EP2525916B1 - Drive device in a helical conveyor centrifuge - Google Patents

Drive device in a helical conveyor centrifuge Download PDF

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Publication number
EP2525916B1
EP2525916B1 EP11730245.5A EP11730245A EP2525916B1 EP 2525916 B1 EP2525916 B1 EP 2525916B1 EP 11730245 A EP11730245 A EP 11730245A EP 2525916 B1 EP2525916 B1 EP 2525916B1
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EP
European Patent Office
Prior art keywords
gearbox
drive
shaft
housing
screw
Prior art date
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Not-in-force
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EP11730245.5A
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German (de)
French (fr)
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EP2525916A2 (en
Inventor
Robert Wagenbauer
Christoph Puls
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Hiller GmbH
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Hiller GmbH
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Priority to SI201130457T priority Critical patent/SI2525916T1/en
Publication of EP2525916A2 publication Critical patent/EP2525916A2/en
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Publication of EP2525916B1 publication Critical patent/EP2525916B1/en
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    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
    • B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing

Definitions

  • the invention relates to a drive device in a screw centrifuge according to the preamble of claim 1, as this example WO-A-8912506 has become known.
  • the invention has for its object to provide a drive device for worm centrifuges, wherein the drum drive is decoupled from the worm drive and both a free-lying storage of the gear for the worm drive and an elastic rotor bearing can be avoided.
  • this object is achieved by the reproduced in the characterizing part features.
  • the advantages of this solution achieved with the invention are mainly in the stand housing, which ensures a defined support for the gear housing for the worm drive and allows instead of a flying bearing support on the foundation.
  • the hollow output shaft is not rigidly connected to the drum drive shaft, but via a coupling, which may be formed, for example, as a positive toothed coupling and which provides for a separation between the gear mass and the rotor mass. Compared to a free-floating gearbox with the risk of gear break while the safety is significantly improved.
  • the drive device according to the invention allows a lighter construction with the advantage of longer service life and lower energy consumption.
  • the transmission has a counter gear stage with a drive gear for a pinion driven by the output shaft of the worm motor, the axis of the drive gear and the output shaft of the worm motor being offset from the axis of rotation of the worm and the pinion.
  • known construction shows in longitudinal section a screw centrifuge 10 with a rotating drum 12 and a mounted therein two radial bearings 14 screw 16.
  • an electric drive motor 18 For the rotary drive of the drum 12 is an electric drive motor 18, the motor shaft via a belt drive 20, a pulley 22 is rotated , which is fixedly connected to the hollow drum drive shaft 24.
  • the drum 12 is rotatably supported on both sides in radial bearings 26.
  • a separate worm motor 28 For the rotary drive of the screw 16 is a separate worm motor 28, the output shaft 30 shown schematically coupled via a shaft coupling 32 with the input shaft 34 of a transmission 36, which sets the worm shaft 38 with a deviating from the rotor shaft differential speed in rotation.
  • the gear 36 is formed here as a planetary gear and housed in a housing 40 which is rigidly connected via a schematically indicated screw 42 with the pulley 22 and thus with the drum drive shaft 24.
  • the gear 36 is decoupled from the drum 12 characterized in that the housing 40 via two radial bearings 46 in a stand housing 44 is rotatably mounted, which is supported on a foundation 48.
  • the housing 40 of the transmission 36 has a hollow output shaft 50 (see. FIG. 2 ), which is connected via a coupling 52 with the hollow drum drive shaft 24.
  • the transmission 36 may, as shown, be a planetary gear or a four-shaft gear or a hydraulic motor.
  • the clutch 52 may be formed as a toothed coupling, for example in the form of an internally toothed sleeve which connects the externally toothed ends of the output shaft 50 of the gear 36 and the drum drive shaft 24 with each other.
  • the output shaft 30 of the worm motor 28 which is supported as the stand housing 44 on the foundation 48, coupled via a shaft coupling 32 to the input shaft 34 of the transmission 36 is in the variant of FIG. 2 the worm motor 28 is flanged to the stand housing 44.
  • the output shaft 30 of the worm motor 28 is here rotatably connected to the input shaft 34 of the transmission 36 or formed integrally therewith.
  • the pulley 22 is fixedly connected to the hollow drum drive shaft 24 mounted in the radial bearing 26, while being connected to the hollow output shaft 50 of the transmission housing 40 via the clutch 52.
  • the tensile forces of the belt drive 20 are received by the radial bearing 26.
  • the embodiments of the Figures 3 and 4 differ from those of FIGS. 1 and 2 in that the pulley 22 is fixedly connected to the hollow output shaft 50 of the transmission case 40 while being connected to the drum drive shaft 24 via the clutch 52. In this case, the tensile forces exerted by the belt drive 20 are absorbed by the radial bearings 14, 46 of the transmission 36.
  • FIG. 5 shows a further possibility for carrying out the invention in which the gear arrangement between the drive motor 18 and drum 12 consists of a spur gear 54 which is in engagement with an external toothing 56 on the housing 40 of the transmission 36.
  • the housing 58 of the spur gear 54 is fixedly connected to the stationary housing 44 or formed integrally therewith.
  • this variant offers the FIG. 5 the ability to form the drive motor 18 for the drum 12 as a flange motor and to attach to the housing 58 of the spur gear 54.
  • FIGS. 7 and 8th show as a variant of FIG. 5 another embodiment in which the transmission 36 has a counter gear 60 with two offset axes of rotation.
  • the worm motor 28 is offset by its output shaft 30, whose axis is indicated by 30 ', to the axis of rotation 38' of the worm shaft 38 and to this coaxial drum 12 by the dimension a.
  • the drum 12 is housed in a drum housing 62 (see. FIG. 7 ).
  • the counter gear stage 60 has a drive gear 70 driven by the worm motor 28 with the rotation axis 30 ', which is connected to the output shaft 30 of the worm motor 28 via the clutch 32 and which meshes with a pinion 64 of the counter gear stage 60.
  • the pinion 64 is fixedly connected to the input shaft 34 of the transmission 36.
  • the axial offset a between the two axes 30 'and 38' is used to guide through the entire gear 36 a to the axis 38 'coaxial feed tube 66 with a central access 68 for lubricant, via not shown radial bores in the feed tube 66 at the required lubrication points are distributed.
  • a targeted oil injection lubrication is made possible from the inside, whereby the frequent problems with decanters gearboxes are avoided, for.

Description

Die Erfindung betrifft eine Antriebsvorrichtung in einer Schneckenzentrifuge nach dem Oberbegriff des Anspruchs 1, wie diese beispielsweise aus WO-A-8912506 bekannt geworden ist.The invention relates to a drive device in a screw centrifuge according to the preamble of claim 1, as this example WO-A-8912506 has become known.

In herkömmlichen Antriebsvorrichtungen dieser Bauart mit außenliegendem Getriebe ist dessen Gehäuse starr mit der Rotortrommel verbunden und bildet eine große freifliegend gelagerte Masse (vgl. z. B. WO 2007/147893 ). Unwuchten des Getriebes und des Rotors wirken sich dabei äußerst nachteilig auf die Rotorlager aus und werden von diesen unmittelbar in das Fundament für die Zentrifuge übertragen.In conventional drive devices of this type with external gear whose housing is rigidly connected to the rotor drum and forms a large free-floating mounted mass (see. WO 2007/147893 ). Imbalances of the transmission and the rotor thereby have an extremely adverse effect on the rotor bearings and are transmitted by them directly into the foundation for the centrifuge.

Zur Vermeidung dieser Nachteile wurde daher schon versucht, die Trommel in elastisch aufgehängten Lagern oder in schwimmenden Lageraufhängungen zu positionieren. Derartige Lagerungen haben sich allerdings nicht durchgesetzt, weil enge Spalte zwischen der Trommel und ihrem Gehäuse nicht eingehalten werden können und überdies bei bestimmten Drehzahlen, die beim Abschalten des Antriebs durchfahren werden, Resonanzschwingungen auftreten.To avoid these disadvantages, therefore, attempts have been made to position the drum in elastically suspended bearings or in floating bearing suspensions. However, such bearings have not enforced because narrow gaps between the drum and its housing can not be met and also occur at certain speeds, which are traversed when switching off the drive, resonant vibrations.

In einer Konstruktionsvariante wurde zusätzlich eine getrennte Getriebelagerung in einem eigenen Lagerbock vorgenommen, wobei jedoch ein freifliegendes Getriebe mit langer Lagerwelle Unwuchten auf der Getriebeseite zur Folge hat (vgl. Stahl, Dekanterhandbuch, Band II, S. 408/409).In a design variant, a separate gearbox bearing was additionally made in a separate bearing block, but a free-running gearbox with long bearing shaft imbalances on the transmission side result (see Steel, Decanter Manual, Volume II, p 408/409).

Der Erfindung liegt die Aufgabe zugrunde, eine Antriebsvorrichtung für Schneckenzentrifugen anzugeben, bei der der Trommelantrieb vom Schneckenantrieb entkoppelt ist und sowohl eine freifliegende Lagerung des Getriebes für den Schneckenantrieb als auch eine elastische Rotorlagerung vermieden werden.The invention has for its object to provide a drive device for worm centrifuges, wherein the drum drive is decoupled from the worm drive and both a free-lying storage of the gear for the worm drive and an elastic rotor bearing can be avoided.

Bei einer Antriebsvorrichtung der im Anspruch 1 angegebenen Gattung wird diese Aufgabe durch die im kennzeichnenden Teil wiedergegebenen Merkmale gelöst.In a drive device of the type specified in claim 1, this object is achieved by the reproduced in the characterizing part features.

Die mit der Erfindung erzielten Vorteile dieser Lösung liegen vor allem in dem Standgehäuse, das eine definierte Lagerung für das Getriebegehäuse für den Schneckenantrieb gewährleistet und an Stelle einer fliegenden Lagerung eine Abstützung auf dem Fundament ermöglicht. Die hohle Ausgangswelle ist nicht starr mit der Trommelantriebswelle verbunden, sondern über eine Kupplung, die beispielsweise als eine formschlüssige Zahnkupplung ausgebildet sein kann und die für eine Trennung zwischen der Getriebemasse und der Rotormasse sorgt. Im Vergleich zu einem freifliegend gelagerten Getriebe mit der Gefahr von Getriebebruch wird dabei die Sicherheit erheblich verbessert.The advantages of this solution achieved with the invention are mainly in the stand housing, which ensures a defined support for the gear housing for the worm drive and allows instead of a flying bearing support on the foundation. The hollow output shaft is not rigidly connected to the drum drive shaft, but via a coupling, which may be formed, for example, as a positive toothed coupling and which provides for a separation between the gear mass and the rotor mass. Compared to a free-floating gearbox with the risk of gear break while the safety is significantly improved.

Gegenüber dem bekannten Stand der Technik erlaubt die erfindungsgemäß ausgebildete Antriebsvorrichtung eine leichtere Bauweise mit dem Vorteil höherer Standzeiten und geringerem Energiebedarf.Compared to the known prior art, the drive device according to the invention allows a lighter construction with the advantage of longer service life and lower energy consumption.

In einer vorteilhaften Ausführungsform hat das Getriebe eine Vorgelege-Getriebestufe mit einem von der Ausgangswelle des Schneckenmotors angetriebenen Antriebszahnrad für ein Ritzel, wobei die Achse des Antriebszahnrads und der Ausgangswelle des Schneckenmotors zur Drehachse der Schnecke und des Ritzels versetzt ist. Damit ist es möglich, koaxial zur Drehachse der Schnecke ein Schmiermittel-Zuführrohr durch die Vorgelege-Getriebestufe zu führen.In an advantageous embodiment, the transmission has a counter gear stage with a drive gear for a pinion driven by the output shaft of the worm motor, the axis of the drive gear and the output shaft of the worm motor being offset from the axis of rotation of the worm and the pinion. This makes it possible to guide a lubricant supply pipe coaxially to the axis of rotation of the screw through the countershaft gear stage.

Weitere Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen und aus der nachfolgenden Beschreibung von Ausführungsbeispielen, die in der Zeichnung schematisch dargestellt sind. Es zeigen:

Figur 1
einen Längsschnitt durch ein erstes Ausführungsbeispiel,
Figur 2
eine Variante der Figur 1,
Figur 3
eine weitere Variante der Figur 1,
Figur 4
eine Variante der Figur 3,
Figur 5
ein nochmals abgeändertes Ausführungsbeispiel,
Figur 6
eine Variante der Figur 5 und
Figur 7
die Ansicht einer abgewandelten Ausführungsform,
Figur 8
die Schnittdarstellung der Variante der Figur 7 und
Figur 9
einen Längsschnitt durch eine Konstruktion des Standes der Technik.
Further features and advantages of the invention will become apparent from the dependent claims and from the following description of exemplary embodiments, which are shown schematically in the drawing. Show it:
FIG. 1
a longitudinal section through a first embodiment,
FIG. 2
a variant of FIG. 1 .
FIG. 3
another variant of FIG. 1 .
FIG. 4
a variant of FIG. 3 .
FIG. 5
a further modified embodiment,
FIG. 6
a variant of FIG. 5 and
FIG. 7
the view of a modified embodiment,
FIG. 8
the sectional view of the variant of FIG. 7 and
FIG. 9
a longitudinal section through a construction of the prior art.

Die in Figur 9 dargestellte, bekannte Konstruktion zeigt im Längsschnitt eine Schneckenzentrifuge 10 mit einer umlaufenden Trommel 12 und einer darin über zwei Radiallager 14 gelagerten Schnecke 16. Für den Drehantrieb der Trommel 12 dient ein elektrischer Antriebsmotor 18, dessen Motorwelle über einen Riementrieb 20 eine Riemenscheibe 22 in Drehung versetzt, die fest mit der hohlen Trommelantriebswelle 24 verbunden ist. Die Trommel 12 ist auf beiden Seiten in Radiallagern 26 drehbar abgestützt.In the FIG. 9 shown, known construction shows in longitudinal section a screw centrifuge 10 with a rotating drum 12 and a mounted therein two radial bearings 14 screw 16. For the rotary drive of the drum 12 is an electric drive motor 18, the motor shaft via a belt drive 20, a pulley 22 is rotated , which is fixedly connected to the hollow drum drive shaft 24. The drum 12 is rotatably supported on both sides in radial bearings 26.

Für den Drehantrieb der Schnecke 16 dient ein eigener Schneckenmotor 28, dessen schematisch dargestellte Ausgangswelle 30 über eine Wellenkupplung 32 mit der Eingangswelle 34 eines Getriebes 36 gekoppelt ist, das die Schneckenwelle 38 mit einer von der Rotorwelle abweichenden Differenzdrehzahl in Drehung versetzt. Das Getriebe 36 ist hier als Planetengetriebe ausgebildet und in einem Gehäuse 40 untergebracht, das über eine schematisch angedeutete Verschraubung 42 starr mit der Riemenscheibe 22 und damit mit der Trommelantriebswelle 24 verbunden ist.For the rotary drive of the screw 16 is a separate worm motor 28, the output shaft 30 shown schematically coupled via a shaft coupling 32 with the input shaft 34 of a transmission 36, which sets the worm shaft 38 with a deviating from the rotor shaft differential speed in rotation. The gear 36 is formed here as a planetary gear and housed in a housing 40 which is rigidly connected via a schematically indicated screw 42 with the pulley 22 and thus with the drum drive shaft 24.

Wie im ersten Ausführungsbeispiel der Erfindung gemäß Figur 1 dargestellt, ist das Getriebe 36 von der Trommel 12 dadurch entkoppelt, dass dessen Gehäuse 40 über zwei Radiallager 46 in einem Standgehäuse 44 drehbar gelagert ist, das sich auf einem Fundament 48 abstützt. Das Gehäuse 40 des Getriebes 36 hat eine hohle Ausgangswelle 50 (vgl. Figur 2), die über eine Kupplung 52 mit der hohlen Trommelantriebswelle 24 verbunden ist.As in the first embodiment of the invention according to FIG. 1 shown, the gear 36 is decoupled from the drum 12 characterized in that the housing 40 via two radial bearings 46 in a stand housing 44 is rotatably mounted, which is supported on a foundation 48. The housing 40 of the transmission 36 has a hollow output shaft 50 (see. FIG. 2 ), which is connected via a coupling 52 with the hollow drum drive shaft 24.

Das Getriebe 36 kann, wie dargestellt, ein Planetengetriebe oder auch ein Vierwellengetriebe oder ein Hydraulikmotor sein.The transmission 36 may, as shown, be a planetary gear or a four-shaft gear or a hydraulic motor.

Die Kupplung 52 kann als Zahnkupplung ausgebildet sein, beispielsweise in Form einer innen verzahnten Hülse, welche die außen verzahnten Enden der Ausgangswelle 50 des Getriebes 36 und der Trommelantriebswelle 24 miteinander verbindet.The clutch 52 may be formed as a toothed coupling, for example in the form of an internally toothed sleeve which connects the externally toothed ends of the output shaft 50 of the gear 36 and the drum drive shaft 24 with each other.

Während im Beispiel der Figur 1 die Ausgangswelle 30 des Schneckenmotors 28, der sich wie das Standgehäuse 44 auf dem Fundament 48 abstützt, über eine Wellenkupplung 32 mit der Eingangswelle 34 des Getriebes 36 gekoppelt ist, ist in der Variante der Figur 2 der Schneckenmotor 28 an das Standgehäuse 44 angeflanscht. Die Ausgangswelle 30 des Schneckenmotors 28 ist hier drehfest mit der Eingangswelle 34 des Getriebes 36 verbunden oder einstückig mit dieser ausgebildet.While in the example of the FIG. 1 the output shaft 30 of the worm motor 28, which is supported as the stand housing 44 on the foundation 48, coupled via a shaft coupling 32 to the input shaft 34 of the transmission 36 is in the variant of FIG. 2 the worm motor 28 is flanged to the stand housing 44. The output shaft 30 of the worm motor 28 is here rotatably connected to the input shaft 34 of the transmission 36 or formed integrally therewith.

Im Ausführungsbeispiel der Figuren 1 und 2 ist die Riemenscheibe 22 mit der im Radiallager 26 gelagerten, hohlen Trommelantriebswelle 24 fest verbunden, während sie mit der hohlen Ausgangswelle 50 des Getriebegehäuse 40 über die Kupplung 52 verbunden ist. Damit werden die Zugkräfte des Riementriebs 20 von dem Radiallager 26 aufgenommen.In the embodiment of FIGS. 1 and 2 the pulley 22 is fixedly connected to the hollow drum drive shaft 24 mounted in the radial bearing 26, while being connected to the hollow output shaft 50 of the transmission housing 40 via the clutch 52. Thus, the tensile forces of the belt drive 20 are received by the radial bearing 26.

Die Ausführungsbeispiele der Figuren 3 und 4 unterscheiden sich von denen der Figuren 1 und 2 dadurch, dass die Riemenscheibe 22 mit der hohlen Ausgangswelle 50 des Getriebegehäuses 40 fest verbunden ist, während sie mit der Trommelantriebswelle 24 über die Kupplung 52 verbunden ist. In diesem Fall werden die vom Riementrieb 20 ausgeübten Zugkräfte von den Radiallagern 14, 46 des Getriebes 36 aufgenommen.The embodiments of the Figures 3 and 4 differ from those of FIGS. 1 and 2 in that the pulley 22 is fixedly connected to the hollow output shaft 50 of the transmission case 40 while being connected to the drum drive shaft 24 via the clutch 52. In this case, the tensile forces exerted by the belt drive 20 are absorbed by the radial bearings 14, 46 of the transmission 36.

Figur 5 zeigt eine weitere Möglichkeit zur Ausführung der Erfindung bei der die Getriebeanordnung zwischen Antriebsmotor 18 und Trommel 12 aus einem Stirnradgetriebe 54 besteht, das mit einer Außenverzahnung 56 am Gehäuse 40 des Getriebes 36 in Eingriff ist. Hier ist zudem das Gehäuse 58 des Stirnradgetriebes 54 fest mit dem Standgehäuse 44 verbunden oder einstückig mit diesem ausgebildet. FIG. 5 shows a further possibility for carrying out the invention in which the gear arrangement between the drive motor 18 and drum 12 consists of a spur gear 54 which is in engagement with an external toothing 56 on the housing 40 of the transmission 36. Here In addition, the housing 58 of the spur gear 54 is fixedly connected to the stationary housing 44 or formed integrally therewith.

Wie Figur 6 zeigt, bietet diese Variante der Figur 5 die Möglichkeit, den Antriebsmotor 18 für die Trommel 12 als Flanschmotor auszubilden und an dem Gehäuse 58 des Stirnradgetriebes 54 anzubringen.As FIG. 6 shows, this variant offers the FIG. 5 the ability to form the drive motor 18 for the drum 12 as a flange motor and to attach to the housing 58 of the spur gear 54.

Die Figuren 7 und 8 zeigen als Variante der Figur 5 eine weitere Ausführungsform, bei der das Getriebe 36 eine Vorgelege-Getriebestufe 60 mit zwei zueinander versetzten Drehachsen hat. Der Schneckenmotor 28 ist mit seiner Ausgangswelle 30, deren Achse mit 30' angedeutet ist, zur Drehachse 38' der Schneckenwelle 38 und der zu dieser koaxialen Trommel 12 um das Maß a versetzt. Die Trommel 12 ist in einem Trommelgehäuse 62 untergebracht (vgl. Figur 7).The FIGS. 7 and 8th show as a variant of FIG. 5 another embodiment in which the transmission 36 has a counter gear 60 with two offset axes of rotation. The worm motor 28 is offset by its output shaft 30, whose axis is indicated by 30 ', to the axis of rotation 38' of the worm shaft 38 and to this coaxial drum 12 by the dimension a. The drum 12 is housed in a drum housing 62 (see. FIG. 7 ).

Die Vorgelege-Getriebestufe 60 hat ein vom Schneckenmotor 28 angetriebenes Antriebszahnrad 70 mit der Drehachse 30', das mit der Ausgangswelle 30 des Schneckenmotors 28 über die Kupplung 32 verbunden ist und das mit einem Ritzel 64 der Vorgelege-Getriebestufe 60 kämmt. Das Ritzel 64 ist mit der Eingangswelle 34 des Getriebes 36 fest verbunden.The counter gear stage 60 has a drive gear 70 driven by the worm motor 28 with the rotation axis 30 ', which is connected to the output shaft 30 of the worm motor 28 via the clutch 32 and which meshes with a pinion 64 of the counter gear stage 60. The pinion 64 is fixedly connected to the input shaft 34 of the transmission 36.

Der Achsversatz a zwischen den beiden Achsen 30' und 38' wird dazu genutzt, durch das gesamte Getriebe 36 ein zur Achse 38' koaxiales Zuführrohr 66 mit einem zentrischen Zugang 68 für Schmiermittel zu führen, das über nicht weiter dargestellte radiale Bohrungen im Zuführrohr 66 an die erforderlichen Schmierstellen verteilt wird. Damit wird eine gezielte Öleinspritzschmierung von innen ermöglicht, wodurch die bei Dekantergetrieben häufigen Probleme vermieden werden, z. B. Planschverluste bei üblichen Sumpfschmierungen.The axial offset a between the two axes 30 'and 38' is used to guide through the entire gear 36 a to the axis 38 'coaxial feed tube 66 with a central access 68 for lubricant, via not shown radial bores in the feed tube 66 at the required lubrication points are distributed. Thus, a targeted oil injection lubrication is made possible from the inside, whereby the frequent problems with decanters gearboxes are avoided, for. B. Splash losses in conventional sump lubrication.

Claims (12)

  1. Drive apparatus in a helical conveyor centrifuge comprising a rotating drum (12), a screw (16) mounted coaxially therein, a drive motor (18) associated with the drum (12) and a screw motor (28) coupled to the screw shaft (38) via a gearbox (36) whose housing (40) is nonrotatably connected to the drum drive shaft (24), characterized in that the housing (40) of said gearbox (36) for driving the screw (16) is rotatably mounted in a stationary housing (44) and has a hollow output shaft (50) that is connected via a coupling (52) to the hollow drum drive shaft (24).
  2. Drive apparatus according to claim 1, wherein the output shaft (30) of the screw motor (28) is connected to the input shaft (34) of the gearbox (36) via a shaft coupling (32).
  3. Drive apparatus according to claim 1, wherein the screw motor (28) is emobodied as a flange motor, which is flange-mounted onto the stationary housing (44) and whose output shaft (30) is nonrotatably connected to the input shaft (34) of the gearbox (36).
  4. Drive apparatus according to one of the preceding claims, wherein the drive motor (18) is connected via a gearbox arrangement to the drum (12).
  5. Drive apparatus according to claim 4, wherein the gearbox arrangement comprises a belt drive (20) having a belt pulley (22) attached between the hollow drum drive shaft (24) and the hollow output shaft (50) of the gearbox housing (40).
  6. Drive apparatus according to claim 5, wherein the belt pulley (22) is firmly connected to the hollow drum drive shaft (24) that is mounted in a radial bearing (26), while it is connected via the coupling (52) to the hollow output shaft (50) of the gearbox housing (40).
  7. Drive apparatus according to claim 5, wherein the belt pulley (22) is connected via the coupling (52) to the hollow drum drive shaft (24) mounted in a radial bearing (26), while it is fixedly connected to the hollow output shaft (50) of the gearbox housing (40).
  8. Drive apparatus according to claim 4, wherein the gearbox arrangement is made up of a spur gearbox (54) that is in engagement with an external tooth set (56) of the housing (40) for the screw drive.
  9. Drive apparatus according to claim 8, wherein the housing (58) of the spur gearbox (54) is connected fixedly to the stationary housing (44).
  10. Drive apparatus according to one of the preceding claims, wherein the gearbox (36) has an intermediate gearbox stage (60) having a drive gear (70), driven by the output shaft (30) of the screw motor (28), that meshes with a pinion (64) of the gearbox (36), the axis (30') of the drive gear (70) and of the output shaft (30) of the screw motor (28) being offset with respect to the rotation axis (38') of the screw (16) and of the pinion (64).
  11. Drive apparatus according to claim 10, wherein a lubricant delivery tube (66) passes trough the intermediate gearbox stage (60) coaxially with the rotation axis (38') of the screw (16).
  12. Drive apparatus according to one of the preceding claims, wherein the coupling (52) is embodied as a toothed coupling.
EP11730245.5A 2010-09-13 2011-06-14 Drive device in a helical conveyor centrifuge Not-in-force EP2525916B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI201130457T SI2525916T1 (en) 2010-09-13 2011-06-14 Drive device in a helical conveyor centrifuge

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010037488 2010-09-13
PCT/EP2011/059815 WO2012034722A2 (en) 2010-09-13 2011-06-14 Drive device in a helical conveyor centrifuge

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EP2525916A2 EP2525916A2 (en) 2012-11-28
EP2525916B1 true EP2525916B1 (en) 2015-01-21

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US (1) US8808154B2 (en)
EP (1) EP2525916B1 (en)
JP (1) JP5858546B2 (en)
CN (1) CN103221140B (en)
BR (1) BR112013005351A2 (en)
CA (1) CA2810450A1 (en)
DE (1) DE102011051037A1 (en)
DK (1) DK2525916T3 (en)
ES (1) ES2532538T3 (en)
PT (1) PT2525916E (en)
RU (1) RU2544703C2 (en)
SI (1) SI2525916T1 (en)
WO (1) WO2012034722A2 (en)

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BR112013005351A2 (en) 2016-08-30
US20130231235A1 (en) 2013-09-05
JP5858546B2 (en) 2016-02-10
SI2525916T1 (en) 2015-05-29
JP2013537102A (en) 2013-09-30
DK2525916T3 (en) 2015-03-02
CA2810450A1 (en) 2012-03-22
ES2532538T3 (en) 2015-03-27
PT2525916E (en) 2016-01-07
US8808154B2 (en) 2014-08-19
WO2012034722A2 (en) 2012-03-22
WO2012034722A3 (en) 2012-05-18
DE102011051037A1 (en) 2012-03-15
CN103221140A (en) 2013-07-24
RU2544703C2 (en) 2015-03-20
RU2013116897A (en) 2014-10-20
EP2525916A2 (en) 2012-11-28
CN103221140B (en) 2015-05-20

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