EP2002126B1 - Pompe centrifuge à accouplement magnétique coaxial - Google Patents

Pompe centrifuge à accouplement magnétique coaxial Download PDF

Info

Publication number
EP2002126B1
EP2002126B1 EP07723756A EP07723756A EP2002126B1 EP 2002126 B1 EP2002126 B1 EP 2002126B1 EP 07723756 A EP07723756 A EP 07723756A EP 07723756 A EP07723756 A EP 07723756A EP 2002126 B1 EP2002126 B1 EP 2002126B1
Authority
EP
European Patent Office
Prior art keywords
pump
pump according
impeller
rotary pump
magnetic
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.)
Not-in-force
Application number
EP07723756A
Other languages
German (de)
English (en)
Other versions
EP2002126A2 (fr
Inventor
Werner Platt
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.)
H Wernert and Co OHG
Original Assignee
H Wernert and Co OHG
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 H Wernert and Co OHG filed Critical H Wernert and Co OHG
Priority to EP08003862A priority Critical patent/EP1965081B1/fr
Publication of EP2002126A2 publication Critical patent/EP2002126A2/fr
Application granted granted Critical
Publication of EP2002126B1 publication Critical patent/EP2002126B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/048—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/025—Details of the can separating the pump and drive area
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/026—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller bearings

Definitions

  • the invention relates to a centrifugal pump having the features of the preamble of claim 1, as shown in EP-B1-0171515 is known.
  • centrifugal pumps with magnetic coupling represent an important type of industrially used machines for the conveyance of liquids. Compared to the simpler centrifugal pumps with mechanical seal they have the advantage of a hermetic seal of the pump chamber. This makes them especially favorable for the promotion of aggressive or toxic liquids.
  • the component referred to below as the pump housing (1) must in practice be made up of several parts. Some of them are wetted by the liquid to be pumped and must be sealed accordingly, others not.
  • the pump housing (1) is here shown in one piece.
  • a first known pump in conventional design is in FIG. 1 and is advertised, for example, in the brochure [1].
  • a rotating pump impeller (4') is arranged, which receives the liquid to be conveyed via the suction nozzle (2 ') and ejects via the discharge nozzle (3') again under pressure.
  • the radial bearing of the pump impeller (4 ') takes place by means of an impeller shaft (5') usually in plain bearings (9 ', 10'), the fixed parts in a bearing insert (11 ') are added.
  • the lubrication and cooling of the sliding bearing (9 ', 10') takes place by the liquid to be pumped itself.
  • This is equipped with permanent magnets (7 '), which in turn must be surrounded before the corrosive and possibly also abrasive attack of the pumped liquid with a cylindrical protective jacket (8') liquid-tight. It should be mentioned only marginally that it may be necessary to protect an approximately metallic, that is to say ferromagnetic, magnet rotor (6 ') from corrosion as well as the shaft (5').
  • the part of the rotary coupling which receives and transmits the driving torque of the motor via the drive shaft (15 ') is commonly referred to as a magnet driver (13'). He is also equipped accordingly with permanent magnets (14 '), but rotate in air and therefore are not subject to any special attack.
  • the radial and axial bearing of the magnetic drive takes place in commercial rolling bearings (16 ').
  • FIG. 2 Another common design, especially for smaller pumps, shows FIG. 2 , Such a pump is advertised eg in [2].
  • a bearing insert (11 ') can be inexpensively eliminated.
  • the pump impeller (4 ') is combined with the magnet rotor (6'), the permanent magnet (7 ') and the protective jacket (8') to a part.
  • This rotating impeller magnetic rotor unit (19 ') is slidably mounted here on a fixed axle (17').
  • the axis (17 ') itself is fastened on one side via flow ribs (18') in the suction nozzle (2 '), supported on the other side in the specially shaped containment shell (12').
  • type A largely conventional construction
  • the magnet driver (13 ') is arranged radially outwardly over the further inside magnetic rotor (6').
  • This design has the advantage that the high moment of inertia of the outside magnet driver (13 ') counteracts the too rapid startup of the driving motor and thus the tearing of the magnetic coupling can be prevented more favorable.
  • this design facilitates in particular a generously axially spaced radial bearing of the pump impeller (4 '), which is always desirable due to the high hydraulic forces within the pump.
  • magnetic coupling pumps with a magnet rotor (6 ') located radially on the outside, which is in contact with the liquid, and an internal magnetic driver (13') are less frequently used.
  • This embodiment is referred to as type B.
  • Such pumps of type B for example, in the DE 01453760 or EP 0171514 or EP 0171515 , are described and in FIG. 3 are shown, must be carefully designed so that the magnetic coupling does not break during rapid startup, which threatens here due to the outside magnetic rotor (6 '). Furthermore, the radially inner magnet driver (13 ') obstructs an axially pulled-out inner slide bearing of the impeller magnetic rotor unit (19'), if not the containment shell (12 '), with its actual opening in the type B drive side must be facing the pump, adversely wound right is executed.
  • An executed pump type B is advertised in [3] and served as a template for the FIG. 3 , That here in contrast to the construction entspr.
  • the present invention seeks to improve the radial bearing in the magnetic coupling of a generic centrifugal pump.
  • a centrifugal pump with the features of claims 1 or 3 is proposed.
  • the fixed part of the slide bearing is arranged on the inside wall surface of the pump housing as a whole or is formed independently by the housing wall or sections of the housing wall of the pump housing, high radial bearing forces can be transmitted over a large axial length and a smooth synchronization of the impeller magnet rotor Unit can be achieved.
  • these are preferably located approximately at the same radial level in order to further improve the running characteristics and the dry running capability of the bearing.
  • radial bearing forces can also be absorbed on the pump impeller, e.g. to achieve an improvement of runflat and / or starting properties. However, best synchronization conditions are achieved if the pump impeller can be rotated radially without contact or force.
  • the sliding bearing of the impeller magnetic rotor unit is carried out in its rotating part as a continuous sleeve, optionally in the form of a molding compound, thereby best possible material pairings and protection of the permanent magnets of the magnet rotor can be improved or simplified.
  • the rotating part of the sliding bearing of the impeller magnetic rotor unit has recesses or elevations on its outer circumference, thereby the sliding properties improving liquid movements can be generated.
  • outside wall of the pump housing is provided in the region of the fixed part of the sliding bearing of the impeller magnetic rotor unit with cooling fins or a cooling jacket, overheating-related bearing damage can be avoided.
  • the pump housing wall has a multilayer structure and the innermost material layer consists of a corrosion- or abrasion-resistant material, the longevity is improved even with difficult pumped media.
  • centrifugal pump is independent of claim 1 of independent inventive importance.
  • the magnet driver has at least one arranged in the region of the interior of the impeller magnetic rotor unit bearing, thereby the pump length can be significantly reduced despite independent storage of the magnetic driver within the pump.
  • the magnetic drive bearing bearings are preferably used.
  • the rolling bearing of the magnetic driver remains unaffected by the pumped liquid.
  • the magnet driver preferably has an open towards the drive side cup shape to receive the at least one bearing of the magnet rotor within the pump housing.
  • a particularly advantageous mounting of the magnetic driver is achieved by a hollow hollow cantilever, through which the drive shaft of the magnet driver is guided, and which preferably carries on at least one inner or outer surface at least one of its end portions a bearing for the magnetic driver. Tapering in these end areas facilitate the placement of such bearings in a small space. When the taper is made from the root of the cantilever, high bearing forces can be absorbed in a lightweight construction.
  • the at least partial storage of the magnetic driver within the space defined by the impeller magnetic rotor unit and the embodiments of such storage are of independent inventive significance.
  • the embodiments have in common that they have a suction nozzle 2 and a discharge nozzle 3 exhibiting pump housing 1, wherein a pump impeller 4 is mounted coaxially with the suction nozzle and is fluidly connected in the radial direction with the discharge nozzle 3.
  • the pump impeller 4 has on the drive side a magnetic rotor 6, with which it forms an open to the drive side impeller magnetic rotor unit. This has on its outer circumference the rotating part 9 of a slide bearing, while the fixed part 10 of this sliding bearing is arranged on the inner wall 20 of the pump housing 1.
  • On the radially inner side of the magnet rotor carries 6 permanent magnets 7.
  • a continuous hollow Kragzapfen 39 from the drive-side housing end wall to the pump side down and has a tapered design 39a, 39b, wherein at its drive end portion which penetrates the drive shaft 15 of the pump is roller-mounted, while a second roller bearing in the opposite end on his Outside the drive shaft 15 indirectly, namely superimposed on the magnet driver 13.
  • the latter has for this purpose on the drive side open cup shape.
  • the fixed part 10 of the plain bearing can readily be brought directly to the stable inner housing wall 20 of the pump housing 1 ( FIG. 5 , upper half) and no longer has to be disadvantageous the basically thin wall of the can 12, as described in [4]. It is even possible, with a suitable choice of the material and with appropriate shaping, that parts of the housing wall 20 of the pump housing 1 itself can become the stationary part of the sliding bearing 10 ( FIG. 5 , lower half), possibly only by a multi-layered design.
  • An arrangement according to claim 1 not only offers significant technological advantages, but also leads to an extremely simple construction of the entire pump.
  • the slide bearing 9, 10 is arranged exactly here, which can be operated as long as desired with the residual liquid with sufficient cooling.
  • very small residual amounts which tend to occur at high delivery heights of the pump and low static counter-pressure, it can not be ruled out that these can escape axially in order to move to even higher radial levels in the impeller. This can be prevented via a lock in the form of a circulating ring 21, in FIG. 6 is shown.
  • the invention can also be exploited to significantly shorten the axial extent of the pump.
  • This is usually an electric motor.
  • the electric motor is flanged directly to the pump, which is known as "block construction".
  • Advantage of this construction is in addition to the effect of axial shortening the savings of the two bearings 16.
  • the disadvantage of this design is that the magnet driver 13 is no longer part of the pump and thus complete assembly of the pump can only be done if the driving motor present is.
  • its size is initially at least in industrial pumps an unknown size and will be determined only on the basis of customer information.
  • the time of final assembly of the pump is necessarily relocated behind this time and is also still an individual assembly with the known economic disadvantages.
  • a, preferably detachable, split pot 12 introduced, as it always finds use in industrial pumps.
  • these splitters are made very thin-walled on the circumference in order to realize the smallest possible radial gap between the magnet rotor 6 and magnet driver 13 can.
  • the containment shell 12 can be designed with a smooth end wall and must point with its larger opening in the direction of the drive side.
  • the split pot 12 itself should not be used to support a rolling bearing because of its thinness, but now offers according FIG. 7 In this way, the axial Baumass the pump can be shortened to that of the conventional block design, but here the magnet driver 13 remains part of the pump, resulting in a complete series assembly and stockpiling of the pump allowed.
  • the shaft end 25 in such an axially shortened construction can advantageously according to FIG. 8 be carried out so that either via a conventional pump clutch (shown only the pin portion 27 of the pump clutch) the direct connection of a motor is possible (which could be flanged via an intermediate ring also directly to the pump) or a shaft journal 28 again with the conventional pump free shaft end leads (eg to comply with specified standard dimensions).
  • a shaft end 25 should provide the opportunity to attach an additional flywheel 26 to compensate for the mentioned disadvantage of the type B chosen here when starting the pump can. All this would be part of the final assembly of the pump unit (which would also be carried out by the user of the pump itself) and would still allow a large-scale series assembly and cheap stockpiling of the pump at the manufacturer as described above.
  • the rotating part 9 of the plain bearing need not necessarily consist of two defined bearing sleeves a and b or from the magnet rotor 6 itself, but can FIG. 9 also as an axially continuous sleeve 29 (FIG. FIG. 9 , upper half) or molding compound 30 ( FIG. 9 , lower half).
  • the supply of external lubricating fluid is loud FIG. 13 and / or a sensory monitoring (eg temperature, vibration, structure-borne noise) of the sliding bearing 9, 10 loud FIG. 14 proposed.
  • a sensory monitoring eg temperature, vibration, structure-borne noise
  • FIG. 15 makes this construction also for the present invention. Since in particular the mentioned plastic materials (eg PTFE or PE) can be used very well as a sliding bearing material in mixed friction area, a construction is proposed, as they FIG. 15 in the lower half shows. If, on the other hand, the material of the innermost material layer 35 is not suitable for plain bearings, the construction in the upper half of FIG FIG. 15 recourse.
  • plastic materials eg PTFE or PE

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Claims (21)

  1. Pompe centrifuge,
    - comportant, à l'intérieur de la pompe en forme de carter (1), une enceinte statique et fermée pour le liquide à mettre en circulation,
    - comportant un accouplement rotatif (6, 7 ; 13, 14) coaxial à aimants permanents, destiné à transmettre un couple d'entraînement vers l'intérieur du carter de la pompe,
    - comportant une roue mobile (4) qui, conjointement avec un rotor magnétique (6), portant des aimants permanents (7), forme une unité en forme de pot (unité 19 à roue mobile et rotor magnétique), ouverte vers le côté entraînement et montée dans un palier lisse,
    - et dans laquelle les lignes d'action magnétiques de la partie motrice de l'accouplement rotatif (organe d'entraînement magnétique 13 et aimants permanents 14) sont dirigés radialement vers l'extérieur et les lignes d'action magnétique de la partie de l'accouplement rotatif (rotor magnétique 6 et aimants permanents 7), reliée à la roue mobile (4), sont dirigés radialement vers l'intérieur,
    caractérisée en ce que pour le montage radial de l'unité (19) à roue mobile et rotor magnétique,
    - la partie rotative (9 ; 9a, 9b) d'un palier lisse est montée dans son ensemble le long de la périphérie extérieure (38) du rotor magnétique (6) et est reliée de manière solidaire à celui-ci ou est formée elle-même par la périphérie extérieure ou des portions de la périphérie extérieure (38) du rotor magnétique (6).
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que la partie fixe (10 ; 10a, 10b) du palier lisse est agencée sur la paroi (20) intérieure du carter (1) de la pompe ou est formée elle-même par la paroi ou des portions de la paroi (20) du carter (1) de la pompe.
  3. Pompe centrifuge selon la revendication 1 ou 2, dans laquelle sont prévus plusieurs parties de palier lisse (9a, 10a ; 9b, 10b), situées à distance axiale les unes des autres et situées sensiblement sur le même niveau radial.
  4. Pompe centrifuge selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la roue mobile (4) de la pompe est montée rotative radialement sans contact ou sans rotation forcée.
  5. Pompe centrifuge selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'entre la roue mobile (4) de la pompe et le palier lisse (9, 10) est montée une bague (21) rotative ou une bride, de telle sorte que la dimension intérieure de celle-ci est inférieure au diamètre de contact du palier lisse (9, 10) et, de ce fait, il se forme une chambre de retenue de liquide (22) dans la zone du palier lisse (9, 10) tant pendant la rotation que pendant l'immobilisation de la roue mobile (4) de la pompe.
  6. Pompe centrifuge selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la partie rotative (9 ; 9a, 9b) du palier lisse est réalisée sous la forme d'un manchon (29) à passage axial ou sous la forme d'une masse profilée (30), moulée ou pressée, à passage axial.
  7. Pompe centrifuge selon la revendication 6, caractérisée en ce que le manchon (29) ou la masse profilée (30) sont ou seront posées, formées ou étanchées par des moyens d'étanchéité (36), de telle sorte qu'ils font partie d'une enveloppe de protection (8) pour les aimants permanents (7) et/ou le rotor magnétique (6).
  8. Pompe centrifuge selon l'une quelconque des revendications 1 à 7, caractérisée en ce que la partie rotative (9 ; 9a, 9b) du palier lisse comporte sur sa périphérie extérieure une pluralité d'évidements (31) ou bosses locaux, qui favorisent le développement de tourbillons hydrauliques stabilisants dans le palier lisse.
  9. Pompe centrifuge selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la paroi extérieure du carter (1) de la pompe comporte des nervures de refroidissement (32) dans la zone de la partie fixe (10) du palier lisse.
  10. Pompe centrifuge selon l'une quelconque des revendications 1 à 9, caractérisée en ce que la partie fixe (10) du palier lisse peut être alimentée en lubrifiant externe par l'intermédiaire d'un ou de plusieurs accès (33) dans la paroi du carter (1) de la pompe.
  11. Pompe centrifuge selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la partie fixe (10) du palier lisse peut être surveillée par capteurs par l'intermédiaire d'un ou de plusieurs accès (34) dans la paroi du carter (1) de la pompe.
  12. Pompe centrifuge selon l'une quelconque des revendications 1 à 11, caractérisée en ce que la paroi du carter (1) de la pompe est formée par plusieurs couches de matière et la couche intérieure (35) est réalisée dans un matériau résistant à la corrosion et/ou à l'abrasion.
  13. Pompe centrifuge selon l'une quelconque des revendications 1 à 12, dans laquelle une cloison est montée entre le rotor magnétique (6) et l'organe d'entraînement magnétique (13), laquelle est orientée avec son ouverture vers le côté entraînement de la pompe et fait la séparation entre le liquide à l'intérieur de la pompe et l'organe d'entraînement magnétique (13), caractérisée
    - en ce que l'organe d'entraînement magnétique (13) est monté dans au moins un palier relié à la pompe, tel qu'un palier à roulements (16),
    - en ce qu'au moins un palier du côté de la roue mobile, tel qu'un palier à roulements (16a), se situe dans la zone intérieure (24) du carter de la pompe, et
    - le montage de l'organe d'entraînement magnétique (13) est réalisé sans contact avec la cloison.
  14. Pompe centrifuge selon la revendication 13, caractérisée en ce que ledit au moins un palier du côté de la roue mobile se situe dans la zone intérieure d'un organe d'entraînement magnétique (13) creux à l'intérieur.
  15. Pompe centrifuge selon la revendication 13 ou 14, caractérisée en ce que la bague intérieure est immobilisée par le palier du côté roue mobile et la bague extérieure associée tourne avec l'organe d'entraînement magnétique (13) monté dans le palier.
  16. Pompe centrifuge selon la revendication 15, caractérisée en ce qu'il est prévu un palier du côté roue mobile, tel qu'un palier à roulements (16b), dont la bague intérieure tourne avec l'arbre d'entraînement (15) monté dans le palier et la bague extérieure associée est immobilisée.
  17. Pompe centrifuge selon l'une quelconque des revendications 13 à 16, caractérisée en ce qu'il est prévu un tourillon (39) en porte-à-faux, creux de part en part, lequel s'engage dans le carter (1) de la pompe depuis le côté entraînement, est destiné à recevoir l'arbre d'entraînement (15) et est relié ou peut être relié au carter de la pompe.
  18. Pompe centrifuge selon la revendication 17, caractérisée en ce que le tourillon creux (39) en porte-à-faux comporte un rétrécissement (39a ; 39b) dans au moins l'une de ses zones d'extrémité.
  19. Pompe centrifuge selon l'une quelconque des revendications 13 à 18, caractérisée en ce que la zone de l'extrémité (25) de l'arbre d'entraînement (15), du côté entraînement, est réalisée de telle sorte qu'elle comporte une masse d'inertie (26) ou peut être munie de celle-ci.
  20. Pompe centrifuge selon l'une quelconque des revendications 13 à 19, caractérisée en ce que la zone de l'extrémité (25) de l'arbre d'entraînement (15), du côté entraînement, est réalisée de telle sorte qu'elle peut être assemblée de manière amovible au choix à une masse d'inertie (26), une partie de tourillon (27) d'un accouplement de la pompe et/ou un tourillon d'arbre (28).
  21. Pompe centrifuge selon l'une quelconque des revendications 13 à 20, caractérisée en ce que l'organe d'entraînement magnétique (13) a une forme de pot ouvert vers le côté entraînement.
EP07723756A 2006-03-31 2007-03-29 Pompe centrifuge à accouplement magnétique coaxial Not-in-force EP2002126B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08003862A EP1965081B1 (fr) 2006-03-31 2007-03-29 Pompe centrifuge dotée d'un embrayage magnétique coaxial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202006005189U DE202006005189U1 (de) 2006-03-31 2006-03-31 Kreiselpumpe mit koaxialer Magnetkupplung
PCT/EP2007/002814 WO2007112938A2 (fr) 2006-03-31 2007-03-29 Pompe centrifuge à accouplement magnétique coaxial

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP08003862A Division EP1965081B1 (fr) 2006-03-31 2007-03-29 Pompe centrifuge dotée d'un embrayage magnétique coaxial
EP08003862.3 Division-Into 2008-03-01

Publications (2)

Publication Number Publication Date
EP2002126A2 EP2002126A2 (fr) 2008-12-17
EP2002126B1 true EP2002126B1 (fr) 2010-06-23

Family

ID=38375284

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08003862A Not-in-force EP1965081B1 (fr) 2006-03-31 2007-03-29 Pompe centrifuge dotée d'un embrayage magnétique coaxial
EP07723756A Not-in-force EP2002126B1 (fr) 2006-03-31 2007-03-29 Pompe centrifuge à accouplement magnétique coaxial

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08003862A Not-in-force EP1965081B1 (fr) 2006-03-31 2007-03-29 Pompe centrifuge dotée d'un embrayage magnétique coaxial

Country Status (9)

Country Link
US (1) US8162630B2 (fr)
EP (2) EP1965081B1 (fr)
JP (1) JP5461172B2 (fr)
KR (1) KR101410628B1 (fr)
CN (1) CN101415950B (fr)
AT (2) ATE472060T1 (fr)
DE (3) DE202006005189U1 (fr)
ES (1) ES2335946T3 (fr)
WO (1) WO2007112938A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060549A1 (de) * 2009-12-23 2011-06-30 Wilo Se, 44263 EC-Motorkreiselpumpe

Families Citing this family (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007054233B4 (de) 2007-11-12 2010-06-10 Ika-Werke Gmbh & Co. Kg Vorrichtung zum Dispergieren oder Homogenisieren
ES2776709T3 (es) 2007-11-21 2020-07-31 Smith & Nephew Apósito para heridas
DE102008008290A1 (de) 2008-02-07 2009-08-20 H. Wernert & Co. Ohg Laufradanordnung für eine Pumpe sowie Verfahren zum Herstellen einer solchen Laufradanordnung
JP4681625B2 (ja) 2008-02-22 2011-05-11 三菱重工業株式会社 血液ポンプおよびポンプユニット
EP2180583B1 (fr) * 2008-10-24 2012-08-08 Biazzi Sa Appareillage à cuve d'agitation
KR100935707B1 (ko) * 2009-04-30 2010-01-07 케이이티주식회사 마그네틱 구동 시일리스 펌프
KR100990096B1 (ko) 2009-06-04 2010-10-29 강선희 마그네트모듈이 적용된 물품 이송시스템
MX341039B (es) * 2010-04-19 2016-08-04 Kolektor Magnet Tech Gmbh Bomba de refrigerante para automovil electrica.
JP4875783B1 (ja) * 2011-09-15 2012-02-15 三菱重工業株式会社 磁気カップリングポンプ及びこれを備えているポンプユニット
TW201317459A (zh) * 2011-10-26 2013-05-01 協磁股份有限公司 永磁罐裝泵結構改良
CN102352848A (zh) * 2011-10-31 2012-02-15 神华集团有限责任公司 磁力泵
TW201320547A (zh) * 2011-11-03 2013-05-16 Assoma Inc 磁驅動泵浦之結構改良
PL2604863T3 (pl) * 2011-12-13 2017-12-29 Eagleburgmann Germany Gmbh & Co. Kg Sprężarka rotacyjna
US8651240B1 (en) 2012-12-24 2014-02-18 United Technologies Corporation Pressurized reserve lubrication system for a gas turbine engine
US8905729B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with electro-magnet coupling inside the impeller
US8905728B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with permanent magnet coupling inside the impeller
CN102931810A (zh) * 2012-11-27 2013-02-13 镇江市江南矿山机电设备有限公司 轴间永磁耦合机构
CN103023241A (zh) * 2012-11-27 2013-04-03 镇江市江南矿山机电设备有限公司 轴间永磁耦合机构
CN102931809A (zh) * 2012-11-27 2013-02-13 镇江市江南矿山机电设备有限公司 轴间永磁耦合机构
CN103401396B (zh) * 2013-06-14 2016-07-06 宝鸡泰华磁机电技术研究所有限公司 内辐射环式永磁联轴器
KR101828544B1 (ko) * 2013-12-13 2018-03-29 한화파워시스템 주식회사 압축기 어셈블리
US9771938B2 (en) 2014-03-11 2017-09-26 Peopleflo Manufacturing, Inc. Rotary device having a radial magnetic coupling
HK1255306A1 (zh) * 2015-08-05 2019-08-16 W‧斯皮塞 磁力驱动的无密封泵
DE102016200013B4 (de) 2016-01-04 2022-11-03 Röchling Automotive SE & Co. KG Pumpe
CN107327570B (zh) * 2016-04-28 2018-10-19 哈尔滨歌瑞得莱机器人制造有限公司 同步双磁环驱动密封装置
CN109416058B (zh) 2016-07-04 2021-05-07 阿莫泰克有限公司 水泵
WO2018008896A1 (fr) * 2016-07-04 2018-01-11 주식회사 아모텍 Pompe à eau
DE202016105312U1 (de) * 2016-09-23 2018-01-09 Speck Pumpen Verkaufsgesellschaft Gmbh Förderpumpe
EP3523539B1 (fr) * 2016-11-01 2020-08-12 PSG Worldwide, Inc. Pompe centrifuge sans joint à entraînement magnétique
NO344365B1 (en) * 2017-12-21 2019-11-18 Fsubsea As Magnetic coupling assembly
DE102017220437B8 (de) * 2017-11-16 2019-06-19 Eagleburgmann Germany Gmbh & Co. Kg Pumpenanordnung, insbesondere zur Versorgung einer Gleitringdichtungsanordnung
DE102017127736A1 (de) * 2017-11-23 2019-05-23 Manfred Sade Magnetpumpe mit Gleitringdichtung
US10047717B1 (en) * 2018-02-05 2018-08-14 Energystics, Ltd. Linear faraday induction generator for the generation of electrical power from ocean wave kinetic energy and arrangements thereof
DE102018102740A1 (de) * 2018-02-07 2019-08-08 Lsp Innovative Automotive Systems Gmbh Außenstator für eine Drehfeldmaschine (E-Motor) mit einem Innenrotor, mit Statorzahngruppen, welche jeweils zwei zueinander benachbarte Statorzähne aufweisen
CN108462366A (zh) * 2018-03-30 2018-08-28 湖南铁路科技职业技术学院 适用于铁路货车的圆柱与圆锥混合型同轴式磁力密封装置
US10947986B2 (en) 2018-07-11 2021-03-16 Ch Biomedical (Usa) Inc. Compact centrifugal pump with magnetically suspended impeller
CN109067138A (zh) * 2018-08-27 2018-12-21 广西科技大学 一种新型混合式永磁传动装置
DE102018129613A1 (de) * 2018-11-23 2020-05-28 Ebm-Papst St. Georgen Gmbh & Co. Kg Radiallüfter mit integrierter Kühlfunktion
GB2581339A (en) * 2019-02-08 2020-08-19 Hmd Seal/Less Pumps Ltd Containment shell for a magnetic pump
KR102817631B1 (ko) * 2019-04-18 2025-06-10 한화파워시스템 주식회사 회전 기기
DE102019122042A1 (de) * 2019-08-16 2021-02-18 HELLA GmbH & Co. KGaA Pumpvorrichtung
EP3795836B1 (fr) * 2019-09-18 2024-11-27 Levitronix GmbH Pompe centrifuge
DE102020202781A1 (de) * 2020-03-04 2021-09-09 Siemens Aktiengesellschaft 8Elektromotor mit Spaltrohr
DE202020101750U1 (de) * 2020-03-31 2020-04-15 Speck Pumpen Verkaufsgesellschaft Gmbh Gegenstromschwimmanlage
CN114263637B (zh) * 2021-12-30 2024-01-02 浙江启尔机电技术有限公司 一种磁力联轴器温度控制系统及采用其的磁力泵
EP4539307A4 (fr) * 2022-06-08 2025-08-27 Panasonic Ip Man Co Ltd Moteur à engrenage magnétique et engrenage magnétique
CN117703777B (zh) * 2023-12-12 2024-10-18 安徽星球盛唐泵业有限公司 耐腐蚀耐高温磁力泵
CN119737318B (zh) * 2024-12-19 2025-10-28 西安交通大学 一种轴流式高温液态金属磁力泵
CN120312614A (zh) * 2025-06-16 2025-07-15 凯利达科技股份有限公司 一种双支撑轴磁力泵

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1453760A1 (de) 1962-01-08 1969-01-09 Fuss Und Stahl Veredlung Gmbh Pumpe mit einem schnell rotierend angetriebenen Laufrad,insbesondere Kreiselpumpe
FR2311201A1 (fr) * 1975-05-12 1976-12-10 Siebec Filtres Perfectionnement apporte aux pompes a entrainement magnetique
JPS5280101U (fr) * 1975-12-11 1977-06-15
EP0171515B1 (fr) * 1984-07-16 1987-09-02 CP Pumpen AG Pompe centrifuge avec chapeau tubulaire d'isolation de l'entrefer
ATE32931T1 (de) 1984-07-16 1988-03-15 Cp Pumpen Ag Kreiselpumpe mit einem spaltrohrtopf.
JP2636097B2 (ja) * 1991-08-08 1997-07-30 動力炉・核燃料開発事業団 浸漬型電動ポンプにおけるスラスト軸受の摩耗量の監視装置
GB2263312A (en) * 1992-01-17 1993-07-21 Stork Pompen Vertical pump with magnetic coupling.
US5253986A (en) 1992-05-12 1993-10-19 Milton Roy Company Impeller-type pump system
FR2715442B1 (fr) * 1994-01-26 1996-03-01 Lorraine Carbone Pompe centrifuge à entraînement magnétique.
JPH09268994A (ja) * 1996-03-30 1997-10-14 Yoshio Yano 液中軸承のない、マグネットを動力源とするポンプ
GB9717866D0 (en) * 1997-08-23 1997-10-29 Concentric Pumps Ltd Improvements to rotary pumps
DE29822717U1 (de) * 1998-12-21 1999-03-18 Feodor Burgmann Dichtungswerke GmbH & Co, 82515 Wolfratshausen Kreiselpumpe, insbesondere zum Pumpen eines Kühlmittels in einem Kühlmittelkreislauf
JP2001119913A (ja) * 1999-10-21 2001-04-27 Canon Precision Inc 自冷動圧流体軸受ブラシレスモータ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060549A1 (de) * 2009-12-23 2011-06-30 Wilo Se, 44263 EC-Motorkreiselpumpe

Also Published As

Publication number Publication date
EP1965081A1 (fr) 2008-09-03
CN101415950B (zh) 2013-02-06
CN101415950A (zh) 2009-04-22
DE502007004191D1 (de) 2010-08-05
US8162630B2 (en) 2012-04-24
WO2007112938A3 (fr) 2008-04-10
JP5461172B2 (ja) 2014-04-02
US20100028176A1 (en) 2010-02-04
EP2002126A2 (fr) 2008-12-17
KR20080108150A (ko) 2008-12-11
JP2009531589A (ja) 2009-09-03
EP1965081B1 (fr) 2009-11-18
DE502007002031D1 (de) 2009-12-31
KR101410628B1 (ko) 2014-06-20
WO2007112938A2 (fr) 2007-10-11
ATE472060T1 (de) 2010-07-15
ES2335946T3 (es) 2010-04-06
ATE449263T1 (de) 2009-12-15
DE202006005189U1 (de) 2007-08-16

Similar Documents

Publication Publication Date Title
EP2002126B1 (fr) Pompe centrifuge à accouplement magnétique coaxial
EP1801420A2 (fr) Pompe centrifuge à accouplement magnétique
DE102010014800B4 (de) Gekapselte Dauermagnet-Pumpe
EP3127221B1 (fr) Dispositif pour la lubrification du palier à roulement d'un moteur électrique
DE3639719C3 (de) Spaltrohrmagnetpumpe
DE202008002617U1 (de) Anordnung zur Förderung von Fluiden
EP3433496A1 (fr) Pompe à entraînement magnétique
DE102011109930A1 (de) Wälzlager und Vakuumpumpe mit Wälzlager
EP2576996B1 (fr) Turbocompresseur à gaz d'échappement doté de paliers lisses pour diminuer les tourbillons de fluide
EP2557316A2 (fr) Pompe à vide
DE1140595B (de) Fuellungsgeregelte Stroemungskupplung, vorzugsweise fuer den Antrieb eines Bremsluft-kompressors in einem Schienenfahrzeug
EP1979621B1 (fr) Pompe centrifuge à entraînement magnétique pour des milieux corrosifs
EP2322803B1 (fr) Pompe dotée d un embrayage magnétique
DE102008038012A1 (de) Ausgleichswelle sowie Rotationssymmetrie-Ergänzungselement für eine derartige Ausgleichswelle
EP2864640B1 (fr) Pompe centrifuge de moteur pourvue d'une garniture étanche à anneau glissant
EP1727987B1 (fr) Pompe
DE3941444C2 (de) Permanentmagnetantrieb für eine Pumpe, ein Rührwerk oder eine Armatur
WO2014170113A1 (fr) Retardateur comprenant une pompe à vide
EP3536956B1 (fr) Sacs de support
DE102014212600A1 (de) Integrierte Schmierpumpe
EP2667034B1 (fr) Pompe à plusieurs étages
EP2927500B1 (fr) Procédé et système d'alimentation d'une disposition de palier
EP3628873B1 (fr) Logement de rotor
EP2045477B1 (fr) Agencement de stockage destiné au stockage rotatif d'une partie de machine
DE202004013081U1 (de) Spalttopfpumpe

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

17P Request for examination filed

Effective date: 20080301

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20090325

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502007004191

Country of ref document: DE

Date of ref document: 20100805

Kind code of ref document: P

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: E. BLUM & CO. AG PATENT- UND MARKENANWAELTE VSP

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20100623

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

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

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20101025

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20101023

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

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

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100924

26N No opposition filed

Effective date: 20110324

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007004191

Country of ref document: DE

Effective date: 20110323

BERE Be: lapsed

Owner name: H. WERNERT & CO. OHG

Effective date: 20110331

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

Ref country code: MC

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

Effective date: 20110331

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: BE

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

Effective date: 20110331

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 NON-PAYMENT OF DUE FEES

Effective date: 20111001

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 472060

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120329

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

Ref country code: LU

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

Effective date: 20110329

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

Ref country code: AT

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

Effective date: 20120329

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100923

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20101004

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100623

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

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

Ref country code: NL

Payment date: 20170323

Year of fee payment: 11

Ref country code: DE

Payment date: 20170327

Year of fee payment: 11

Ref country code: CH

Payment date: 20170327

Year of fee payment: 11

Ref country code: FR

Payment date: 20170323

Year of fee payment: 11

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

Ref country code: GB

Payment date: 20170327

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007004191

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20180401

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

Effective date: 20180329

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

Ref country code: NL

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

Effective date: 20180401

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: 20180329

Ref country code: LI

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

Effective date: 20180331

Ref country code: CH

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

Effective date: 20180331

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

Ref country code: FR

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

Effective date: 20180331

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 NON-PAYMENT OF DUE FEES

Effective date: 20181002