EP0376919B1 - Décanteur à élément de construction suspendu élastiquement - Google Patents

Décanteur à élément de construction suspendu élastiquement Download PDF

Info

Publication number
EP0376919B1
EP0376919B1 EP90100036A EP90100036A EP0376919B1 EP 0376919 B1 EP0376919 B1 EP 0376919B1 EP 90100036 A EP90100036 A EP 90100036A EP 90100036 A EP90100036 A EP 90100036A EP 0376919 B1 EP0376919 B1 EP 0376919B1
Authority
EP
European Patent Office
Prior art keywords
decanter
drum
machine bed
component
drive motor
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.)
Expired - Lifetime
Application number
EP90100036A
Other languages
German (de)
English (en)
Other versions
EP0376919A2 (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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25875828&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0376919(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
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

Links

Images

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 is carried out using centrifugal force, which is why high speeds are required depending on the suspension.
  • the solid that collects under the influence of gravity on the inner surface of the jacket is usually guided with the aid of a screw rotating within the rapidly rotating centrifuge jacket with a comparatively low differential speed over 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 disruptive 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 object of the invention is to circumvent or dampen 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 in that the mass system is shifted to higher values with regard to the critical natural frequencies by decoupling part of the mass.
  • such a measure may already be sufficient to locate the so-called critical natural frequency of the system, which is 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 excited.
  • the decoupled mass part that is to say a component which is already present for the operation of the decanter, is separated insofar as 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 it will be preferred to use this suspension to change the oscillating mass, less the mass of the decoupled part itself, which cannot be changed arbitrarily due to its function. It is important that the decoupled Mass part with respect to its natural frequency or set-up frequency with respect to the machine bed and thus the remaining components of the mass system dimensioned or adjusted in its elastic suspension so 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 set-up 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 above 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 vibration 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 that occur on the worm due to the solid load are particularly harmful to the gear unit because, after the occurrence of corresponding voltages, 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 in a resilient manner, 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 regulation 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 matches 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 screw 4, which are connected to one another via a differential speed gear 5 in such a way that the screw 4, depending on the right or left-hand pitch of its helix or Direction of rotation of the drum 3 moves slower or faster than this, in any case so that a solid settling on the drum inner wall 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 connected directly to the drum or 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 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 from the zone 12 to the circumference seen over the bridges 10 between the breakthroughs 9 result in appropriately long material webs 11.
  • 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 via friction losses.
  • FIG 3 shows such an example using a drive motor 6, which with the help of so-called vibrating metals, i. 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 vibrations between the screw and drum to be absorbed by these measures being thereby caused by the solids which accumulate in each case are that the worm is frictionally inclined to reduce its differential speed relative to the drum and corresponding forces are stored in the gearbox 5 until it suddenly accelerates due to its elasticity the worm relative to the drum.
  • 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 spiral, 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 oscillation, for example the oscillation 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 tuning 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.

Landscapes

  • Centrifugal Separators (AREA)

Claims (11)

  1. Décanteur servant à séparer une suspension en une phase solide et en une ou plusieurs phases liquides, constitué des composants suivants, à savoir un tambour (3), un transporteur à vis (4), une transmission (5) et un moteur d'entraînement (6), décanteur dans lequel :
    - le tambour (3) est monté tournant sur le bâti de machine, la vis de transport (4) peut être entraînée en continu à l'intérieur du tambour à une vitesse différente de celle du tambour, la transmission (5) est intercalée entre le tambour (3) et la vis (4),
    - le moteur (6) est relié par la transmission (5) à l'ensemble tournant constitué par le tambour (3) et la vis (4),
    - le décanteur dispose de conduites d'amenée et de sortie de la suspension et/ou des phases solide et liquides, ainsi que d'équipements auxiliaires montée également sur le bâti de machine (1),
    caractérisé en ce que :
    - au moins un composant (6, 4) est désaccouplé élastiquement des autres composants portés par le bâti de machine (1), au moins selon la direction de déplacement tandis qu'il reste accouplé à ces autres composants par l'intermédiaire d'un organe amortisseur (13, 16, 18) fonctionnant en parallèle avec le désaccouplement élastique,
    - au moins un composant désaccouplé (6, 4) et/ou son support sur le bâti de machine (1) sont respectivement dimensionnés par rapport aux autres composants (1, 3, 4, 5) de manière à être accordés sur une fréquence critique propre au reste de l'installation de décantation, en particulier en ce qui concerne l'élasticité du support.
  2. Décanteur selon la revendication 1,
    caractérisé en ce que
    le moteur d'entraînement (6) est le composant monté sur le bâti (1), qui est désaccouplé autant que possible des autres composants.
  3. Décanteur selon la revendication 1 ou 2,
    caractérisé en ce que
    le composant (1, 3, 4, 5), en particulier le moteur (6) est monté sur une paroi à membrane (8) qui, par la présence d'ouvertures concentriques à la zone de maintien (12) du composant (6), est flexible perpendiculairement à son plan, ces ouvertures étant interrompues par des ponts (10) décalés périphériquement de manière à créer des bandes de matière (11) qui, vues radialement à partir de la zone (12) vers l'extérieur, dessinent des méandres imbriqués de longueurs correspondantes.
  4. Décanteur selon la revendication 1 ou 2,
    caractérisé en ce que
    le composant désaccouplé autant que possible des autres composants (1, 3, 4, 5), en particulier le moteur (6) est raccordé au bâti de machine (1) par des pièces élastiques de liaison (métaux vibratiles 14) et comprend éventuellement un tirant (15) servant à encaisser les forces engendrées par la transmission des couples.
  5. Décanteur selon les revendications 1 à 4,
    caractérisé en ce que
    un support désaccouplé est réalisé entre le composant et les autres composants et le bâti de machine, par utilisation d'une matière plastique présentant un frottement interne élevé aux températures de fonctionnement.
  6. Décanteur selon la revendication 1,
    caractérisé en ce que
    un coupleur élastique en rotation (16), équipé en particulier d'un dispositif de frottement jouant le rôle d'organe amortisseur (18), est monté sur la ligne de transmission entre la vis (4) et le tambour (3).
  7. Décanteur selon les revendications 1 ou 6,
    caractérisé en ce que
    la vis (4) peut coulisser élastiquement par rapport au tambour (3), en direction axiale, en particulier avec frottement simultané assuré par un organe amortisseur (18).
  8. Décanteur selon une des revendications 3 à 5,
    caractérisé en ce que
    le composant désaccouplé est le moteur (6) d'entraînement du décanteur (2), le dispositif de transmission du couple étant constitué de courroies (20) dont la tension est assurée par la paroi à membrane agissant en désaccouplement dans toutes les autres directions de forces.
  9. Décanteur selon une des revendications 1 à 5,
    caractérisé en ce que
    le composant désaccouplé est le moteur (6) du décanteur, monté coaxialement à celui-ci, ce moteur ne pouvant tourner autour de son axe grâce à un montage essentiellement non élastique, par exemple, dans le cas d'un montage sur des pieds vibratiles en métal (14), au moyen d'un tirant (15) reliant le carter du moteur au bâti de machine (1).
  10. Décanteur selon une des revendications 1 à 9,
    caractérisé en ce que
    un dispositif d'analyse des vibrations commande le réglage des fréquences propres et de montage du composant (6, 4) déconnecté du reste du système massique, en fonction de la fréquence analysée.
  11. Décanteur selon la revendication 10,
    caractérisé en ce que
    le dispositif d'analyse des vibrations est placé sur la suspension reliant le tambour au bâti, un dispositif hydraulique de réglage commandant la caractéristique élastique du support du moteur sur le bâti de machine.
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
DE3844407 1988-12-30
DE3844406 1988-12-30
DE3844407 1988-12-30
DE3844406 1988-12-30

Publications (3)

Publication Number Publication Date
EP0376919A2 EP0376919A2 (fr) 1990-07-04
EP0376919A3 EP0376919A3 (fr) 1991-05-02
EP0376919B1 true 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
CN101247893B (zh) * 2005-08-26 2010-12-08 巴工业株式会社 滗析器型离心分离机
CN103221140B (zh) * 2010-09-13 2015-05-20 希勒有限责任公司 螺旋运输离心式分离器中的驱动装置
DE102011002126A1 (de) * 2011-04-18 2012-10-18 Gea Mechanical Equipment Gmbh Zentrifuge und Verfahren zur Überwachung eines Drehmoments

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE499434A (fr) * 1949-11-18
GB894311A (en) * 1959-04-23 1962-04-18 Lewis Appliance Corp Ltd Improvements in centrifugal dryers
GB955532A (en) * 1961-07-11 1964-04-15 Monsanto Chem Australia Ltd Improvements relating to industrial centrifuges
CA1072066A (fr) * 1976-07-06 1980-02-19 Karl G. Reed Centrifugeuse verticale a roulement amortisseur
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
DE3142779C2 (de) * 1981-10-28 1986-03-20 Werner Prof. Dr. 6740 Landau Stahl Vollmantel-Schnecken-Zentrifuge

Also Published As

Publication number Publication date
DK0376919T3 (da) 1997-04-28
EP0376919A2 (fr) 1990-07-04
US5120298A (en) 1992-06-09
EP0376919A3 (fr) 1991-05-02
DE59010695D1 (de) 1997-05-15

Similar Documents

Publication Publication Date Title
DE19527614B4 (de) Dynamischer Dämpfer vom Doppelmassen-Typ, der zwei miteinander verbundene Dämpfersysteme hat, und mit dem dynamischen Dämpfer ausgerüstete Antriebswelle
DE19733478B4 (de) Schwingungsdämpfer für eine rohrförmige Gelenkwelle
DE3635702C2 (fr)
EP0301190B1 (fr) Amortisseur d'oscillations, en particulier pour machines à laver
DE2127433B2 (de) Unwuchterreger zum antrieb einer schwingrinne oder eines schwingsiebes
DE4314440C1 (de) Zentrifugalseparator mit Schwerstanlauf
DE69820920T2 (de) Abgestimmter Schwingungsdämpfer mit doppelten Biegeelementen
DE6609011U (de) Haushaltswasch- oder schleudermaschine
EP2063998B1 (fr) Centrifugeuse à rotor à axe de rotation horizontal
EP0376919B1 (fr) Décanteur à élément de construction suspendu élastiquement
DE10326037B4 (de) Mittellager-Resonanzdämpfer
DE3700589C2 (de) Schwingungsdämpfer
EP0654619A1 (fr) Suspension pour élément vibrateur
EP2699355B1 (fr) Centrifugeuse et procédé pour contrôler un couple
DE10034266B4 (de) Zentrifuge
DE2746348C2 (fr)
DE102007004449A1 (de) Stützvorrichtung für einen Wickelkopf sowie damit ausgestatteter Stator und Verfahren zum Umrüsten eines Stators
EP1881220A1 (fr) Disque d'embrayage pour un embrayage à friction
WO2022008246A1 (fr) Entraînement de broche pour un actionneur d'un dispositif de direction à direction par câble d'un véhicule à moteur et dispositif de direction à direction par câble
EP0764796A2 (fr) Support à amortissement hydraulique
EP0733406B1 (fr) Centrifugeuse avec unité d'entraínement et un moyen de transmission sans fin
DE4439153A1 (de) Trommelwaschmaschine mit einem schwingend befestigten Waschaggregat
DE102019113895A1 (de) Elastomerlager zur Anbringung eines Aggregats in einem Kraftfahrzeug
EP2491270B1 (fr) Dispositif pour l'amortissement des vibrations dans un mécanisme de transmission
DE102004035128A1 (de) Prüfvorrichtung und Verfahren zum Prüfen von Fahrzeug-Stabilisatoren

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

RBV Designated contracting states (corrected)

Designated state(s): DE DK FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL

17P Request for examination filed

Effective date: 19911029

17Q First examination report despatched

Effective date: 19921126

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

ITF It: translation for a ep patent filed

Owner name: SOCIETA' ITALIANA BREVETTI S.P.A.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE DK FR GB IT

ET Fr: translation filed
REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

REF Corresponds to:

Ref document number: 59010695

Country of ref document: DE

Date of ref document: 19970515

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19970707

PLBQ Unpublished change to opponent data

Free format text: ORIGINAL CODE: EPIDOS OPPO

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: ALFA LAVAL AB

Effective date: 19980108

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

PLBO Opposition rejected

Free format text: ORIGINAL CODE: EPIDOS REJO

APAC Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPO

APAE Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOS REFNO

APAC Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPO

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20020103

Year of fee payment: 13

APAC Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPO

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 20020910

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030102

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20030102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050102

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20090116

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20081127

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090129

Year of fee payment: 20

REG Reference to a national code

Ref country code: DK

Ref legal event code: EUP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20100102