Furthermore, a separating device is known, in which a sealing means, such as a labyrinth seal, can be provided. The device is received in the upper chamber of a housing divided into two by a partition wall. The oil-gas mixture is supplied via an opening in the lower chamber of the housing and passes through the upper chamber and the separator via a central opening in the housing bulkhead. The drive chamber is accommodated in the lower chamber and separated from the flowing into the lower chamber of the oil-gas mixture. In order to achieve a desired suction effect at the opening of the housing partition wall and in this way to convey the oil-gas mixture into the separator chamber of the separator, the gap between the partition wall and the facing end wall of the separator must not be too large. For this reason, in addition, a labyrinth seal may be provided at this point, but this is not necessary and not desirable for a needs-based dimensioning of the intermediate gap between partition and facing end wall of the separation device, since the supply of the oil-gas mixture can be hindered.

Schließlich zeigt das Dokument EP 0 933 507 B1 eine Trennvorrichtung, bei der der Zentrifugalrotor über einen Kettentrieb angetrieben wird.Finally, the document shows EP 0 933 507 B1 a separator in which the centrifugal rotor is driven by a chain drive.

Aufgabe und erfindungsgemäße LösungTask and solution according to the invention

Es ist Aufgabe der vorliegenden Erfindung, eine Vorrichtung der eingangs bezeichneten Art bereitzustellen, die bei einfachem und kostengünstigem Aufbau eine hinreichend fluiddichte Abdichtung zwischen Abscheiderkammer und Antriebskammer bereitstellt, jedoch einen Druckausgleich zwischen diesen Kammern ermöglicht.It is an object of the present invention to provide a device of the type described, which provides a sufficiently fluid-tight seal between the separator chamber and drive chamber with simple and inexpensive construction, but allows pressure equalization between these chambers.

Diese Aufgabe wird durch eine Vorrichtung der eingangs bezeichneten Art gelöst, bei der eine Lagerbuchse der Gehäusetrennwand einen Rohransatz aufweist, der zur Antriebskammer vorsteht und zur Realisierung der Labyrinthdichtung dient.This object is achieved by a device of the type described, in which a bearing bush of the housing partition has a pipe socket which projects to the drive chamber and serves to realize the labyrinth seal.

Es wurde nämlich erkannt, dass eine berührungslose Labyrinthdichtung ausreicht, um die in der Antriebskammer entstehenden Öltröpfchen an einem Eindringen in die Abscheiderkammer zu hindern. Der Einsatz einer berührungslosen Labyrinthdichtung hat jedoch gegenüber der im Stand der Technik gemäß WO 2004/091799 A1 beschriebenen Lösung den Vorteil, dass in Betriebszuständen hohen Drucks in der Abscheiderkammer ein Druckausgleich zwischen Antriebskammer und Abscheiderkammer durch den Spalt der Labyrinthdichtung erfolgen kann. So kommt es nicht zu einem unerwünschten "Blockieren" der Öl-Austrittsöffnung, so dass weiterhin auch während des Druckausgleichs Öl aus der Abscheiderkammer abströmen kann. In der Folge lässt sich ein zuverlässigerer Betrieb der erfindungsgemäßen Vorrichtung gegenüber dem Stand der Technik erreichen.It has been recognized that a non-contact labyrinth seal is sufficient to prevent the resulting oil droplets in the drive chamber from penetrating into the deposition chamber. However, the use of a non-contact labyrinth seal has over that in the prior art according to WO 2004/091799 A1 described solution has the advantage that in operating conditions of high pressure in the separator chamber pressure equalization between the drive chamber and the separator chamber can be done through the gap of the labyrinth seal. Thus, there is no undesirable "blocking" of the oil outlet opening, so that continue to flow out of the separator chamber during pressure equalization. As a result, a more reliable operation of the device according to the invention over the prior art can be achieved.

Bei einer vorteilhaften Ausführungsform der Erfindung ist vorgesehen, dass in der Lagerbuchse der Gehäusetrennwand ein Lager, insbesondere ein Kugellager, zum Lagern der Rotorwelle aufgenommen ist. In diesem Zusammenhang kann ferner vorgesehen sein, dass die Lagerbuchse in der Gehäusetrennwand integriert ist.In an advantageous embodiment of the invention it is provided that a bearing, in particular a ball bearing, is accommodated for supporting the rotor shaft in the bearing bush of the housing partition wall. In this context, it may further be provided that the bearing bush is integrated in the housing partition.

Der Rohransatz wird in vorteilhafter Weise zur Realisierung der Labyrinthdichtung genutzt. So sieht eine Weiterbildung der Erfindung vor, dass die Labyrinthdichtung eine Dichtscheibe mit einer umlaufenden Axialnut aufweist und dass ein freies Ende des Rohransatzes in die Axialnut, vorzugsweise berührungsfrei, eingreift. Ferner kann bei dieser Ausführungsvariante der Erfindung vorgesehen sein, dass die Dichtscheibe mit der Rotorwelle drehgekoppelt ist. Die Labyrinthdichtung ist somit bei dieser Ausführungsform der Erfindung zwischen dem gehäusefesten Rohransatz und der sich drehenden Rotorwelle ausgebildet. Die Erfindung vermeidet also eine Abdichtung von sich im Betrieb zueinander drehenden Teilen mit einer für Verschleiß anfälligen Berührungsdichtung.The pipe socket is used advantageously for the realization of the labyrinth seal. Thus, a further development of the invention that the labyrinth seal has a sealing disc with a circumferential axial groove and that a free end of the pipe socket in the axial groove, preferably non-contact, engages. Furthermore, it can be provided in this embodiment of the invention that the sealing disc is rotationally coupled to the rotor shaft. The labyrinth seal is thus formed in this embodiment of the invention between the housing-fixed pipe socket and the rotating rotor shaft. The invention thus avoids sealing parts that rotate with one another in operation with a contact seal that is prone to wear.

Eine Ausführungsform der Erfindung sieht vor, dass die Antriebseinrichtung ein fluidisch antreibbares Antriebsrad, vorzugsweise ein fluidisch beaufschlagtes Turbinenrad, aufweist, das drehfest auf der Rotorwelle angebracht und mit der Dichtscheibe gekoppelt ist.An embodiment of the invention provides that the drive device has a drive wheel which can be driven fluidly, preferably a fluidically impinged turbine wheel, which is mounted in a rotationally fixed manner on the rotor shaft and coupled to the sealing disk.

Bei Verwendung eines Antriebsrads sieht eine Weiterbildung der Erfindung vor, dass die Dichtscheibe zwischen Antriebsrad und Lager angeordnet ist. Bei dieser konstruktiven Ausführungsform der Erfindung kann ferner vorgesehen sein, dass die Dichtscheibe einen Radialbereich größerer Dicke aufweist, der einen Innenring des Lagers kontaktiert. Dadurch lässt sich die Dichtscheibe zugleich zum Verspannen des Lagers einsetzen.When using a drive wheel, a development of the invention provides that the sealing washer between the drive wheel and bearing is arranged. In this constructive embodiment of the invention can also be provided that the sealing disc has a radial region of greater thickness, which contacts an inner ring of the bearing. As a result, the sealing disc can be used at the same time for bracing the bearing.

Die Erfindung betrifft ferner eine Dichtungsanordnung bei einer Vorrichtung der vorstehend beschriebenen Art, umfassend eine Labyrinthdichtung, die berührungslos die Abscheiderkammer von der Antriebskammer abdichtet.The invention further relates to a sealing arrangement in a device of the type described above, comprising a labyrinth seal which seals non-contact the separator chamber of the drive chamber.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die Erfindung wird im Folgenden beispielhaft anhand der beiliegenden Figuren erläutert. Es stellen dar:

Fig. 1
einen achsenthaltenden Schnitt einer erfindungsgemäßen Vorrichtung;
Fig. 2
eine vergrößerte Darstellung des in Fig. 1 mit II bezeichneten Bereichs und
Fig. 3
einen Querschnitt durch eine erfindungsgemäße Dichtungsscheibe.
The invention is explained below by way of example with reference to the accompanying figures. They show:
Fig. 1
an axis-containing section of a device according to the invention;
Fig. 2
an enlarged view of the in Fig. 1 with II designated area and
Fig. 3
a cross section through a sealing washer according to the invention.

Beschreibung eines erfindungsgemäßen AusführungsbeispielsDescription of an embodiment according to the invention

In Fig. 1 ist eine erfindungsgemäße Zentrifugal-Trennvorrichtung in einem die Längsachse A enthaltenden Schnitt gezeigt und allgemein mit 10 bezeichnet. Die Trennvorrichtung 10 umfasst ein Gehäuse 12, das eine Abscheiderkammer 14 umschließt. Das Gehäuse 12 ist nach unten offen ausgebildet und durch eine bodenseitige Gehäusetrennwand 16 verschlossen. Im oberen Bereich ist das Gehäuse mit einem Einlassstutzen 18 versehen, der einen in die Abscheiderkammer 14 einmündenden Einlass 20 definiert. In seinem unteren Bereich besitzt das Gehäuse 12 ferner einen nicht gezeigten Auslass. Nahe dem Einlass 20 weist das Gehäuse 12 Haltestege 22 und 24 auf, die einen Lagertopf 26 aufnehmen und in dem Gehäuse 12 halten. Der Lagertopf 26 ist gestuft ausgebildet und umfasst Durchbrüche 28, so dass der die Einlass 20 mit der Abscheiderkammer 14 fluidisch verbunden ist.In Fig. 1 a centrifugal separating device according to the invention is shown in a section containing the longitudinal axis A and generally designated 10. The separator 10 includes a housing 12 enclosing a separator chamber 14. The housing 12 is formed open at the bottom and closed by a bottom-side housing partition 16. In the upper area, the housing is provided with an inlet nozzle 18, which defines an inlet 20 opening into the separator chamber 14. In its lower region, the housing 12 further has an outlet, not shown. Near the inlet 20, the housing 12 holding webs 22 and 24 which receive a bearing cup 26 and hold in the housing 12. The bearing cup 26 is stepped and includes apertures 28 such that the inlet 20 is fluidly connected to the separator chamber 14.

In dem Lagertopf 26 ist ein Kugellager 30 mit seinem Außenring drehfest aufgenommen. Der Innenring des Kugellagers 30 ist auf eine Rotorwelle 32 aufgepresst. Die Rotorwelle 32 ist ferner über ein weiteres Kugellager 34 in der Gehäusetrennwand 16 gelagert. Hierzu weist die Gehäusetrennwand 16 einen zentralen Durchbruch auf, der von einem integral ausgebildeten rohrförmigen Ansatz 36 umgeben ist. Das Kugellager 34 ist mit seinem Außenring in die Innenumfangsfläche des Rohransatzes 36 eingepresst und wird am unteren Ende durch eine Durchmesserverengung an dem Ansatz 36 gehalten. Der Innenring des Kugellagers 34 sitzt hingegen auf der Rotorwelle 32.In the bearing cup 26, a ball bearing 30 is rotatably received with its outer ring. The inner ring of the ball bearing 30 is pressed onto a rotor shaft 32. The rotor shaft 32 is also mounted via a further ball bearing 34 in the housing partition 16. For this purpose, the housing partition 16 has a central opening which is surrounded by an integrally formed tubular extension 36. The ball bearing 34 is pressed with its outer ring in the inner peripheral surface of the pipe socket 36 and is held at the lower end by a diameter constriction on the neck 36. The inner ring of the ball bearing 34, however, sits on the rotor shaft 32nd

Zwischen den beiden Kugellagern 30 und 34 sind auf der Rotorwelle 32 mehrere kegelstumpfförmige Abscheiderbleche 38 in regelmäßigen Abständen angeordnet und drehfest angebracht. Auch die Abscheiderbleche 38 weisen in ihrem horizontal verlaufenden zentralen Bereich jeweils Durchbrüche 40 auf. Die Rotorwelle 32 und die Abscheiderbleche 38 bilden zusammen einen Zentrifugalrotor 39.Between the two ball bearings 30 and 34, a plurality of frustoconical Abscheiderbleche 38 are arranged at regular intervals and rotatably mounted on the rotor shaft 32. The separator plates 38 also have openings 40 in their horizontally extending central area. The rotor shaft 32 and the separator plates 38 together form a centrifugal rotor 39.

In dem Gehäuse 12 ist ferner ein Bodenteil 42 mit einem darin integral ausgebildeten Sammelkanal 44 angeordnet. Der Sammelkanal 44 wird radial innenseitig von einer an dem Trichterboden 42 angeformten umlaufenden Kanalwand 46 begrenzt. Zwischen dem Bodenteil 42 und der Gehäusetrennwand 16 bildet sich so ein Ölsammelbecken 48 aus. Der Sammelkanal 44 ist über in Umfangsrichtung gleichmäßig verteilte bodenseitige Ablaufschlitze 50 mit dem Ölsammelbecken 48 verbunden. In dem Ölsammelbecken 48 ist eine Abströmöffnung 52 zur Ölableitung vorgesehen.In the housing 12, a bottom part 42 is further arranged with a collecting channel 44 integrally formed therein. The collecting channel 44 is bounded radially on the inside by a circumferential channel wall 46 formed on the funnel bottom 42. Between the bottom part 42 and the housing partition wall 16 so an oil sump 48 is formed. The collecting duct 44 is connected to the oil collecting basin 48 via bottom-side drainage slots 50, which are distributed uniformly in the circumferential direction. In the oil collection basin 48, a discharge opening 52 is provided for oil discharge.

Unterhalb der Gehäusetrennwand 16 ist eine Antriebskammer 60 angeordnet, die nur teilweise gezeigt ist. Die Rotorwelle 16 erstreckt sich durch den Rohransatz 36 in die Antriebskammer 60. An ihrem freien Ende 62 ist ein als Turbinenrad 64 ausgebildetes Antriebsrad drehfest angebracht. Das Turbinenrad 64 weist an seinem oberen Ende Turbinenschaufeln 66 auf, die über eine in Fig. 1 und 2 nicht gezeigte Düse mit einem Ölstrahl beaufschlagt werden können, so dass das auf die Turbinenschaufeln 66 treffende Öl das Turbinenrad 64 und damit die Rotorwelle 16 samt der daran angebrachten Abscheiderbleche 38 in Drehung um die Achse A versetzt. Einzelheiten der Anordnung im Bereich des unteren Kugellagers 34 gehen auch aus Fig. 2 hervor.Below the housing partition wall 16, a drive chamber 60 is arranged, which is only partially shown. The rotor shaft 16 extends through the tube extension 36 in the drive chamber 60. At its free end 62, a drive wheel designed as a turbine wheel 64 is mounted rotationally fixed. The turbine wheel 64 has at its upper end turbine blades 66, which via an in Fig. 1 and 2 No nozzle can be acted upon with an oil jet, so that the oil impinging on the turbine blades 66, the turbine wheel 64 and thus the rotor shaft 16 together with the separator plates attached thereto 38 in rotation about the axis A. Details of the arrangement in the region of the lower ball bearing 34 also go out Fig. 2 out.

In Fig. 1 und 2 erkennt man ferner, dass in dem Turbinenrad 64 an seinem oberen Ende eine Vertiefung 68 vorgesehen ist, in die eine Dichtscheibe 70 aus Stahl oder einem anderen formstabilen Material eingesetzt ist. Die Dichtscheibe 70 ist in einer Einzelteildarstellung in Fig. 3 gezeigt. Sie weist einen zentralen Durchbruch 72 auf, der von einem erhabenen Radialbereich 74 eingefasst ist. Der erhabene Radialbereich 74 dient zur Anlage an dem Innenring des Kugellagers 36. Die Unterseite der Dichtscheibe 70 ist im Wesentlichen eben ausgebildet. Ferner weist die Dichtscheibe 70 eine umlaufende Nut 76 auf, deren Breite B die Wandstärke b des unteren freien Endes des Rohransatzes 36 übersteigt. Im montierten Zustand ragt das untere freie Ende des Rohransatzes 36 berührungslos in die Nut 76 hinein, so dass sich ein labyrinthartiger Spalt zwischen dem unteren freien Endes des Rohransatzes 36 und der Nut 76 ausbildet. Die Spaltbreite liegt beispielsweise im Bereich von 0,01 mm bis 0,20 mm.In Fig. 1 and 2 can be seen further that in the turbine wheel 64 at its upper end a recess 68 is provided into which a sealing washer 70 made of steel or another dimensionally stable material is used. The sealing washer 70 is in a single part illustration in Fig. 3 shown. It has a central opening 72, which is bordered by a raised radial area 74. The raised radial region 74 serves to rest on the inner ring of the ball bearing 36. The underside of the sealing disc 70 is essentially planar. Furthermore, the sealing disc 70 has a circumferential groove 76 whose width B exceeds the wall thickness b of the lower free end of the tube extension 36. In the assembled state, the lower free end of the pipe socket 36 protrudes contactlessly into the groove 76, so that a labyrinthine gap between the lower free end of the pipe socket 36 and the groove 76 is formed. The gap width is, for example, in the range of 0.01 mm to 0.20 mm.

Im Folgenden wird die Funktionsweise der erfindungsgemäßen Vorrichtung 10 erläutert. Wie bereits angedeutet, werden die Turbinenschaufeln 66 des Turbinenrads 64 mit einem Fluid, vorzugsweise Motoröl, unter Druck angestrahlt, so dass das Turbinenrad 64 in Drehung versetzt wird und die Rotorwelle 32 antreibt. Mit der Rotorwelle 32 drehen sich die Abscheiderbleche 38. Sie versetzen die im zentralen Bereich des aus Rotorwelle 32 und Abscheiderbleche 38 bestehenden Zentrifugalrotors 39 befindliche Luft in Drehbewegung, so dass diese aufgrund der Zentrifugalwirkung nach außen strömt. Dadurch ergibt sich ein Unterdruck im zentralen Bereich und eine Ansaugwirkung (siehe Pfeil P), so dass ein Öl-Luft-Gemisch über den Einlassstutzen 18 aus einem Kurbelgehäuse eines Verbrennungsmotors angesaugt wird. Das Öl-Luft-Gemisch enthält Ölpartikel, die von der Luft abgeschieden werden sollen.The mode of operation of the device 10 according to the invention is explained below. As already indicated, the turbine blades 66 of the turbine wheel 64 are under pressure with a fluid, preferably engine oil, so that the turbine wheel 64 is rotated and drives the rotor shaft 32. The separator plates 38 rotate with the rotor shaft 32. They set the air in the central region of the centrifugal rotor 39 consisting of the rotor shaft 32 and separator plates 38 to rotate, so that it flows outwards due to the centrifugal action. This results in a negative pressure in the central region and an intake effect (see arrow P), so that an oil-air mixture is sucked in via the inlet port 18 from a crankcase of an internal combustion engine. The oil-air mixture contains oil particles that are to be separated from the air.

Das Öl-Luft-Gemisch tritt durch die Durchbrüche 28 zu den Abscheiderblechen 38 und wird dort in Drehbewegung versetzt. Ein Teil des Öl-Luft-Gemisches strömt durch die Durchbrüche 40 nach unten, der andere Teil des Öl-Luft-Gemisches bewegt sich zentrifugalkraftbedingt nach radial auswärts und trifft auf die konischen Bereiche der Abscheiderbleche 38. Dabei scheiden sich die in dem Öl-Luft-Gemisch enthaltenen Öltröpfchen von der Luft ab und bleiben an den Abscheiderblechen haften. Das abgeschiedene Öl wird durch die Zentrifugalkraft auf den Abscheiderblechen 38 nach radial auswärts gefördert und schließlich an deren radial äußerem Rand abgeschleudert, wie in Fig. 1 bei 54 gezeigt. An der Gehäuseseitenwand 56 bildet sich ein Ölfilm 58, der schwerkraftbedingt nach unten fließt und sich im Sammelkanal 44 sammelt. Von dort kann das abgeschiedene Öl über die Ablaufschlitze 50 in das Fluidsammelbecken 48 abfließen und zurück in den Ölkreislauf des Motors geführt werden. Die von den Ölpartikeln getrennte gereinigte Luft strömt über den nicht gezeigten Auslass aus der Abscheiderkammer 14 und kann an die Atmosphäre abgegeben werden.The oil-air mixture passes through the openings 28 to the separator plates 38 and is rotated there. Part of the oil-air mixture flows through the apertures 40 down, the other part of the oil-air mixture moves due to centrifugal force radially outward and impinges on the conical regions of Abscheiderbleche 38. In this case, the divide in the oil-air Mixed oil droplets from the air and stick to the separator plates. The separated oil is conveyed by the centrifugal force on the Abscheiderblechen 38 radially outwardly and finally thrown off at the radially outer edge, as in Fig. 1 shown at 54. On the side wall 56 of the housing, an oil film 58 is formed which, due to gravity, flows downwards and collects in the collecting duct 44. From there, the separated oil can flow via the drainage slots 50 into the fluid collection basin 48 and be led back into the oil circuit of the engine. The purified air separated from the oil particles flows out of the separator chamber 14 via the outlet, not shown, and can be discharged to the atmosphere.

Im Betrieb ist es unbedingt zu vermeiden, dass größere Mengen an Öl, das beim Antreiben des Turbinenrads 64 in der Antriebskammer verspritzt wird, in den Bereich des Sammelbeckens 48 oder bis in den Bereich der Abscheiderkammer 14 eintreten. Dadurch würde die Funktionsweise der Vorrichtung 10 stark beeinträchtigt werden. Zu diesem Zweck ist die Dichtscheibe 70 zur Ausbildung der Labyrinthdichtung vorgesehen. Es hat sich gezeigt, dass der erfindungsgemäße Einsatz der Dichtscheibe 70 mit der Nut 76 und eine daraus resultierende berührungslose Labyrinthdichtung erhebliche Vorteile gegenüber kontaktierenden Dichtungen aufweist, wie beispielsweise in der WO 2004/091799 A1 gezeigt. Zum einen unterliegen kontaktierende Dichtungen mit zunehmender Betriebsdauer immer größer werdendem Verschleiß, was sogar zu einem Versagen der Dichtung führen kann. Hingegen funktioniert die erfindungsgemäße Labyrinthdichtung kontaktfrei und unterliegt daher auch keinerlei reibungsbedingtem Verschleiß. Ferner kann es in bestimmten Betriebssituationen, insbesondere bei einem Hochleistungsbetrieb des Verbrennungsmotors, zu verhältnismäßig hohen Drücken oder Druckspitzen in der Abscheiderkammer kommen, die kurzfristig abgebaut werden müssen. Dabei ist ein Druckabbau über die Ablaufschlitze 50 und die Abströmöffnung 52 zu vermeiden, weil andernfalls der Ölablaufvorgang unterbrochen werden und unter Umständen zu viel Öl in der Abscheiderkammer 14 verbleiben würde. Dies hätte eine Verschlechterung der Abscheiderwirkung zur Folge. Die Erfindung bietet nun den Vorteil, dass ein Druckabbau zur Antriebskammer 60 hin über die Labyrinthdichtung zwischen der Dichtscheibe 70 und dem Rohransatz 36 erfolgen kann. Dennoch sorgt die Labyrinthdichtung für eine hinreichend gute Abdichtung der Abscheiderkammer 14 von der Antriebskammer 60, so dass in der Antriebskammer 60 vorhandene Öltröpfchen nicht in die Abscheiderkammer 14 eintreten können.In operation, it is important to avoid that larger amounts of oil splashed in the drive chamber when the turbine wheel 64 is driven enter the area of the collecting basin 48 or into the area of the separator chamber 14. As a result, the functioning of the device 10 would be severely impaired. For this purpose, the sealing washer 70 is provided for the formation of the labyrinth seal. It has been found that the inventive use of the sealing disc 70 with the groove 76 and a resulting non-contact labyrinth seal has significant advantages over contacting seals, such as in the WO 2004/091799 A1 shown. On the one hand, contact seals are subject to ever-increasing wear as the operating time increases, which can even lead to seal failure. On the other hand it works Labyrinth seal according to the invention without contact and is therefore not subject to any friction due to wear. Furthermore, in certain operating situations, in particular in a high-performance operation of the internal combustion engine, relatively high pressures or pressure peaks may occur in the separator chamber, which must be reduced in the short term. In this case, a pressure reduction via the drain slots 50 and the discharge opening 52 is to be avoided, because otherwise the oil drainage process would be interrupted and under certain circumstances too much oil would remain in the separator chamber 14. This would result in a deterioration of the separator effect. The invention now offers the advantage that a pressure reduction to the drive chamber 60 can take place via the labyrinth seal between the sealing washer 70 and the tube extension 36. Nevertheless, the labyrinth seal ensures a sufficiently good sealing of the separator chamber 14 from the drive chamber 60, so that in the drive chamber 60 existing oil droplets can not enter the separator chamber 14.

Claims (9)

  1. Apparatus (10) for purifying gas while venting a crank housing, said apparatus comprising
    - a housing (12) inside which a separator chamber (14) is provided,
    - a rotor arrangement with a rotor shaft (32) that is rotatably mounted in the housing and a centrifugal rotor (39) located in the separator chamber (14), and
    - a fluid driving device (64) for driving the rotor shaft (32) by means of a driving fluid,
    wherein the driving device (64) is disposed in a driving chamber (60) that is separated from the separator chamber (14) by means of a housing partition (16),
    wherein the rotor shaft (32) extends through an opening in the housing partition (16),
    and wherein a labyrinth-type seal (70) is provided in the zone of the opening in order to seal the driving chamber (60) from the separator chamber (14),
    characterized in that a bearing bush of the housing partition (16) has a pipe socket (36) projecting to the driving chamber (60) and serving as realization of the labyrinth-type seal (70).
  2. Apparatus (10) according to Claim 1,
    characterized in that a bearing (34), in particular a ball bearing, for carrying the rotor shaft (32) is received in the bearing bush (36) of the housing partition (16).
  3. Apparatus (10) according to Claim 2,
    characterized in that the bearing bush (36) is integrated in the housing partition (16).
  4. Apparatus (10) according to one of the preceding claims,
    characterized in that the labyrinth-type seal has a sealing washer (70) with a surrounding axial groove (76), and that a free end of the pipe socket (36) engages with the axial groove (76), preferably without contact.
  5. Apparatus (10) according to Claim 4,
    characterized in that the sealing washer (70) is connected to the rotor shaft (32) so that it can rotate.
  6. Apparatus (10) according to Claim 4 or 5,
    characterized in that the driving device has a driving wheel (64) which can be driven by fluid, preferably a turbine wheel which is struck by fluid, and which is attached to the rotor shaft in a torque-proof manner and connected to the sealing washer (70).
  7. Apparatus (10) according to Claims 2 and 6,
    characterized in that the sealing washer (70) is arranged between the driving wheel (64) and the bearing (34).
  8. Apparatus (10) according to one of Claims 4 to 7,
    characterized in that the sealing washer (70) has a radial zone (74) of greater thickness, which contacts an inner ring of the bearing (34).
  9. Apparatus according to one of the preceding claims, with a seal arrangement comprising a labyrinth-type seal which seals the separator chamber (14) from the driving chamber (60) without contact.
EP06724681.9A 2005-05-09 2006-05-02 Apparatus for the purification of gas while bleeding a crank housing Active EP1880090B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005021278A DE102005021278B4 (en) 2005-05-09 2005-05-09 Device for cleaning gas when venting a crankcase
PCT/EP2006/004098 WO2006119890A1 (en) 2005-05-09 2006-05-02 Apparatus for the purification of gas while bleeding a crank housing

Publications (2)

Publication Number Publication Date
EP1880090A1 EP1880090A1 (en) 2008-01-23
EP1880090B1 true EP1880090B1 (en) 2013-11-20

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US (1) US8172917B2 (en)
EP (1) EP1880090B1 (en)
JP (1) JP2008540908A (en)
CN (1) CN101189414B (en)
DE (1) DE102005021278B4 (en)
RU (1) RU2405945C2 (en)
WO (1) WO2006119890A1 (en)

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RU2405945C2 (en) 2010-12-10
CN101189414A (en) 2008-05-28
US20080256912A1 (en) 2008-10-23
DE102005021278A1 (en) 2006-11-16
JP2008540908A (en) 2008-11-20
US8172917B2 (en) 2012-05-08
WO2006119890A1 (en) 2006-11-16
EP1880090A1 (en) 2008-01-23
RU2007145512A (en) 2009-06-20
DE102005021278B4 (en) 2010-04-15
CN101189414B (en) 2010-05-19

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