EP2063998A1 - Centrifuge having a rotor having horizontal axis of rotation - Google Patents

Centrifuge having a rotor having horizontal axis of rotation

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Publication number
EP2063998A1
EP2063998A1 EP07820074A EP07820074A EP2063998A1 EP 2063998 A1 EP2063998 A1 EP 2063998A1 EP 07820074 A EP07820074 A EP 07820074A EP 07820074 A EP07820074 A EP 07820074A EP 2063998 A1 EP2063998 A1 EP 2063998A1
Authority
EP
European Patent Office
Prior art keywords
drum
centrifuge according
spring
screw centrifuge
spring elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07820074A
Other languages
German (de)
French (fr)
Other versions
EP2063998B1 (en
Inventor
Martin Overberg
Stefanos Doudis
Stefan Terholsen
Helmut Figgener
Hans-Joachim Beyer
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.)
GEA Mechanical Equipment GmbH
Original Assignee
GEA Westfalia Separator GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GEA Westfalia Separator GmbH filed Critical GEA Westfalia Separator GmbH
Publication of EP2063998A1 publication Critical patent/EP2063998A1/en
Application granted granted Critical
Publication of EP2063998B1 publication Critical patent/EP2063998B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • B04B9/12—Suspending rotary bowls ; Bearings; Packings for bearings

Definitions

  • the invention relates to a screw centrifuge according to the preamble of claim 1.
  • WO 94/07605 shows a similar construction as the above-mentioned writings, but only one axial end of the drum is supported sprung.
  • An elongated centrifuge with a device for the reduction of structure-borne sound transmission shows the DE 43 15 694 Al.
  • the technological background is still the DE 26 32 586 Al, US 2,094,058, US 4,640,770 and DE 711 095 C called.
  • the invention has over this prior art, the task of creating an improved resilient support of the drum - or the entire rotor with the drum - for a centrifuge of the generic type.
  • the suitability should be suitable for elongated constructions in which the ratio between the length of the rotor and the diameter of the rotor is greater than 2.
  • the spring elements are aligned vertically or substantially vertically.
  • the support is carried out with combined spring / damping elements or with spring elements and these separate damping elements.
  • the drum or the entire rotor is resiliently supported with the drum without narrow gaps exist between the relatively movable parts in the region of the resilient support, which make the system relatively difficult to control.
  • Such a centrifuge with a horizontal axis of rotation is created, which has an optimized resilient mounting of the rotor, so that there is an optimized behavior during operation.
  • the invention is particularly suitable for elongated constructions in which the ratio between the length of the rotor or the drum and the diameter the rotor or the drum is preferably greater than 2, preferably greater than 2.5, in particular greater than 3.
  • Rotoreigenfrequenzen which can limit the possible operating speed are shifted by the decoupling of the frame or foundation mass to higher frequencies. This makes it possible to raise the operating speed significantly.
  • the spring elements preferably also have appreciable damping properties in addition to spring properties or because damping elements are provided in addition to the supporting spring elements, there is the possibility of a targeted damping of the oscillatory rotor system, which offers some further advantages.
  • the inventive design makes it possible to operate the screw centrifuge supercritically with respect to the first rotor natural frequencies at very high speed, so that the operating speed above the first resonant frequency of the rotor or the rotor parts (drum and screw) may be.
  • the gaps between the drum and the catcher can even be reduced with respect to the solutions previously proposed for supercritical operation without or with little damping. As the gaps are reduced, their sealing is also simplified.
  • the spring and damping elements preferably have frequency dependent, non-constant characteristics such that minimization of the displacement paths, i. the ways that the rotor is deflected at resonance frequencies with respect to the foundation or the machine frame, is possible.
  • this liquid of the screw centrifuge can also stimulate oscillation, especially in partial fillings on startup and shutdown.
  • suspension and damping can also be achieved that the rotor is not excited to excite from the outside inadmissible to vibrate.
  • the damping is speed and travel-dependent and designed such that at low speeds when passing through the rotor natural frequencies already present a high attenuation, while prevails at the operating speed above the resonant frequency, a relatively low attenuation. As a result, the deflections are effectively limited when driving through the natural frequency.
  • the damping should be at least 3%, particularly good results are achieved at attenuations between 10% and 30%.
  • damping is understood the conversion of the vibrational energy in another form of energy, eg heat.
  • the energy conversion causes the amplitudes to be reduced in the range of the resonance frequency.
  • the percentages of attenuation are to be understood in the sense of Lehr 's attenuation measure D:
  • the low damping causes small dynamic bearing forces, which makes a long bearing life possible.
  • the system is tuned such that the resonance frequency is achieved at a speed which is less than 70% of the operating speed, preferably less than half the operating speed.
  • a screw centrifuge in particular with a solid casing, can be realized, with which a particularly high operating speed can be driven.
  • Operating speed is a relatively quiet-working screw centrifuge is created, since the body sound entry is reduced or is particularly low, because it is done by the rotating system no direct unattenuated structure-borne sound transmission to a housing or a frame.
  • the housing of the screw centrifuge is particularly compact, if the screw centrifuge is designed according to the invention.
  • FIG. 1 is a side view of a schematically illustrated solid bowl screw centrifuge
  • FIG. 2 shows a view, rotated by 90 ° with respect to FIG. 1, of the region of a bearing device of the screw centrifuge from FIG. 1;
  • FIG. 3 shows a view similar to FIG. 2 of a further embodiment of the region of a bearing device of a solid bowl screw centrifuge.
  • FIG. 1 shows a solid-bowl screw centrifuge with a housing 1 which surrounds a rotatable drum 2 with a horizontal axis of rotation D.
  • a drive device with a gearbox with gear stages 4, 5, wherein the gear stage 4 here via belt drives 6, 7 by a first motor 8 and a second motor 9 is driven.
  • the drum 2 or the entire rotor as the entire rotating area of the solid bowl centrifuge having at least the spindle 19, the drum 2 and the screw 3 is rotatably supported by means of bearings 10, 11, which at the two axial ends of Drum 2 are arranged.
  • the one of the two bearing devices 10 between the two gear stages 4, 5 is located axially outside the one axial end of the drum.
  • mel 2 and the other bearing means 11 are arranged axially outside the other axial end of the drum 2 around the spindle (sections) 19.
  • the bearing devices 10, 11 preferably each comprise two rolling or sliding bearings 12, 13 with bearing housings 14, 15, which are supported by means of spring elements 17, 18 on a machine frame 16.
  • one of the bearings 12 is designed as a deep groove ball bearing and the other of the bearings 13 as a cylindrical roller bearing, so that with the cylindrical roller bearing a radial and with the deep groove ball bearings an axial and a radial support is achieved.
  • the rotor is supported at its two axial ends in each case by means of two of the spring elements 17, 18 resiliently on the machine frame 16 or on a foundation.
  • the spring elements for resilient support of the drum 2 act on the machine frame 16 or foundation in the non-radial direction as pressure elements.
  • the two spring elements 17, 18 are arranged axially in relation to the axis of rotation D in the region of the bearing devices 10, 11. Preferably, they are arranged axially even in a plane between the two bearings 12, 13 of each bearing device 10, 11.
  • the spring elements 17, 18 are formed according to the exemplary embodiment of Figure 2 as a combined spring and damping elements, relative to the horizontal axis of rotation D (in the coordinate system in Figure 1 in the X direction) aligned vertically or substantially vertically (in the Z direction) are.
  • This is achieved by - as shown in Figure 2 - the spring and Dämptungs- elements between cantilevers 20, 21 on the bearing housings 14, 15 and the machine frame 16 are arranged.
  • the two arms 20, 21 project from the outer circumference of the bearing housings in opposite directions, pointing away from each other.
  • a horizontal orientation perpendicular to the axis of rotation) and according to FIG. 3, a design slightly inclined to the horizontal (Y) is realized.
  • the arms 20, 21 are preferably arranged above the horizontally oriented axis of rotation of the drum.
  • the spring and damping elements 17, 18 are preferably arranged laterally next to the drum such that their upper end lies above the axis of rotation D of the drum 2 and its lower end lies below the axis of rotation of the drum 2 (FIG. 2).
  • the center of the springs lies in the axial direction laterally adjacent to the bearings at a height corresponding to the height of the center of the bearings.
  • Such an arrangement of the spring elements 17, 18 in a vertical or substantially vertical orientation is possible in that the spring elements 17, 18 in several directions - in Fig. 2 in the vertical and in the horizontal direction - have a spring stiffness.
  • Each coil spring is loaded in the vertical direction to pressure.
  • horizontal rotor movements lead to a thrust in the spring.
  • An embodiment in which the horizontal spring stiffness is about 30 to 100% of the vertical spring stiffness is advantageous.
  • the spring elements 17, 18 each slightly inclined to the vertical Z align (angle ⁇ to the vertical Z).
  • the angle .alpha between the longitudinal axes of the spring elements 17, 18 designed as a helical spring lies in each case between 0 ° and a maximum of 30 ° relative to the vertical Z, particularly preferably between 0 and 15 °.
  • the vertical orientation has the advantage that the containers with the viscous material need not be particularly sealed, which may be necessary if - as shown in Fig. 3 - no vertical alignment is selected.
  • the distance of the bearings 12, 13 is preferably such that it corresponds to at least half the bearing inner diameter.
  • the invention is suitable for implementation in fixed bearing floating bearing arrangements, in employed bearings, floating bearings, double-row bearings, bearings and plain bearings of various kinds.
  • the fixed bearing floating bearing arrangement allows a relatively simple installation and does not require adjusting the employment.
  • the drive of the drum 1 is preferably via belts directly to the spring-mounted drum 2.
  • suitable tuning of the spring stiffness of the spring elements 17, 18 is achieved that a possible change in the shaft drive caused by the wave forces (eg decrease in the biasing force by the centrifugal forces in the circulating area) does not lead to any impermissible operating states.
  • the motors 8, 9 are also decoupled from the machine frame. It is also conceivable, in particular for pillow block versions, to decouple the motors from the machine frame. It is particularly advantageous if several motors 8, 9 are used, which are arranged on a common plate.
  • the customer installation is then limited to wiring and connecting the pipes.
  • the spring elements 17, 18 (shown schematically) locally / constructively separated from the damping elements 22 are arranged.
  • the spring elements 17, 18 could in turn be coil springs, whereas for damping hydraulic or pneumatic damper, possibly controllable type, could be used.

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  • Centrifugal Separators (AREA)

Abstract

A screw centrifuge, having a rotor having a drum (2) having a horizontal axis of rotation, comprises the following: - the drum (2) having a horizontal axis of rotation (D); a screw (3) which is arranged in the drum and is rotatable at a differential speed relative to the rotatable drum; bearing elements (10, 11) at both axial ends of the drum (2) for mounting the drum (2); - spring elements (17, 18) for sprung support of the drum (2) on a machine frame (16), in each case at least two of the spring elements (17, 18) are arranged at the two axial ends of the drum, wherein the spring elements (17, 18) are orientated vertically or essentially vertically.

Description

Zentrifuge mit einem Rotor mit horizontaler Drehachse Centrifuge with a rotor with horizontal axis of rotation
Die Erfindung betrifft eine Schneckenzentrifuge nach dem Oberbegriff des Anspruchs 1.The invention relates to a screw centrifuge according to the preamble of claim 1.
Aus der EP 0 107470 B 1 und der US 4 504262 ist es bekannt, die Trommeln von De- kantern (Vollmantel-Schneckenzentrifugen) federnd abzustützen. Dabei sind die Federn als Schraubenfedern ausgebildet, welche radial zur Drehachse ausgerichtet sind. Durch Schraubbolzen, welche die Schraubenfedern durchsetzen, wird jeweils eine federnde Abstützung zwischen den Lagergehäusen der Lager der Trommel und einem Stützring realisiert, welcher konzentrisch zum Lagergehäuse angeordnet und am Maschinenge- stell befestigt oder mit diesem verbunden ist. Derart soll es möglich sein, Betriebsdrehzahlen oberhalb der Hauptresonanzfrequenz des Systems einzustellen. Konstruktiv darf zwischen den Lagergehäusen und den diesen umgebenden Stützringen nur ein relativ geringes Spiel bestehen.From EP 0 107470 B 1 and US Pat. No. 4,504,262 it is known to resiliently support the drums of decanters (solid bowl screw centrifuges). The springs are designed as helical springs, which are aligned radially to the axis of rotation. By bolt, which pass through the coil springs, a resilient support between the bearing housings of the bearings of the drum and a support ring is realized in each case, which is arranged concentrically to the bearing housing and attached to the machine frame or connected to this. In this way, it should be possible to set operating speeds above the main resonance frequency of the system. Structurally may exist between the bearing housings and the surrounding support rings only a relatively small game.
Die WO 94/07605 zeigt eine ähnliche Konstruktion wie die vorstehend genannten Schriften, wobei aber nur das eine axiale Ende der Trommel gefedert abgestützt ist.WO 94/07605 shows a similar construction as the above-mentioned writings, but only one axial end of the drum is supported sprung.
Eine lang gestreckte Zentrifuge mit einer Einrichtung zur Verminderung von Körperschallübertragungen zeigt die DE 43 15 694 Al.An elongated centrifuge with a device for the reduction of structure-borne sound transmission shows the DE 43 15 694 Al.
Lagerungen, die für eher kurz bauende Trommel geeignet und nicht stützend sondern hängend ausgelegt sind, zeigen die DE 26 06 589 Al, die DE 31 34 633 Al und die DE 66 09 01 I U.Bearings that are suitable for rather short drum and not supporting but designed hanging, show the DE 26 06 589 Al, DE 31 34 633 Al and DE 66 09 01 I U.
Zum technologischen Hintergrund werden noch die die DE 26 32 586 Al, die US 2,094,058, die US 4,640,770 und die DE 711 095 C genannt. Die Erfindung hat gegenüber diesem Stand der Technik die Aufgabe, eine verbesserte federnde Abstützung der Trommel - bzw. des gesamten Rotors mit der Trommel - für eine Zentrifuge der gattungsgemäßen Art zu schaffen. Insbesondere soll die Eignung für lang gestreckte Konstruktionen geeignet sein, bei denen das Verhältnis zwischen Länge des Rotors und dem Durchmesser des Rotors größer als 2 ist.The technological background is still the DE 26 32 586 Al, US 2,094,058, US 4,640,770 and DE 711 095 C called. The invention has over this prior art, the task of creating an improved resilient support of the drum - or the entire rotor with the drum - for a centrifuge of the generic type. In particular, the suitability should be suitable for elongated constructions in which the ratio between the length of the rotor and the diameter of the rotor is greater than 2.
Die Erfindung löst diese Aufgabe durch den Gegenstand des Anspruchs 1.The invention solves this problem by the subject matter of claim 1.
Vorteilhafte Ausgestaltungen sind den Unteransprüchen zu entnehmen.Advantageous embodiments can be found in the dependent claims.
Nach dem Kennzeichen des Anspruchs 1 sind die Federelemente vertikal oder im Wesentlichen vertikal ausgerichtet.According to the characterizing part of claim 1, the spring elements are aligned vertically or substantially vertically.
Vorzugsweise erfolgt die Abstützung mit kombinierten Feder-/Dämpfungselementen oder mit Federelementen und zu diesen separaten Dämpfungselementen.Preferably, the support is carried out with combined spring / damping elements or with spring elements and these separate damping elements.
Durch den Gegenstand des Anspruchs 1 wird die Trommel bzw. wird der gesamte Rotor mit der Trommel federnd abgestützt, ohne dass im Bereich der federnden Abstützung enge Spalte zwischen den relativ zueinander beweglichen Teilen bestehen, welche das System relativ schwer beherrschbar machen.By the subject matter of claim 1, the drum or the entire rotor is resiliently supported with the drum without narrow gaps exist between the relatively movable parts in the region of the resilient support, which make the system relatively difficult to control.
Von daher ist es anders als beim Stand der Technik nunmehr problemlos möglich, die Trommel mit einer Betriebsdrehzahl zu betreiben, die deutlich oberhalb der Grundresonanzfrequenz (Rotoreigenform) des Systems liegt.Therefore, unlike the prior art, it is now easily possible to operate the drum at an operating speed that is well above the fundamental resonance frequency (rotor shape) of the system.
Derart wird eine Zentrifuge mit horizontaler Drehachse geschaffen, die eine optimierte federnde Lagerung des Rotors aufweist, so dass sich im Betrieb ein optimiertes Verhalten ergibt.Such a centrifuge with a horizontal axis of rotation is created, which has an optimized resilient mounting of the rotor, so that there is an optimized behavior during operation.
Die Erfindung eignet sich insbesondere für lang gestreckte Konstruktionen, bei welchen das Verhältnis zwischen der Länge des Rotors bzw. der Trommel und dem Durchmesser des Rotors bzw. der Trommel vorzugsweise größer als 2, vorzugsweise größer als 2,5, insbesondere größer als 3 ist.The invention is particularly suitable for elongated constructions in which the ratio between the length of the rotor or the drum and the diameter the rotor or the drum is preferably greater than 2, preferably greater than 2.5, in particular greater than 3.
Aufgrund der Länge bilden sich bei sehr langen Rotoren bei bestimmten Frequenzen Biegeeigenformen bzw. Biegelinien des Rotors aus. Diese Frequenzen liegen in der Re- gel etwas oberhalb der üblichen Betriebsdrehzahlen.Due to the length, bending modes or bending lines of the rotor are formed at very high frequencies for very long rotors. These frequencies are usually slightly above the normal operating speeds.
Rotoreigenfrequenzen, welche die mögliche Betriebsdrehzahl begrenzen können, werden durch die Abkopplung der Gestell- oder Fundamentmasse zu höheren Frequenzen hin verschoben. Hierdurch ist es möglich, die Betriebsdrehzahl deutlich anzuheben.Rotoreigenfrequenzen, which can limit the possible operating speed are shifted by the decoupling of the frame or foundation mass to higher frequencies. This makes it possible to raise the operating speed significantly.
Da die Federelemente außer Federeigenschaften vorzugsweise auch nennenswerte dämpfende Eigenschaften aufweisen oder da zusätzlich zu den abstützenden Federelementen Dämpfungselemente vorgesehen sind, ergibt sich die Möglichkeit zu einer gezielten Dämpfung des schwingungsfähigen Rotorsystems, was einige weitere Vorteile bietet.Since the spring elements preferably also have appreciable damping properties in addition to spring properties or because damping elements are provided in addition to the supporting spring elements, there is the possibility of a targeted damping of the oscillatory rotor system, which offers some further advantages.
So wird die Auslenkung beim Durchlaufen kritischer Drehzahlen (Resonanzdrehzahlen bzw. Resonanzfrequenzen) z.B. des Rotorsystems gegenüber dem Maschinengestell oder Fundament beim An- und Abfahren der Schneckenzentrifuge auf sehr kleine Werte begrenzt. Hierdurch wird ein Anschlagen der bewegten Teile an den stillstehenden Teilen vermieden.Thus, the deflection when passing through critical speeds (resonance speeds or resonant frequencies) e.g. of the rotor system relative to the machine frame or foundation when starting and stopping the screw centrifuge to very small values. As a result, a striking of the moving parts is avoided at the stationary parts.
Durch die erfindungsgemäße Auslegung wird es möglich, den Schneckenzentrifuge in Hinsicht auf die ersten Rotoreigenfrequenzen überkritisch mit sehr hoher Drehzahl zu betreiben, so dass die Betriebsdrehzahl oberhalb der ersten Resonanzfrequenz des Rotors bzw. der Rotorteile (Trommel und Schnecke) liegen kann.The inventive design makes it possible to operate the screw centrifuge supercritically with respect to the first rotor natural frequencies at very high speed, so that the operating speed above the first resonant frequency of the rotor or the rotor parts (drum and screw) may be.
Da zudem nur kleine Wege zurückgelegt werden, können die Spalte z.B. zwischen Trommel und Fänger gegenüber den bisher für einen überkritischen Betrieb vorgeschla- genen Lösungen ohne bzw. mit geringer Dämpfung sogar verringert werden. Da die Spalte verringert werden, wird auch deren Abdichtung vereinfacht.Since, moreover, only small paths are covered, the gaps between the drum and the catcher, for example, can even be reduced with respect to the solutions previously proposed for supercritical operation without or with little damping. As the gaps are reduced, their sealing is also simplified.
Die Feder- und die Dämpfungselemente haben vorzugsweise frequenzabhängige, nicht konstante Eigenschaften, so dass eine Minimierung der Auslenkungswege, d.h. der Wege, die der Rotor bei Resonanzfrequenzen gegenüber dem Fundament oder dem Ma- schinengestell ausgelenkt wird, möglich ist.The spring and damping elements preferably have frequency dependent, non-constant characteristics such that minimization of the displacement paths, i. the ways that the rotor is deflected at resonance frequencies with respect to the foundation or the machine frame, is possible.
Da die Trommeln mit Flüssigkeit gefüllt sind, wenn sie sich im Betrieb drehen, kann auch diese Flüssigkeit der Schneckenzentrifuge zur Schwingung anregen, insbesondere bei Teilfüllungen beim An- und Abfahren.Since the drums are filled with liquid when they rotate during operation, this liquid of the screw centrifuge can also stimulate oscillation, especially in partial fillings on startup and shutdown.
Durch die Kombination aus Federung und Dämpfung kann ferner erreicht werden, dass der Rotor nicht zur Anregung von außen unzulässig zum Schwingen angeregt wird.The combination of suspension and damping can also be achieved that the rotor is not excited to excite from the outside inadmissible to vibrate.
Anregungen von außen liegen zwar meist nur mit einer relativ kleinen Amplitude vor.Although suggestions from outside are usually only available with a relatively small amplitude.
Sie könnten aber zufällig genau eine Resonanz des Systems anregen. Bei einem zu schwach gedämpften System gerät der Rotor dann in nicht erwünschte Schwingungen.They could, however, randomly stimulate exactly one resonance of the system. If the system is weakly dampened, the rotor will then turn into unwanted vibrations.
Durch die gewählte Positionierung der Federelemente direkt an der Trommellagerung wird zudem eine isotrope Dämpfung in vertikaler und horizontaler Richtung ermöglicht, die durch geeignete Anpassung des Dämpfers auch in gewünschter Weise beeinflussbar ist (anisotrop). Vorteilhaft ist eine isotrope Dämpfung.By the selected positioning of the spring elements directly to the drum bearing is also an isotropic damping in the vertical and horizontal direction allows, which can be influenced by suitable adaptation of the damper in the desired manner (anisotropic). Advantageous is an isotropic damping.
Die Dämpfung ist drehzahl- und wegabhängig und derart ausgelegt, dass bei geringen Drehzahlen beim Durchfahren der Rotoreigenfrequenzen bereits eine hohe Dämpfung vorliegt, während bei der Betriebsdrehzahl oberhalb der Resonanzfrequenz eine relativ geringe Dämpfung vorherrscht. Hierdurch werden beim Durchfahren der Eigenfrequenz die Ausschläge effektiv begrenzt.The damping is speed and travel-dependent and designed such that at low speeds when passing through the rotor natural frequencies already present a high attenuation, while prevails at the operating speed above the resonant frequency, a relatively low attenuation. As a result, the deflections are effectively limited when driving through the natural frequency.
In der Resonanz sollte die Dämpfung bei mindestens 3% liegen, besonders gute Ergebnisse werden bei Dämpfungen zwischen 10% und 30% erzielt. Unter Dämpfung wird die Umwandlung der Schwingungsenergie in eine andere Energieform, z.B. Wärme verstanden. Die Energieumwandlung bewirkt, dass die Amplituden im Bereich der Resonanzfrequenz verkleinert werden. Die prozentualen Angaben der Dämpfung sind im Sinne des Lehr' sehen Dämpfungsmaßes D zu verstehen:At resonance, the damping should be at least 3%, particularly good results are achieved at attenuations between 10% and 30%. Under damping is understood the conversion of the vibrational energy in another form of energy, eg heat. The energy conversion causes the amplitudes to be reduced in the range of the resonance frequency. The percentages of attenuation are to be understood in the sense of Lehr 's attenuation measure D:
D = d / G)0 D = d / G) 0
mitWith
d = k / (2m) undd = k / (2m) and
(Abklingkonstante der einhüllenden e-Funktion)(Decay constant of the enveloping e-function)
G)0 =V (c/m)G) 0 = V (c / m)
<öo :- Eigenfrequenz des ungedämpften Systems c := Federkonstante<öo: - natural frequency of the undamped system c: = spring constant
Bei der Betriebsdrehzahl bewirkt dagegen die geringe Dämpfung kleine dynamische Lagerkräfte, was eine hohe Lagerlebensdauer möglich macht. Hierzu ist es vorteilhaft, wenn das System derart abgestimmt ist, dass die Resonanzfrequenz bei einer Drehzahl erreicht wird, die kleiner als 70% der Betriebsdrehzahl, vorzugsweise kleiner als die halbe Betriebsdrehzahl ist.At operating speed, on the other hand, the low damping causes small dynamic bearing forces, which makes a long bearing life possible. For this purpose, it is advantageous if the system is tuned such that the resonance frequency is achieved at a speed which is less than 70% of the operating speed, preferably less than half the operating speed.
Erfindungsgemäß wird zusammenfassend eine Schneckenzentrifuge, insbesondere mit einem Vollmantel, realisierbar, mit der eine besonders hohe Betriebsdrehzahl gefahren werden kann.In summary, according to the invention, a screw centrifuge, in particular with a solid casing, can be realized, with which a particularly high operating speed can be driven.
Als besonderer Vorteil zu erwähnen ist noch, dass erfindungsgemäß trotz dieser hohenA particular advantage to mention is that according to the invention despite this high
Betriebsdrehzahl eine relativ leise arbeitende Schneckenzentrifuge geschaffen wird, da der Körperschalleintrag reduziert wird bzw. besonders niedrig ist, denn es erfolgt vom drehenden System keine direkte ungedämpfte Körperschallübertragung an ein Gehäuse oder ein Gestell.Operating speed is a relatively quiet-working screw centrifuge is created, since the body sound entry is reduced or is particularly low, because it is done by the rotating system no direct unattenuated structure-borne sound transmission to a housing or a frame.
Auch das Gehäuse der Schneckenzentrifuge baut besonders kompakt, wenn der Schneckenzentrifuge erfindungsgemäß ausgelegt ist.The housing of the screw centrifuge is particularly compact, if the screw centrifuge is designed according to the invention.
Nachfolgend wird die Erfindung unter Bezug auf die Zeichnung anhand von Ausführungsbeispielen näher beschrieben. Es zeigen:The invention will be described in more detail below with reference to the drawing with reference to exemplary embodiments. Show it:
Figur 1 eine Seitenansicht einer schematisch dargestellten Vollmantel- Schneckenzentrifuge; Figur 2 eine zu Fig. 1 um 90° gedrehte Ansicht des Bereichs der einen Lagereinrichtung der Schneckenzentrifuge aus Figur 1; undFigure 1 is a side view of a schematically illustrated solid bowl screw centrifuge; FIG. 2 shows a view, rotated by 90 ° with respect to FIG. 1, of the region of a bearing device of the screw centrifuge from FIG. 1; and
Figur 3 eine zu Figur 2 analoge Ansicht einer weiteren Ausgestaltung des Bereichs einer Lagervorrichtung einer Vollmantel-Schneckenzentrifuge.FIG. 3 shows a view similar to FIG. 2 of a further embodiment of the region of a bearing device of a solid bowl screw centrifuge.
Figur 1 zeigt eine Vollmantel-Schneckenzentrifuge mit einem Gehäuse 1, das eine drehbare Trommel 2 mit horizontaler Drehachse D umgibt.FIG. 1 shows a solid-bowl screw centrifuge with a housing 1 which surrounds a rotatable drum 2 with a horizontal axis of rotation D.
In der Trommel 2 ist eine mit einer Differenzdrehzahl zur Trommel 2 drehbare Schnecke 3 angeordnet.In the drum 2 a rotatable with a differential speed to the drum 2 screw 3 is arranged.
Zum Antrieb dient hier beispielhaft eine Antriebsvorrichtung mit einem Getriebe mit Getriebestufen 4, 5, wobei die Getriebestufe 4 hier über Riementriebe 6, 7 von einem ersten Motor 8 und einem zweiten Motor 9 angetrieben wird.To drive here is exemplified a drive device with a gearbox with gear stages 4, 5, wherein the gear stage 4 here via belt drives 6, 7 by a first motor 8 and a second motor 9 is driven.
Die Trommel 2 bzw. der gesamte Rotor als der gesamte sich drehende Bereich der Vollmantel- Schneckenzentrifuge, der zumindest die Spindel 19, die Trommel 2 und die Schnecke 3 aufweist, ist mittels Lagereinrichtungen 10, 11 drehbar gelagert, die an den beiden axialen Enden der Trommel 2 angeordnet sind.The drum 2 or the entire rotor as the entire rotating area of the solid bowl centrifuge having at least the spindle 19, the drum 2 and the screw 3 is rotatably supported by means of bearings 10, 11, which at the two axial ends of Drum 2 are arranged.
Beispielhaft - und vorteilhaft - ist hier die eine der beiden Lagereinrichtungen 10 zwischen den zwei Getriebestufen 4, 5 axial außerhalb des einen axialen Endes der Trom- mel 2 und die andere Lagereinrichtung 11 axial außerhalb des anderen axialen Endes der Trommel 2 um die Spindel(abschnitte) 19 angeordnet.By way of example, and advantageously, the one of the two bearing devices 10 between the two gear stages 4, 5 is located axially outside the one axial end of the drum. mel 2 and the other bearing means 11 are arranged axially outside the other axial end of the drum 2 around the spindle (sections) 19.
Die Lagereinrichtungen 10, 11 umfassen vorzugsweise jeweils zwei Wälz- oder Gleitlager 12, 13 mit Lagergehäusen 14, 15, die mittels Federelementen 17, 18 an einem Ma- schinengestell 16 abgestützt sind.The bearing devices 10, 11 preferably each comprise two rolling or sliding bearings 12, 13 with bearing housings 14, 15, which are supported by means of spring elements 17, 18 on a machine frame 16.
Besonders vorteilhaft ist es, wenn eines der Lager 12 als Rillenkugellager und das andere der Lager 13 als Zylinderrollenlager ausgebildet ist, so dass mit dem Zylinderrollenlager eine radiale und mit dem Rillenkugellager eine axiale und eine radiale Abstützung erreicht wird.It is particularly advantageous if one of the bearings 12 is designed as a deep groove ball bearing and the other of the bearings 13 as a cylindrical roller bearing, so that with the cylindrical roller bearing a radial and with the deep groove ball bearings an axial and a radial support is achieved.
Aufgrund geringer Axialkräfte ist es aber auch möglich, statt des Rillenkugellagers ein weiteres Zylinderrollenlager als Festlager einzusetzen, das mit entsprechenden Borden ausgestattet ist.Due to low axial forces but it is also possible to use instead of the deep groove ball bearing another cylindrical roller bearing as a fixed bearing, which is equipped with appropriate Borden.
Der Rotor ist an seinen beiden axialen Enden jeweils mittels zwei der Federelemente 17, 18 federnd an dem Maschinengestell 16 oder an einem Fundament abgestützt. Dabei wirken die Federelemente zur federnden Abstützung der Trommel 2 an dem Maschinengestell 16 oder Fundament in nicht radialer Richtung als Druckelemente.The rotor is supported at its two axial ends in each case by means of two of the spring elements 17, 18 resiliently on the machine frame 16 or on a foundation. The spring elements for resilient support of the drum 2 act on the machine frame 16 or foundation in the non-radial direction as pressure elements.
Die beiden Federelemente 17, 18 sind hier in bevorzugter Ausgestaltung axial - bezogen auf die Drehachse D - im Bereich der Lagereinrichtungen 10, 11 angeordnet. Vorzugsweise werden sie axial sogar in einer Ebene zwischen den beiden Lagern 12, 13 jeder Lagereinrichtung 10, 11 angeordnet.In a preferred embodiment, the two spring elements 17, 18 are arranged axially in relation to the axis of rotation D in the region of the bearing devices 10, 11. Preferably, they are arranged axially even in a plane between the two bearings 12, 13 of each bearing device 10, 11.
Dabei sind die Federelemente 17, 18 nach dem Ausfuhrungsbeispiel der Figur 2 als kombinierte Feder- und Dämpfungselemente ausgebildet, die bezogen zur horizontalen Drehachse D (im Koordinatensystem in Figur 1 in X-Richtung) vertikal oder im wesentlichen vertikal (in Z-Richtung) ausgerichtet sind. Dies wird erreicht, indem - wie aus Figur 2 ersichtlich - die Feder- und Dämptungs- elemente zwischen Auslegern 20, 21 an den Lagergehäusen 14, 15 und dem Maschinengestell 16 angeordnet sind. Vorzugsweise stehen die beiden Ausleger 20, 21 vom Außenumfang der Lagergehäuse in entgegen gesetzten, voneinander weg weisenden Richtungen vor. Dabei wird nach Fig. 2 eine horizontale Ausrichtung senkrecht zur Drehachse) und nach Fig. 3 eine leicht zur Horizontalen (Y) geneigte Auslegung verwirklicht. Die Ausleger 20, 21 sind vorzugsweise oberhalb der horizontal ausgerichteten Drehachse der Trommel angeordnet. Die Feder- und Dämpfungselemente 17, 18 sind vorzugsweise seitlich neben der Trommel derart angeordnet, dass ihr oberes Ende oberhalb der Drehachse D der Trommel 2 liegt und ihr unteres Ende unterhalb der Drehach- se der Trommel 2 (Fig. 2). Vorzugsweise liegt die Mitte der Federn in ihrer axialen Richtung seitlich neben den Lagern in einer Höhe, die der Höhe der Mitte der Lager entspricht.The spring elements 17, 18 are formed according to the exemplary embodiment of Figure 2 as a combined spring and damping elements, relative to the horizontal axis of rotation D (in the coordinate system in Figure 1 in the X direction) aligned vertically or substantially vertically (in the Z direction) are. This is achieved by - as shown in Figure 2 - the spring and Dämptungs- elements between cantilevers 20, 21 on the bearing housings 14, 15 and the machine frame 16 are arranged. Preferably, the two arms 20, 21 project from the outer circumference of the bearing housings in opposite directions, pointing away from each other. In this case, according to FIG. 2, a horizontal orientation perpendicular to the axis of rotation) and according to FIG. 3, a design slightly inclined to the horizontal (Y) is realized. The arms 20, 21 are preferably arranged above the horizontally oriented axis of rotation of the drum. The spring and damping elements 17, 18 are preferably arranged laterally next to the drum such that their upper end lies above the axis of rotation D of the drum 2 and its lower end lies below the axis of rotation of the drum 2 (FIG. 2). Preferably, the center of the springs lies in the axial direction laterally adjacent to the bearings at a height corresponding to the height of the center of the bearings.
Eine derartige Anordnung der Federelemente 17, 18 in vertikaler oder im wesentlichen vertikaler Ausrichtung ist dadurch möglich, dass die Federelemente 17, 18 in mehreren Richtungen - in Fig. 2 in vertikaler und in horizontaler Richtung - eine Federsteifigkeit aufweisen.Such an arrangement of the spring elements 17, 18 in a vertical or substantially vertical orientation is possible in that the spring elements 17, 18 in several directions - in Fig. 2 in the vertical and in the horizontal direction - have a spring stiffness.
Ergänzend werden bevorzugt kombinierte Feder- und Dämpfüngselemente 17, 18 ein- gesetzt.In addition, combined spring and damping elements 17, 18 are preferably used.
Derartige kombinierte Feder- und Dämpfungselemente sind an sich bekannt.Such combined spring and damping elements are known per se.
Sie können konstruktiv beispielsweise dadurch realisiert werden, dass als Federelemente 17, 18 entsprechend ausgelegte Schraubfedern verwendet werden, die jeweils in einem mit viskoser Flüssigkeit oder viskoser Masse gefüllten, vorzugsweise geschlossenen Behältnis angeordnet sind.They can be realized structurally, for example, by using correspondingly designed helical springs as spring elements 17, 18 which are each arranged in a preferably closed container filled with viscous liquid or viscous material.
Durch die Positionierung der Federelemente 17, 18 seitlich der Lagergehäuse wird eine nahezu isotrop federnde Unterstützung des Rotors in vertikaler und horizontaler Richtung ermöglicht. Durch eine Abstimmung der vertikalen und horizontalen Federraten der Federelemente kann darüber hinaus das Verhältnis der beiden Federraten in gewünschter Weise beein- flusst werden.By positioning the spring elements 17, 18 laterally of the bearing housing is a nearly isotropic resilient support of the rotor in the vertical and horizontal directions possible. By adjusting the vertical and horizontal spring rates of the spring elements, moreover, the ratio of the two spring rates can be influenced in the desired manner.
In der Konstruktion der Figur 1 geschieht dies beispielsweise durch Anpassung des Verhältnisses zwischen der Länge und dem Durchmesser der Schraubenfedern.In the construction of Figure 1 this is done, for example, by adjusting the ratio between the length and the diameter of the coil springs.
Jede Schraubenfeder wird in vertikaler Richtung auf Druck belastet. Horizontale Rotorbewegungen führen dagegen zu einem Schub in der Feder. Vorteilhaft ist eine Ausfüh- rung, bei der die horizontale Federsteifigkeit etwa 30 bis 100 % der vertikalen Feder- steifigkeit beträgt.Each coil spring is loaded in the vertical direction to pressure. By contrast, horizontal rotor movements lead to a thrust in the spring. An embodiment in which the horizontal spring stiffness is about 30 to 100% of the vertical spring stiffness is advantageous.
Durch die Nutzung der Federsteifigkeit in allen Richtungen (auch in axialer Richtung) ist es möglich, kombinierte Federdämpferelemente zu verwenden und diese Elemente entsprechend, insbesondere parallel oder nahezu parallel aufzustellen.By using the spring stiffness in all directions (also in the axial direction), it is possible to use combined spring damper elements and set up these elements accordingly, in particular parallel or nearly parallel.
Dabei wird die parallele Aufstellung in vertikaler Richtung nach Art der Figur 2 bevorzugt.Here, the parallel installation in the vertical direction of the type of Figure 2 is preferred.
Es ist aber auch möglich, die Federelemente 17, 18 jeweils etwas geneigt zur Vertikalen Z auszurichten (Winkel α zur Vertikalen Z).But it is also possible, the spring elements 17, 18 each slightly inclined to the vertical Z align (angle α to the vertical Z).
Eine derartige Ausführungsform mit zwei nach oben hin zueinander geneigten Federn, die aber nicht radial ausgerichtet sind, zeigt Figur 3. Es wäre auch denkbar, dass der Winkel α jeweils entgegengesetzt ausgerichtet wäre (nicht dargestellt).Such an embodiment with two mutually upwardly inclined springs, but which are not radially aligned, Figure 3. It would also be conceivable that the angle α would be aligned opposite each other (not shown).
Bevorzugt liegt der Winkel α zwischen den Längsachsen der als Schraubenfeder ausgebildeten Federelemente 17, 18 hier relativ zur Vertikalen Z jeweils zwischen 0° und maximal 30°, besonders bevorzugt zwischen 0 und 15°. Die vertikale Ausrichtung bringt den Vorteil mit sich, dass die Behälter mit der Viskomasse nicht besonders abgedichtet werden müssen, was notwendig sein kann, wenn - wie in Fig. 3 gezeigt - keine vertikale Ausrichtung gewählt wird.Preferably, the angle .alpha. Between the longitudinal axes of the spring elements 17, 18 designed as a helical spring lies in each case between 0 ° and a maximum of 30 ° relative to the vertical Z, particularly preferably between 0 and 15 °. The vertical orientation has the advantage that the containers with the viscous material need not be particularly sealed, which may be necessary if - as shown in Fig. 3 - no vertical alignment is selected.
Da die Lagerböcke durch die Federelemente kippbeweglich unterstützt sind, müssen die Trommellager zwischen Lagerbock und Trommel in der Lage sein, auch Kippmomente aufzunehmen.Since the bearing blocks are supported by the spring elements tilting, the drum bearings between bearing block and drum must be able to take up tilting moments.
Dies wird durch eine Anordnung der zwei Lager 12, 13 mit einem gewissen Abstand im Lagerbock erreicht. Der Abstand der Lager 12, 13 ist vorzugsweise so bemessen, dass er mindestens dem halben Lagerinnendurchmesser entspricht.This is achieved by an arrangement of the two bearings 12, 13 with a certain distance in the bearing block. The distance of the bearings 12, 13 is preferably such that it corresponds to at least half the bearing inner diameter.
Im Falle einer angestellten Lagerung gilt dies für die Stützbasis.In the case of salaried storage this applies to the support base.
Die Erfindung eignet sich zur Realisierung bei Festlager-Loslager- Anordnungen, bei angestellten Lagerungen, schwimmenden Lagerungen, Zweireihen-Lagerungen, Wälzlagern und Gleitlagern verschiedener Art.The invention is suitable for implementation in fixed bearing floating bearing arrangements, in employed bearings, floating bearings, double-row bearings, bearings and plain bearings of various kinds.
Besonders vorteilhaft ist eine Festlager-Loslager-Anordnung.Particularly advantageous is a fixed bearing floating bearing arrangement.
Die Festlager-Loslager-Anordnung erlaubt eine relativ einfache Montage und erfordert kein Justieren der Anstellung.The fixed bearing floating bearing arrangement allows a relatively simple installation and does not require adjusting the employment.
Der Antrieb der Trommel 1 erfolgt vorzugsweise über Riemen direkt auf die federnd gelagerte Trommel 2. Durch geeignete Abstimmung der Federsteifigkeiten der Feder- elemente 17, 18 wird erreicht, dass eine mögliche Änderung der durch den Riementrieb verursachten Wellenkräfte (z.B. Abnahme der Vorspannkraft durch die Fliehkräfte im umlaufenden Bereich) zu keinen unzulässigen Betriebszuständen führt.The drive of the drum 1 is preferably via belts directly to the spring-mounted drum 2. By suitable tuning of the spring stiffness of the spring elements 17, 18 is achieved that a possible change in the shaft drive caused by the wave forces (eg decrease in the biasing force by the centrifugal forces in the circulating area) does not lead to any impermissible operating states.
Die Motoren 8, 9 sind auch vom Maschinengestell abkoppelbar. Es ist auch denkbar, insbesondere bei Stehlagerversionen, die Motoren vom Maschinengestell abzukoppeln. Besonders vorteilhaft ist es, wenn mehrere Motoren 8, 9 verwendet werden, die auf einer gemeinsamen Platte angeordnet werden.The motors 8, 9 are also decoupled from the machine frame. It is also conceivable, in particular for pillow block versions, to decouple the motors from the machine frame. It is particularly advantageous if several motors 8, 9 are used, which are arranged on a common plate.
Die Unterbringung aller Komponenten in bzw. an einem gemeinsamen Gehäuse erlaubt die Ausfuhrung als installationsfertige Einheit, die vom Werk komplett geprüft ausge- liefert wird.The placement of all components in or on a common housing allows the execution as a ready to install unit, which is delivered fully tested by the factory.
Die kundenseitige Installation beschränkt sich dann auf Verkabeln und Anschließen der Rohrleitungen.The customer installation is then limited to wiring and connecting the pipes.
Nach Fig. 1 sind die Federelemente 17, 18 (schematisch dargestellt) örtlich/konstruktiv getrennt von den Dämpfungselementen 22 angeordnet. Die Federelemente 17, 18 könnten hier wiederum Schraubenfedern sein, wohingegen zur Dämpfung Hydraulik- oder Pneumatikdämpfer, ggf. steuerbarer Art, eingesetzt werden könnten. According to Fig. 1, the spring elements 17, 18 (shown schematically) locally / constructively separated from the damping elements 22 are arranged. The spring elements 17, 18 could in turn be coil springs, whereas for damping hydraulic or pneumatic damper, possibly controllable type, could be used.
Bezugszeichenreference numeral
Gehäuse 1Housing 1
Trommel 2Drum 2
Drehachse DRotation axis D
Schnecke 3Snail 3
Getriebestufen 4,5Gear stages 4.5
Riementriebe 6,7Belt drives 6,7
Motor 8,9Engine 8,9
Lagereinrichtungen 10,11Storage facilities 10,11
Wälz- oder Gleitlager 12,13Rolling or plain bearings 12,13
Lagergehäuse 14,15Bearing housing 14,15
Maschinengestell 16Machine frame 16
Federelemente 17,18Spring elements 17,18
Spindel 19Spindle 19
Auslegern 20,21Boom 20,21
Dämpfungselemente 23Damping elements 23
Vertikal ZVertical Z
Axial XAxial X
Horizontal Y Horizontal Y

Claims

Ansprüche claims
1. Schneckenzentrifuge mit einem Rotor mit einer Trommel (2) mit horizontaler Drehachse, die folgendes aufweist: a. die Trommel (2) mit horizontaler Drehachse (D) b. eine relativ zur drehbaren Trommel mit einer Differenzdrehzahl drehbare, in der Trommel angeordnete, Schnecke (3); c. an beiden axialen Enden der Trommel (2) Lagereinrichtungen (10, 11) zur Lagerung der Trommel (2); d. Federelemente (17, 18) zur federnden Abstützung der Trommel (2) an einem Maschinengestell (16) oder Fundament, e. wobei jeweils wenigstens zwei der die Trommel (2) abstützenden Federelemente (10, 11) an den beiden axialen Enden der Trommel angeordnet sind, dadurch gekennzeichnet, dass f. die Federelemente (17, 18) vertikal oder im Wesentlichen vertikal ausgerichtet sind.A centrifuge with a rotor having a drum (2) with a horizontal axis of rotation, comprising: a. the drum (2) with horizontal axis of rotation (D) b. a worm (3) rotatable relative to the rotatable drum at a differential speed and disposed in the drum; c. bearing means (10, 11) for supporting the drum (2) at both axial ends of the drum (2); d. Spring elements (17, 18) for resilient support of the drum (2) on a machine frame (16) or foundation, e. wherein at least two of the drum (2) supporting spring elements (10, 11) are arranged at the two axial ends of the drum, characterized in that f. the spring elements (17, 18) are aligned vertically or substantially vertically.
2. Schneckenzentrifuge nach Anspruch 1, dadurch gekennzeichnet, dass das2. centrifuge according to claim 1, characterized in that the
Verhältnis zwischen der Länge des Rotors bzw. der Trommel zum Durchmesser des Rotors bzw. der Trommel vorzugsweise größer als 2, vorzugsweise 2,5 insbesondere drei ist.Ratio between the length of the rotor or the drum to the diameter of the rotor or the drum is preferably greater than 2, preferably 2.5 in particular three.
3. Schneckenzentrifuge nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Federelemente (17, 18) als kombinierte Feder- und Dämpfungselemente ausgebildet sind.3. screw centrifuge according to claim 1 or 2, characterized in that the spring elements (17, 18) are designed as combined spring and damping elements.
4. Schneckenzentrifuge nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die die Abstützung über Federelemente und/oder zu diesen separaten Dämpfungselemente erfolgt. 4. screw centrifuge according to claim 1 or 2, characterized in that the support is via spring elements and / or to these separate damping elements.
5. Schneckenzentrifuge nach Anspruch 2, 3 oder 4, dadurch gekennzeichnet, dass die Federelemente (17, 18) zur federnden Abstützung der Trommel (2) an einem Maschinengestell (16) oder Fundament in nicht radialer Richtung als Druckelemente wirken.5. A centrifuge according to claim 2, 3 or 4, characterized in that the spring elements (17, 18) for resilient support of the drum (2) on a machine frame (16) or foundation in the non-radial direction act as pressure elements.
6. Schneckenzentrifuge nach Anspruch 3, 4 oder 5, dadurch gekennzeichnet, dass die Federelemente (17, 18) Schraubenfedern aufweisen, und dass die Längsachsen der Schraubenfedern vertikal oder im Wesentlichen vertikal ausgerichtet, d.h. in einem Winkel von 0 bis 30° zur Vertikalen (z) ausgerich- tet sind.A centrifuge according to claim 3, 4 or 5, characterized in that the spring elements (17, 18) comprise helical springs, and in that the longitudinal axes of the helical springs are oriented vertically or substantially vertically, i. are aligned at an angle of 0 to 30 ° to the vertical (z).
7. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Schraubenfedern in einem Winkel von 0 bis 15° zur Vertikalen ausgerichtet sind.7. Slug centrifuge according to one of the preceding claims, characterized in that the coil springs are aligned at an angle of 0 to 15 ° to the vertical.
8. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Federelemente (17, 18) in wenigstens zwei zueinander senkrechten Richtungen eine hohe Federsteifigkeit aufweisen.8. A screw centrifuge according to one of the preceding claims, characterized in that the spring elements (17, 18) in at least two mutually perpendicular directions have a high spring stiffness.
9. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Konstruktion derart ausgelegt ist, dass jede Schraubenfeder in vertikaler Richtung auf Druck und in Achsrichtung, insbesondere in horizontaler Richtung, auf Schub belastet wird.9. screw centrifuge according to any one of the preceding claims, characterized in that the construction is designed such that each coil spring in the vertical direction to pressure and in the axial direction, in particular in the horizontal direction, is loaded on thrust.
10. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Federelemente (17, 18) bei vertikaler Ausrichtung ihrer Längsachsen im eingebauten Zustand eine horizontale Federsteifigkeit aufweisen, die 30% bis 100% der vertikalen Federsteifigkeit beträgt.10. A screw centrifuge according to one of the preceding claims, characterized in that the spring elements (17, 18) in the vertical orientation of their longitudinal axes in the installed state have a horizontal spring stiffness, which is 30% to 100% of the vertical spring stiffness.
11. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Federelemente (17, 18) bei vertikaler Ausrichtung ih- rer Längsachsen eine horizontale Federsteifigkeit aufweisen, die 50% - 100% der vertikalen Federsteifigkeit beträgt.11. A screw centrifuge according to one of the preceding claims, characterized in that the spring elements (17, 18) in vertical alignment ih- Longitudinal axes have a horizontal spring stiffness, which is 50% - 100% of the vertical spring stiffness.
12. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Federelemente (17, 18) als kombinierte Feder- und Dämpfungselemente ausgebildet sind.12. Slug centrifuge according to one of the preceding claims, characterized in that the spring elements (17, 18) are designed as combined spring and damping elements.
13. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass neben den Federelementen (17', 18') von diesen räumlich getrennt angeordnete Dämpfungselemente (22) zum Abstützen der Trommel vorgesehen sind.13. A screw centrifuge according to one of the preceding claims, characterized in that in addition to the spring elements (17 ', 18') of these spatially separated damping elements (22) are provided for supporting the drum.
14. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Dämpfung der separaten Dämpfungselemente oder der kombinierten Feder-/Dämpfüngselemente drehzahlabhängig derart ausgelegt ist, dass bei geringen Drehzahlen vom Durchfahren der Rotoreigenform bereits eine hohe Dämpfung vorliegt, während bei der Betriebsdrehzahl oberhalb der Resonanzfrequenz eine niedrigere Dämpfung vorherrscht.14. A screw centrifuge according to one of the preceding claims, characterized in that the damping of the separate damping elements or the combined spring / Dämpfüngselemente speed-dependent is designed such that at low speeds from passing through the rotor shape already exists a high attenuation, while at the operating speed above the Resonant frequency a lower attenuation prevails.
15. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch ge- kennzeichnet, dass an jedem Ende der Trommel zwei der Federelemente (17,15. A screw centrifuge according to any one of the preceding claims, characterized in that at each end of the drum two of the spring elements (17,
18) vorgesehen sind, welche seitlich neben der Trommel (2) angeordnet sind.18) are provided, which are arranged laterally next to the drum (2).
16. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass an jedem Ende der Trommel (2) zwei der Federelemente seitlich neben der Trommel zwischen Auslegern (20, 21) der Lagergehäuse16, screw centrifuge according to one of the preceding claims, characterized in that at each end of the drum (2) has two of the spring elements laterally adjacent to the drum between cantilevers (20, 21) of the bearing housing
(14, 15) der Lagereinrichtungen und dem Maschinengestell (16) angeordnet sind.(14, 15) of the storage facilities and the machine frame (16) are arranged.
17. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch ge- kennzeichnet, dass die beiden Ausleger (20, 21) vom Außenumfang der La- gergehäuse (14, 15) in entgegen gesetzten, voneinander weg weisenden Richtungen vorstehen.17. A centrifuge according to one of the preceding claims, characterized in that the two arms (20, 21) from the outer circumference of the La gergehäuse (14, 15) protrude in opposite directions, facing away from each other.
18. Schneckenzentrifüge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Ausleger (20, 21) horizontal ausgerichtet sind.18. screw centrifuge according to one of the preceding claims, characterized in that the two arms (20, 21) are aligned horizontally.
19. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Ausleger (20, 21) zur Horizontalen geneigt ausgerichtet sind.19, screw centrifuge according to one of the preceding claims, characterized in that the two arms (20, 21) are inclined to the horizontal.
20. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Ausleger (20, 21) oberhalb der Drehachse der Trommel angeordnet sind.20. Screw centrifuge according to one of the preceding claims, characterized in that the two arms (20, 21) are arranged above the axis of rotation of the drum.
21. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch ge- kennzeichnet, dass die Lagereinrichtungen (10. 11) jeweils zwei Lager (12,21. A screw centrifuge according to one of the preceding claims, characterized in that the bearing devices (10. 11) each have two bearings (12,
13) aufweisen, wobei die Federelemente (17, 18) in einer Ebene senkrecht zur Drehachse angeordnet sind, die zwischen den beiden Lagern (12, 13) liegt oder die beiden Lager (12, 13) umfasst.13), wherein the spring elements (17, 18) are arranged in a plane perpendicular to the axis of rotation, which lies between the two bearings (12, 13) or the two bearings (12, 13).
22. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Mitte der Federn in ihrer axialen Richtung seitlich neben den Lagern in einer Höhe liegt, die der Höhe der Mitte der Lager entspricht.22. A screw centrifuge according to one of the preceding claims, characterized in that the center of the springs in the axial direction laterally adjacent to the bearings at a height corresponding to the height of the center of the bearing.
23. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass das eine der Lager (12, 13) ein Rillenkugellager und das andere Lager ein Zylinderrollenlager ist und/oder in jedem der Lagergehäuse (14, 15) zwei Lager angeordnet sind. 23. A screw centrifuge according to one of the preceding claims, characterized in that one of the bearings (12, 13) is a deep groove ball bearing and the other bearing is a cylindrical roller bearing and / or in each of the bearing housings (14, 15) two bearings are arranged.
24. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Abstand der Lager (12, 13) vorzugsweise so bemessen, dass er mindestens dem halben Lagerinnendurchmesser entspricht.24. A screw centrifuge according to one of the preceding claims, characterized in that the distance between the bearings (12, 13) preferably such that it corresponds to at least half the bearing inner diameter.
25. Schneckenzentrifuge nach einem der vorstehenden Ansprüche, gekennzeich- net durch eine Auslegung derart, dass die Dämpfung in der Resonanz bei mindestens 3%, vorzugsweise zwischen 10% und 30% liegt. 25. A screw centrifuge according to one of the preceding claims, characterized by a design such that the damping in the resonance is at least 3%, preferably between 10% and 30%.
EP07820074.8A 2006-09-11 2007-09-07 Centrifuge having a rotor having horizontal axis of rotation Active EP2063998B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006043265 2006-09-11
PCT/EP2007/059421 WO2008031775A1 (en) 2006-09-11 2007-09-07 Centrifuge having a rotor having horizontal axis of rotation

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EP2063998A1 true EP2063998A1 (en) 2009-06-03
EP2063998B1 EP2063998B1 (en) 2017-04-19

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US (1) US8465406B2 (en)
EP (1) EP2063998B1 (en)
JP (1) JP5087806B2 (en)
CN (1) CN101511489B (en)
AU (1) AU2007296304B2 (en)
BR (1) BRPI0716798B1 (en)
DE (1) DE102007042549B4 (en)
DK (1) DK2063998T3 (en)
ES (1) ES2630395T3 (en)
NO (1) NO342206B1 (en)
NZ (1) NZ574969A (en)
RU (1) RU2456084C2 (en)
WO (1) WO2008031775A1 (en)

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Also Published As

Publication number Publication date
BRPI0716798A2 (en) 2013-09-17
DE102007042549B4 (en) 2017-12-28
DK2063998T3 (en) 2017-07-31
CN101511489A (en) 2009-08-19
US8465406B2 (en) 2013-06-18
CN101511489B (en) 2012-09-05
WO2008031775A1 (en) 2008-03-20
AU2007296304B2 (en) 2011-08-18
RU2009112856A (en) 2010-10-20
NO20091304L (en) 2009-03-30
RU2456084C2 (en) 2012-07-20
ES2630395T3 (en) 2017-08-21
BRPI0716798B1 (en) 2019-05-07
JP5087806B2 (en) 2012-12-05
NZ574969A (en) 2011-10-28
NO342206B1 (en) 2018-04-16
JP2010502441A (en) 2010-01-28
EP2063998B1 (en) 2017-04-19
DE102007042549A1 (en) 2008-03-27
AU2007296304A1 (en) 2008-03-20
US20100167902A1 (en) 2010-07-01

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