EP2063998B1 - Zentrifuge mit einem rotor mit horizontaler drehachse - Google Patents

Zentrifuge mit einem rotor mit horizontaler drehachse Download PDF

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Publication number
EP2063998B1
EP2063998B1 EP07820074.8A EP07820074A EP2063998B1 EP 2063998 B1 EP2063998 B1 EP 2063998B1 EP 07820074 A EP07820074 A EP 07820074A EP 2063998 B1 EP2063998 B1 EP 2063998B1
Authority
EP
European Patent Office
Prior art keywords
drum
screw centrifuge
spring
rotor
bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP07820074.8A
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German (de)
English (en)
French (fr)
Other versions
EP2063998A1 (de
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
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GEA Mechanical Equipment GmbH
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Publication date
Application filed by GEA Mechanical Equipment GmbH filed Critical GEA Mechanical Equipment GmbH
Publication of EP2063998A1 publication Critical patent/EP2063998A1/de
Application granted granted Critical
Publication of EP2063998B1 publication Critical patent/EP2063998B1/de
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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.
  • the WO 94/07605 shows a similar construction as the aforementioned writings, but only one axial end of the drum is spring supported.
  • An elongated centrifuge with a device for reducing structure-borne noise transmissions shows the DE 43 15 694 A1 .
  • the invention has the object over this prior art, an improved resilient support of the drum - or the entire rotor with the drum - for To create 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 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 suitable for elongated constructions in which the ratio between the length of the rotor or the drum and the diameter of the rotor or the drum is greater than 2, preferably greater than 2.5, in particular greater than 3. 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 usual operating speeds.
  • 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 may be e.g. between drum and catcher over the previously proposed for a supercritical operation solutions without or with low attenuation even be reduced.
  • the spring and the damping elements preferably have frequency-dependent, non-constant properties, so that a minimization of the deflection paths, ie the paths 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 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.
  • a particular advantage to mention is that according to the invention despite this high operating speed, a relatively quiet-working screw centrifuge is created because the body sound is reduced or is particularly low, because it is done by the rotating system no direct undamped 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 shows a solid bowl centrifuge with a housing 1, which surrounds a rotatable drum 2 with 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 bearing devices 10, 11 preferably each comprise two rolling or plain 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 according to the embodiment of FIG. 2 formed as a combined spring and damping elements, relative to the horizontal axis of rotation D (in the coordinate system in FIG. 1 in the X direction) are oriented vertically or substantially vertically (in the Z direction).
  • FIG. 2 This is achieved by - like out FIG. 2 seen - the spring and damping elements between arms 20, 21 are arranged on the bearing housings 14, 15 and the machine frame 16.
  • the two arms 20, 21 project from the outer circumference of the bearing housings in opposite directions, pointing away from each other. It is after Fig. 2 a horizontal orientation perpendicular to the axis of rotation) and after Fig. 3 realized a slightly inclined to the horizontal (Y) interpretation.
  • 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 its upper end is above the axis of rotation D of the drum 2 and its lower end below the axis of rotation of the drum 2 (FIG. 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.
  • the ratio of the two spring rates can be influenced in the desired manner.
  • FIG. 1 This is done, for example, by adjusting the ratio between the length and the diameter of the coil springs.
  • Each coil spring is loaded in the vertical direction to pressure.
  • horizontal rotor movements lead to a thrust in the spring.
  • the horizontal spring stiffness is about 30 to 100% of the vertical spring stiffness.
  • the spring elements 17, 18 each slightly inclined to the vertical Z align (angle ⁇ to the vertical Z).
  • the angle ⁇ between the longitudinal axes of the spring elements 17, designed as a helical spring is in each case between 0 ° and 15 ° relative to the vertical Z.
  • the vertical orientation has the advantage that the containers with the viscous mass need not be specially sealed, which may be necessary if - as in Fig. 3 shown - no vertical alignment is selected.
  • the distance between 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 movable bearing arrangements, in salaried bearings, floating bearings, two-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 carried out via belt directly on the spring-mounted drum 2.
  • By appropriate tuning of the spring stiffness of the spring elements 17, 18 is achieved that a possible change in the belt drive caused by the wave forces (eg decrease in the biasing force by the centrifugal forces in the circumferential Range) 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.
  • the customer installation is then limited to wiring and connecting the pipes.
  • Fig. 1 To Fig. 1 are the spring elements 17, 18 (shown schematically) locally / constructively separated from the damping elements 22 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.

Landscapes

  • Centrifugal Separators (AREA)
EP07820074.8A 2006-09-11 2007-09-07 Zentrifuge mit einem rotor mit horizontaler drehachse Active EP2063998B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006043265 2006-09-11
PCT/EP2007/059421 WO2008031775A1 (de) 2006-09-11 2007-09-07 Zentrifuge mit einem rotor mit horizontaler drehachse

Publications (2)

Publication Number Publication Date
EP2063998A1 EP2063998A1 (de) 2009-06-03
EP2063998B1 true EP2063998B1 (de) 2017-04-19

Family

ID=38698388

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07820074.8A Active EP2063998B1 (de) 2006-09-11 2007-09-07 Zentrifuge mit einem rotor mit horizontaler drehachse

Country Status (13)

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

Families Citing this family (8)

* Cited by examiner, † Cited by third party
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DE102006028804A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge mit Antriebsvorrichtung
DE102007042549B4 (de) * 2006-09-11 2017-12-28 Gea Mechanical Equipment Gmbh Zentrifuge mit einem Rotor mit horizontaler Drehachse
US8808154B2 (en) * 2010-09-13 2014-08-19 Hiller Gmbh Drive apparatus in a scroll centrifuge having a gearbox with a housing nonrotatably connected to a drive shaft
DE102011080036A1 (de) * 2011-07-28 2013-01-31 Zf Friedrichshafen Ag Radnahe Antriebseinheit für ein Kraftfahrzeug
DE102014102472B4 (de) * 2014-02-25 2021-04-22 Andreas Hettich Gmbh & Co. Kg Zentrifuge
DE102018119279A1 (de) 2018-08-08 2020-02-13 Gea Mechanical Equipment Gmbh Vollmantel-Schneckenzentrifuge
USD928856S1 (en) * 2019-06-11 2021-08-24 Henan Changda Bee Industry Co., Ltd Gearbox for honey centrifuge
EP3878559A1 (en) 2020-03-12 2021-09-15 Alfa Laval Corporate AB A centrifugal separator

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Also Published As

Publication number Publication date
NO342206B1 (no) 2018-04-16
BRPI0716798A2 (pt) 2013-09-17
AU2007296304B2 (en) 2011-08-18
US8465406B2 (en) 2013-06-18
WO2008031775A1 (de) 2008-03-20
US20100167902A1 (en) 2010-07-01
RU2009112856A (ru) 2010-10-20
BRPI0716798B1 (pt) 2019-05-07
EP2063998A1 (de) 2009-06-03
AU2007296304A1 (en) 2008-03-20
NO20091304L (no) 2009-03-30
JP2010502441A (ja) 2010-01-28
DE102007042549A1 (de) 2008-03-27
RU2456084C2 (ru) 2012-07-20
ES2630395T3 (es) 2017-08-21
JP5087806B2 (ja) 2012-12-05
DK2063998T3 (en) 2017-07-31
CN101511489A (zh) 2009-08-19
DE102007042549B4 (de) 2017-12-28
NZ574969A (en) 2011-10-28
CN101511489B (zh) 2012-09-05

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