EP0376919A2 - Décanteur à élément de construction suspendu élastiquement - Google Patents

Décanteur à élément de construction suspendu élastiquement Download PDF

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Publication number
EP0376919A2
EP0376919A2 EP90100036A EP90100036A EP0376919A2 EP 0376919 A2 EP0376919 A2 EP 0376919A2 EP 90100036 A EP90100036 A EP 90100036A EP 90100036 A EP90100036 A EP 90100036A EP 0376919 A2 EP0376919 A2 EP 0376919A2
Authority
EP
European Patent Office
Prior art keywords
decanter
machine bed
drum
components
decoupled
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
EP90100036A
Other languages
German (de)
English (en)
Other versions
EP0376919B1 (fr
EP0376919A3 (fr
Inventor
Ernst Adolf Dr. Jäger
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.)
Flottweg GmbH
Original Assignee
Flottweg 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
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Application filed by Flottweg GmbH filed Critical Flottweg GmbH
Publication of EP0376919A2 publication Critical patent/EP0376919A2/fr
Publication of EP0376919A3 publication Critical patent/EP0376919A3/fr
Application granted granted Critical
Publication of EP0376919B1 publication Critical patent/EP0376919B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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 decanter with the features of the preamble of claim 1.
  • Decanters - also called solid bowl screw centrifuges - are used to separate so-called suspensions, substances that comprise a mixture of solid matter and one or more liquids of different weights. The separation takes place using centrifugal force, which is why high speeds are required depending on the suspension.
  • the solid that accumulates under the influence of gravity on the inner surface of the jacket is guided with the aid of a screw rotating within the rapidly rotating centrifuge jacket with a comparatively low differential speed, usually via a drying section that increases conically towards the axis of rotation to the so-called solid discharge, while the liquid phase or also several liquid phases of different weights with a decreasing specific gravity towards the axis of rotation are generally drawn off at the end of the drum axially opposite the solids discharge.
  • Such decanters are known.
  • Such a particularly fast-rotating decanter together with its drive and possibly also auxiliary units such as a control cabinet, etc., all of which are held on a common machine bed, forms a mass system that has at least one critical natural frequency for the operating behavior of the decanter, which is one of several natural frequencies of this Mass system can be.
  • This critical natural frequency in which the moving parts execute a vibration of a correspondingly high amplitude, is disturbing if it is close to or below the operating frequency of the decanter, which is determined by the rotating parts such as the drum, screw, drive motor etc.
  • This operating frequency is only theoretically a constant, it is actually a certain operating frequency range due to the influence of the solids taken up, an operating control and the like.
  • the invention is based on the task of circumventing or damping critical natural vibrations in a decanter system of the type mentioned at the outset, that is to say a mass system connected via the machine bed.
  • the starting point is initially to keep the critical natural frequency away from the range of the operating frequencies because the operating frequency has a stimulating effect due to imbalances in the drum, the screw, etc.
  • this is achieved by shifting the mass system towards higher values by decoupling part of the mass with regard to the critical natural frequencies.
  • such a measure may already be sufficient to locate the so-called critical natural frequency of the system reduced by the decoupled part of the mass outside, or more precisely above, the operating frequency range, so that the feared critical natural frequency is no longer caused by the occurring operating frequency is triggered stimulating.
  • the decoupled mass part that is to say a component which is already present for the operation of the decanter, is decoupled to the extent that its suspension is made correspondingly “softer” with respect to the elastic coupling with respect to the machine bed or the rest of the other components.
  • this suspension to change the vibrating mass, less the mass of the decoupled part itself, which cannot be changed arbitrarily due to its function. It is important that the copied pelte mass part with respect to its natural frequency or set-up frequency compared to the machine bed and thus the remaining components of the mass system so dimensioned or adjusted in its elastic suspension that its natural frequency corresponds to the critical natural frequency of the remaining mass system.
  • an attenuator is switched on, which is actuated in the event of the occurrence of the critical natural frequency by the correspondingly high amplitudes associated therewith over a correspondingly large friction path and thus absorbs vibrational energy.
  • this decoupled mass can be the drive motor of the decanter, the frequency of which is accordingly in the range of the critical natural frequency of the remaining mass system.
  • the motor is thus suspended in relation to the machine bed in such a way that it triggers an oscillation when it starts, the frequency of which lies in the range of the critical natural frequency, so that with appropriate excitation and occurrence of a correspondingly large amplitude, the damping element arranged between the motor and the machine bed has a correspondingly high friction work accomplishes.
  • the decanter's drive motor was given as an example of a mass that can be decoupled.
  • auxiliary units or other parts of the decanter can also be uncoupled in a comparable manner and "synchronized" with regard to the critical natural frequency.
  • a disturbing oscillation can also occur during operation due to the influence of the solid matter of the suspension being processed. This influence is not constant or does not depend linearly on the speed.
  • a decoupling between the screw and the decanter can be carried out in a targeted manner, preferably in the area of the rotational connection between these two components.
  • the gear between worm and drum can be a rigid gear, but it can also be a controllable gear motor.
  • the decoupling between the worm and the rotor is preferably carried out via a friction member, similar to the principle known for clutches from the field of motor vehicles.
  • the arrangement of such a resilient friction clutch can be provided anywhere between the drum and the worm, in particular between the differential speed gear and the worm hub.
  • the vibrations caused by the solid matter load on the worm are particularly damaging to the gearbox, because after the occurrence of corresponding stresses, sudden loads have to be absorbed.
  • the friction member which - as with the rest Solutions - preferably arranged parallel to the resilient coupling, these vibrations are damped to a greater extent with increasing amplitude and thus longer friction path.
  • the aforementioned auxiliary damper in the form of the decoupled partial mass matched to the critical natural frequency also comes into effect, and the more effective the closer the interference frequencies in the range of the critical natural frequencies of the remaining mass system.
  • the screw can also be supported axially, at least resiliently, whereby the bearings of the decanter are kept free or protected from corresponding shock loads.
  • an attenuator can also be used in this range of motion.
  • the axial damping or cushioning can be provided in addition to that in the course of the gear connection between the screw and drum.
  • the component decoupled from the rest of the mass system can also be designed in a controlled manner with regard to its natural frequency, in order to bring about an adaptation to the respectively occurring maximum amplitude in the course of a control with automatic scanning of the vibrations of the system, for example the vibration amplitudes.
  • the value obtained by scanning the vibration amplitudes can, for example, be used to determine the rigidity of the to change the sprung connection of the decoupled mass to the rest of the system or the machine bed so that the natural frequency of the decoupled component corresponds to the critical, respectively sensed natural frequency of the rest of the system.
  • FIG. 1 shows in two views rotated by 90 ° as essential a holder 8 for a drive motor 6, which is arranged on a common machine bed 1 together with the centrifuge or decanter designated as a whole by 2 (FIG. 2).
  • FIGS. 1 shows in two views rotated by 90 ° as essential a holder 8 for a drive motor 6, which is arranged on a common machine bed 1 together with the centrifuge or decanter designated as a whole by 2 (FIG. 2).
  • the rotation unit 2 of the decanter consists of a drum 3 and a worm 4, which are connected to one another via a differential speed gear 5 in such a way that the worm 4, depending on the right or left pitch of its helix or Direction of rotation of the drum 3 moves slower or faster than this, so that a solid settling on the inner wall of the drum due to the centrifugal force under the rotational movement is transported from the screw to a discharge opening, not shown, in the conically narrowing part of the drum.
  • This design of decanters or solid bowl screw centrifuges is known.
  • the gear 5 arranged between the worm 4 and the drum 3 can be one that works with a fixed reduction, but it can also be a gear with variable reduction, in so far as it is a gear motor.
  • the drive motor 6 which drives the decanter as a whole, which, for example, is directly connected to the drum or also to the screw, regularly via the intermediate gear, is designed as a so-called decoupled mass part of the overall system of the decanter, which - as shown - consists of drum 3, screw 4, gear 5 and auxiliary units (not shown) and of course there is the drive motor 6, which is arranged in Figures 2 and 3 via a belt drive 20 and in Figures 4 and 5 coaxial to the axis of rotation of the decanter.
  • the drive motor 6 which is arranged in Figures 2 and 3 via a belt drive 20 and in Figures 4 and 5 coaxial to the axis of rotation of the decanter.
  • the drive motor 6 is fastened in the central region of a membrane wall 8, designated overall by 7, which is connected to the machine bed 1 in a manner not shown in any more detail.
  • the membrane wall 8 is provided with a large number of openings 9 which extend approximately concentrically around a centrally arranged holding zone 12, in which the motor - indicated in FIG. 1 - is flanged.
  • the breakthroughs are seen in the circumferential direction each interrupted by bridges 10, so that there are material webs 11 of appropriately long design from zone 12 to the circumference over bridges 10 between perforations 9.
  • the purpose of this embodiment is to make the membrane wall 8 rigid from the holding zone 12 with respect to the machine bed 1 with respect to torque transmissions, while the holding zone 12 is flexible in directions which have a component perpendicular to the plane of the membrane wall 8.
  • the mass and elasticity of the overall mass system decanter responsible for the critical natural frequency is increased insofar as part of the mass, namely that of the drive motor, is withdrawn from this system.
  • such a measure may already be sufficient to avoid critical natural frequencies in the operating range or to be able to run through them uncritically.
  • the critical natural frequency will often remain at least in the vicinity of the operating frequency and thus the vibrations corresponding to the excitation, which is why, in a particularly preferred embodiment, the decoupled component - there may also be several of them - with regard to its "set-up frequency", ie its natural frequency compared to the machine bed is interpreted that this natural frequency coincides with the critical natural frequency of the system of the remaining components. Then there are long vibration paths in the event that the critical natural frequency occurs more or less strongly due to excitation, and these movements can be reduced accordingly by using damping elements, that is, as a rule, converted into heat by means of friction losses.
  • FIG 3 shows such an example using a drive motor 6, which with the help of so-called vibrating metals, i.e. Rubber-elastic feet in all directions on which the machine bed 1 is supported.
  • the motor housing is held inelastic in this respect by a pull rod 15 on the machine bed 1 in the direction of the belt tension.
  • This tie rod 15 takes over the task of the membrane wall 8 as far as the rigidity in the direction of the torque transmission is concerned.
  • the motor 6 is held with respect to the machine bed 1 by means of these oscillating metals 14 with a natural oscillation which is in the order of magnitude of the critical natural frequency of the remaining mass system of the decanter.
  • FIG. 3 shows the arrangement of the damping element with respect to the vibrations to be damped.
  • FIGS. 4 and 5 show a spring-loaded and / or damped mounting of the screw 4 with respect to the drum 3, the vibration phenomena to be intercepted between the screw and the drum caused by these measures being caused by the solids that accumulate are that the worm is frictionally inclined to reduce its differential speed relative to the drum and corresponding forces are stored in the gear 5 until this accelerates the worm suddenly against the drum due to its elasticity. This also causes rhythmic running disturbances that have the character of vibrations and put a considerable strain on the operation, above all the storage of the rotating decanter parts. Due to the inclination of the screw helix, the forces that trigger such vibrations between the drum and the screw are both rotational and translational in the direction of the axis of rotation, which is why - FIG.
  • critical natural frequencies By scanning the vibration, for example the vibration amplitude, of the decanter, critical natural frequencies can be determined, and the signals obtained from such monitoring can be used to control the natural frequency of the component or components decoupled with the aim of matching their natural frequency to critical natural frequencies of the decanter mass system in order to be able to provide large damping paths.
  • This can be done, for example, by controlling the spring characteristic in the suspension of the decoupled one Component, drive motor or worm in the present example, in particular with the aid of a correspondingly arranged hydraulic device which influences the spring travel and / or the spring hardness.

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  • Centrifugal Separators (AREA)
EP90100036A 1988-12-30 1990-01-02 Décanteur à élément de construction suspendu élastiquement Expired - Lifetime EP0376919B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3844406 1988-12-30
DE3844407 1988-12-30
DE3844406 1988-12-30
DE3844407 1988-12-30

Publications (3)

Publication Number Publication Date
EP0376919A2 true EP0376919A2 (fr) 1990-07-04
EP0376919A3 EP0376919A3 (fr) 1991-05-02
EP0376919B1 EP0376919B1 (fr) 1997-04-09

Family

ID=25875828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90100036A Expired - Lifetime EP0376919B1 (fr) 1988-12-30 1990-01-02 Décanteur à élément de construction suspendu élastiquement

Country Status (4)

Country Link
US (1) US5120298A (fr)
EP (1) EP0376919B1 (fr)
DE (1) DE59010695D1 (fr)
DK (1) DK0376919T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK167600B1 (da) * 1992-10-01 1993-11-29 Ffg Projektudvikling Aps Dekantercentrifuge
WO2007023566A1 (fr) * 2005-08-26 2007-03-01 Tomoe Engineering Co., Ltd. Séparateur centrifuge de type décanteur
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
DE102011002126A1 (de) * 2011-04-18 2012-10-18 Gea Mechanical Equipment Gmbh Zentrifuge und Verfahren zur Überwachung eines Drehmoments

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1027844A (fr) * 1949-11-18 1953-05-15 Laval Separator Co De Séparateur centrifuge à entraînement direct
DE1152961B (de) * 1959-04-23 1963-08-14 Lewis Appliance Corp Ltd Elastische Lagerung fuer Trommelwellen von Zentrifugen
GB955532A (en) * 1961-07-11 1964-04-15 Monsanto Chem Australia Ltd Improvements relating to industrial centrifuges
FR2357307A1 (fr) * 1976-07-06 1978-02-03 Pennwalt Corp Centrifugeuse verticale a decharge continue des matieres solides
DE3142779A1 (de) * 1981-10-28 1983-05-11 Werner Prof. Dr. 6740 Landau Stahl Dekantier-zentrifuge

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4069966A (en) * 1976-10-14 1978-01-24 Bird Machine Company, Inc. Centrifuge with chatter suppression
DE3103029A1 (de) * 1981-01-30 1982-08-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Schneckenzentrifuge

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1027844A (fr) * 1949-11-18 1953-05-15 Laval Separator Co De Séparateur centrifuge à entraînement direct
DE1152961B (de) * 1959-04-23 1963-08-14 Lewis Appliance Corp Ltd Elastische Lagerung fuer Trommelwellen von Zentrifugen
GB955532A (en) * 1961-07-11 1964-04-15 Monsanto Chem Australia Ltd Improvements relating to industrial centrifuges
FR2357307A1 (fr) * 1976-07-06 1978-02-03 Pennwalt Corp Centrifugeuse verticale a decharge continue des matieres solides
DE3142779A1 (de) * 1981-10-28 1983-05-11 Werner Prof. Dr. 6740 Landau Stahl Dekantier-zentrifuge

Also Published As

Publication number Publication date
US5120298A (en) 1992-06-09
DE59010695D1 (de) 1997-05-15
EP0376919B1 (fr) 1997-04-09
DK0376919T3 (da) 1997-04-28
EP0376919A3 (fr) 1991-05-02

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