EP2582983A1 - Pompe centrifuge double flux - Google Patents

Pompe centrifuge double flux

Info

Publication number
EP2582983A1
EP2582983A1 EP11723310.6A EP11723310A EP2582983A1 EP 2582983 A1 EP2582983 A1 EP 2582983A1 EP 11723310 A EP11723310 A EP 11723310A EP 2582983 A1 EP2582983 A1 EP 2582983A1
Authority
EP
European Patent Office
Prior art keywords
impeller
centrifugal pump
gaps
pump
sealing
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
EP11723310.6A
Other languages
German (de)
English (en)
Other versions
EP2582983B1 (fr
Inventor
Manfred Britsch
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.)
Allweiler GmbH
Original Assignee
Allweiler GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Allweiler GmbH filed Critical Allweiler GmbH
Publication of EP2582983A1 publication Critical patent/EP2582983A1/fr
Application granted granted Critical
Publication of EP2582983B1 publication Critical patent/EP2582983B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • 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
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid pumps
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/406—Casings; Connections of working fluid especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a, preferably single-stage, double-flow centrifugal pump, in particular a cooling water pump for a marine diesel engine or a Balastigan practicepumpe on a ship, with a pump housing and with a rotatably driven shaft rotatably mounted double-flight impeller, with which a fluid from two axial sides of a Low pressure region (suction side) is sucked and in the radial direction in a pressure range (pressure side) is conveyed, wherein the negative pressure region is sealed relative to the overpressure region by means of at least two axially spaced (over the pressure range) sealing gaps between the impeller and at least one stationary pump component, in particular the Pump housing are formed.
  • sealing gaps extend in the axial direction and are formed between the impeller and the pump housing.
  • a resulting radial force component acting on the cantilevered shaft occurs, so that the shaft is deflected in the radial direction with the impeller fixed to it in a rotationally fixed manner.
  • the sealing gaps formed as axial gaps must be dimensioned correspondingly broad.
  • centrifugal pumps are suitable, if the shaft is mounted on one side, only for applications in which comparatively low volume flows have to be conveyed.
  • the impeller bearing shaft is usually mounted on both axial sides of the impeller to minimize the radial deflection movement during operation. In a only one-sided storage of the shaft for these applications Wei Wei would have to be used with a correspondingly large diameter and / or complex storage.
  • the present invention seeks to provide a double-flow centrifugal pump, in particular for large volume flows of at least 500m 3 / h, with a high efficiency without complex design measures is possible.
  • the impeller bearing shaft of the centrifugal pump is to be stored exclusively on one side and have the smallest possible diameter. A striking of the impeller on the pump housing should be safely avoided.
  • the sealing gaps are formed as extending in the circumferential direction and in the radial direction axially between the pump member and the impeller arranged axial gaps whose, preferably measured in the axial direction, gap width is greater than the radial distances of Impeller to all components, which are arranged radially spaced radially outside the impeller.
  • the gap width of the sealing gaps designed as axial gaps is greater than the gap widths of all the other gaps (radial gaps) which are delimited on one side by the impeller.
  • the invention is based on the idea that the sealing gaps between the impeller and at least one pump part, with which the suction side of the centrifugal pump is sealed against the pressure side, with respect to their longitudinal extent extending in the radial direction, ie form as an axial gap.
  • the impeller according to the invention by means of the sealing gaps in the axial direction spaced from the at least one, preferably exclusively a pump component.
  • the gap width of the sealing gap is smaller than the radial distance of the impeller to all components of the pumps located radially outside the impeller.
  • the sealing gaps are characterized by the fact that their axial extent is (substantially) less than their radial extent.
  • the gap width of the axial gap (sealing gap) measured in the axial direction is preferably greater than the gap width measured in the radial direction of a radial gap arranged between the impeller and the pump component bounding the axial gap.
  • the gap width of the sealing gaps is at least 20%, preferably at least 12%, more preferably 6% of the radial distance of the impeller 7 to the axial gap limiting Pumpenbauteii, in particular the pump housing and / or, preferably a housing portion forming insert.
  • sealing gaps each formed as an axial gap. It is preferred, however, only one axial gap provided trained sealing gap, which are understood as sealing gaps in each case the column with the smallest gap width.
  • the sealing gaps are arranged in a region radially inwardly of circumferentially closed radial gaps, via which the impeller is spaced from the at least one, preferably only one, pump component. It is particularly preferred if the axial gaps, starting from the radial gaps in the radial direction extend inwards. Particularly preferred is therefore an embodiment variant in which the axial gaps, at least in a radially inner region, have a smaller distance from the shaft than the radial gaps.
  • the sealing gaps are located within an imaginary circular cylinder whose lateral surface receives the radial gaps in itself. Due to such a variant, the sealing effect is improved.
  • the impeller has a circular cylindrical envelope contour, wherein it is even more preferred if the sealing gaps (axial gaps) between each end face of a cylindrical envelope contour having impeller and the at least one, preferably exclusively one, pump component are formed.
  • an envelope contour can also be provided in which the impeller extends with its outlet region farther outward in the radial direction.
  • the axial sealing gap is arranged in a region which has a smaller radius than a possible radial gap, which is arranged between the pump jet and the impeller.
  • the sealing gaps Due to the inventive design of the sealing gaps as axial gaps, it is possible to measure the gap width of the sealing gaps much lower than in the prior art, without the risk that the impeller at a radial deflection abuts on the sealing gap defining pump component. It is thus possible to achieve a high efficiency of the centrifugal pump by the inventive design of the sealing gaps, since the Fiüsstechniksmenge flowing from the pressure range in the suction region (negative pressure region) is minimized by the small gap width of the sealing gaps. In the radial direction, the distance between the impeller and the pump component and / or other components of the pump can be dimensioned so that there is no risk of collision even with the largest possible occurring during operation deflection of the impeller.
  • the sealing gaps - within the tolerances - exactly in relation to their longitudinal extent in the radial direction is also a slightly curved or slightly oblique configuration of the sealing gaps by a corresponding formation of at least one sealing column bounding component (impeller and / or pump component, in particular pump housing) possible, in particular such that the gap geometry of the curved deflection movement of the impeller, especially in one-sided Shaft bearing follows, so that the gap width, regardless of the degree of deflection of the impeller during operation, at least independently remains constant.
  • the radius of curvature at least approximately corresponds to the distance of the impeller to the bearing of the impeller bearing shaft.
  • the gap width of the sealing gaps designed as axial gaps is selected from a value range between 200 ⁇ m and 2000 ⁇ m, very particularly preferably between 200 ⁇ m and 400 ⁇ m. It is particularly useful if the minimum, ie the smallest radial distance of the impeller to the designed as axial sealing Dichtspaite limiting Pumpenbauteii the centrifugal pump (with a stationary impeller) is selected from a range between 2mm to 10mm. In other words, the distance between the impeller and the aforementioned pump component is preferably greater than the distances of the specified range of values.
  • the aforementioned minimum radial distance is not only the minimum radial distance of the impeller to the at least one, preferably only a sealing column defining pump component, but the minimum radial distance of the impeller to all components of the pump to a collision at radial To prevent deflection safely.
  • An embodiment of the double-flow centrifugal pump in which the sealing gaps are arranged between the end faces of the impeller pointing in the axial direction and the at least one pump component is particularly preferred. In other words, it is preferred if the sealing gaps have the greatest possible axial distance from each other. This can for example be realized in that the impeller has an at least approximately circular cylindrical envelope contour.
  • an imaginary circular cylindrical surface receiving the radial gaps encloses the axial gaps radially on the outside.
  • an axial gap (sealing gap) extending in the radial direction is understood to mean not only an embodiment in which the sealing gaps extend exactly in the radial direction with respect to their longitudinal extent, ie they are, for example, annular disk-shaped. It is also an embodiment conceivable in which the sealing gaps have a small pitch angle or are slightly curved, ie have a large radius of curvature, this preferably, at least approximately, in particular for one-sided bearing shaft, the distance of the respective sealing gap of the shaft bearing.
  • the respective sealing gap is then formed so that the gap width during operation of the centrifugal pump, so not with a possible radial deflection of the impeller, or only slightly as possible, since the gap geometry follows the Ausienkamba.
  • the curvature or chamfering of the sealing string can be realized by a corresponding geometric shape of the impeller and / or the at least one, preferably only one, the sealing gaps on the opposite axial side of the impeller pump component.
  • the angle (inclination angle) of the respective sealing gap to an imaginary, arranged orthogonal to the longitudinal extent of the shaft radial plane is selected from a range of values between 0.01 ° and 2.0 °.
  • a possible radius of curvature is selected from a value range between 200 mm and 1000 mm, preferably 300 mm and 700 mm.
  • the radius of curvature of the respective sealing gap, more precisely at least one surface delimiting the sealing gap (the impeller and / or the pump component) preferably corresponds, at least approximately, to the distance of the respective sealing gap (in particular at a radially innermost region of the sealing gap) to the shaft bearing, in particular on one side stored (pump shaft).
  • the angle of inclination of the gap explained in the description refers to the inclination of at least one surface delimiting the sealing gap (the impeller and / or the pump component) relative to the aforementioned radial plane.
  • the centrifugal pump according to the invention is designed for large volume flow, in particular marine applications.
  • the centrifugal pump for conveying a volume flow from a value range between about 500m 3 / h and about 4000m 3 / h, preferably between about 800m 3 / h and about 1500m 3 / h (for example, smaller Cooling water pump) or between about 1500m 3 / h and about 2300m 3 / h (for example, medium-sized cooling water pump) or between 2300m 3 / h and 3500m 3 / h (for example, larger cooling water pump) is designed, preferably at a maximum head from a range between about 20m and about 50m, preferably about 30m.
  • the double-flow centrifugal pump is realized in a vertical design, that is to say in such a way that the shaft runs perpendicular to a stationary surface of the centrifugal pump. It is particularly preferred if the centrifugal pump is a single-stage centrifugal pump, that is to say exclusively an impeller.
  • the pump housing is a so-called spiral housing, which predetermines the flow path on the suction side to the two axial sides of the impeller and preferably spirally combines two outlet channels on the pressure side.
  • the invention also leads to the use of a trained according to the concept of the invention double-flow centrifugal pump as a cooling water pump for a marine diesel engine or ballast water pump on a ship.
  • 1 is a sectional view of an embodiment of a trained according to the concept of the invention double-flow centrifugal pump
  • FIG. 2 shows a schematic drawing to illustrate the gap conditions
  • Fig. 7 different design options of the sealing gaps.
  • like elements and elements having the same function are denoted by the same reference numerals.
  • a double-flow centrifugal pump 1 is shown in a vertical sectional view in a sectional view.
  • a cooling water pump for a marine diesel engine which is designed to promote a flow rate of 2300m3 / h at a maximum head of 30m.
  • the centrifugal pump 1 comprises a pump housing 2 designed as a spiral housing with a suction-side inlet 3 and a pressure-side outlet 4.
  • a shaft 5 mounted on one side, which is mounted by means of a bearing 6 designed as a ball bearing
  • the end of the shaft 5 carries a doppelflutiges impeller 7 with a substantially circular cylindrical envelope contour.
  • a shaft seal 8 In a region axially between the bearing 6 and the impeller 7 is a shaft seal 8.
  • the shaft 5 passes through in a region above the shaft seal 8 a on the pump housing 2 fixed by screwing cover 9.
  • the impeller 7 separates a negative pressure region 10 (suction side) from an overpressure region 11 (pressure side).
  • the shaft 5 is rotatable by means of a motor, not shown, in particular an electric motor in a conventional manner, said rotating with the shaft 5 impeller 7 from both axial sides of the negative pressure region 10 fluid, here sucking cooling water and in the radial direction outwardly into the overpressure region 11 promotes, wherein the pressure area 11 is divided into two spirally arranged flow channels 12, 13 which are separated by a partition 14 from each other. In the region of the outlet 4, the two flow channels 12, 13 or the fluid streams are brought together again.
  • the radial gaps 15, 16 are not designed as sealing gaps by the approximately 5 mm in the exemplary embodiment shown or do not fulfill a sufficient sealing function.
  • the radial gaps have the shape of Kreiszylindermantelfikieen. If the radial gaps 15, 16 were the only sealing gaps, the centrifugal pump 1 would have an extremely poor efficiency due to the comparatively large gap width, since liquid, here cooling water constantly in large quantity through the radial gaps 15, 16 from the overpressure region 11 in the negative pressure region 10 flow and thus would be promoted directly in a circle.
  • the pump housing 2 engages the impeller 7 at both axial sides, ie up and down in the radial direction inwards, such that between each end face 17, 18th of the impeller 7 and the pump housing 2 (pump component) formed as an axial gap, extending in terms of its longitudinal extent in the radial direction sealing gap 19, 20 is formed is. It is essential that these sealing gaps 19, 20, measured at their narrowest point, have a smaller gap width than the radial gaps 15, 16.
  • the sealing strips 19, 20 are located radially inside the Radiaispaite 15, 16, wherein the radial gaps 15, 16 pass into the sealing gaps 19, 20 and the sealing gaps 19, 20 directly adjacent to the radial gaps 15, 15 at.
  • the gap width of the sealing gaps 19, 20 corresponds to about 400pm.
  • the sealing gaps 19, 20 are, as explained on the one hand in the axial direction bounded by the impeller 7, in the embodiment shown by one end face 17, 18 of the impeller 7 and opposite of a parallel here to the respective end face 17, 18 aligned wall surface 21, 22nd of the pump housing 2.
  • the end faces 17, 18 are displaced substantially parallel to the wall surfaces 21, 22 of the pump housing 2, so that a collision can not occur here.
  • the radial gaps 15, 16 are, as explained, so broadly dimensioned that a collision with the impeller 7, even at a maximum permissible deflection exits.
  • the impeller 7 is surrounded by a pump component 23, here the pump housing 2, more precisely an insert part 24, which forms part of the pump housing 2.
  • the insert can not be formed and arranged forming part of the housing, ie within the pump housing and that at a distance to a housing outside.
  • the liquid flows in arrow directions from the suction side (negative pressure area) 10 to the pressure side (overpressure area) 1 1.
  • sealing gaps 19, 20 are axial gaps, which are formed axially between the pump component 23 and the impeller 7.
  • the gap width s of the sealing gaps 19, 20 is 400 ⁇ in the embodiment shown.
  • the two flat-ring-disk-shaped sealing gaps 19, 20 are spaced apart from one another and separated from one another in the axial direction 15, 16 are provided whose gap width a is greater than the gap width s of the sealing gaps.
  • the gap width a with stationary impeller 7 is about 5mm.
  • the sealing gaps 19, 20 are located radially inside the radial gaps 15, 16, that is, they are spaced less far from the shaft 5 than the radial gaps 15, 16.
  • the radial gaps are circular-cylinder-jacket-shaped.
  • the sealing gaps 19, 20 have approximately the shape of a circular disk.
  • On the provision of the (narrow) radial gaps 15, 16 can also be dispensed with a modified design of the pump component 23. It is also conceivable on at least one of the two axial sides, preferably on both axial sides, of the impeller 7 to provide a plurality of sealing gaps 19, 20, which are preferably located in parcel planes and in which they are each provided with axial gaps.
  • two axially adjacent sealing gaps are connected to one another via a radial gap with a larger gap width than the gap width of the sealing gaps.
  • a stepped gap formation would result, with the axial gap sections representing the sealing gaps. This results in a stepped gap design.
  • the sealing gaps are axial gaps which essentially extend in the radial direction with respect to their longitudinal extent and whose axial extent is (substantially) less than their radial extent.
  • a sealing gap 19 is formed between the impeller 7 and a pump component 23.
  • the sealing gap 19 delimiting portion of the impeller 7 extends in relation to the longitudinal extent of the shaft exactly in the radial direction, whereas the surface portion of the pump member 23 which limits the sealing gap 19 is slightly inclined with respect to a radial plane, here at an angle ⁇ of ⁇ 1 °. This results in a sealing gap inclination by this angle with respect to an imaginary radial plane, in which in the embodiment shown, the illustrated surface portion of the impeller 7 is located.
  • both the sealing gap 19 delimiting surface portion of the impeller 7 and the sealing gap 19 opposite limiting surface portion of the pump member 23 are inclined with respect to a Radiaiebene, in the chiefsbeispiei shown both at the same angle ⁇ from here ⁇ 10 °. It is also the realization of different, but similar inclination angle feasible.
  • the surface section of the impeller 7 delimiting the sealing gap 19 lies in a radial plane relative to the longitudinal extension of the shaft, whereas the surface section of the pump component 23 delimiting the sealing gap 19 is curved, Preferably, the curvature has a radius which has the sealing gap 19 from the bearing of the shaft 5, not shown.
  • both the sealing gap 19 limiting surfaces as both the impeller 7 and the pump member 23 are slightly curved.
  • the sealing gap 19 delimiting surface of the impeller 7 is flat, but at an angle ⁇ of ⁇ 10 ° inclined to the radial plane, whereas the sealing gap 19 bounding surface of Pumpenbauteiis 23 is curved and preferably a curvature radius of 500mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe centrifuge double flux, en particulier une pompe à eau de refroidissement pour un moteur diesel de bateau, ou une pompe à eau de ballast, comprenant un corps de pompe (2) et une roue à aubes double flux (7), montée solidaire en rotation, sur un arbre (3) entraîné en rotation, au moyen de laquelle un fluide peut être aspiré des deux côtés axiaux, d'une zone en dépression (10), et peut être refoulé en direction radiale, dans une zone en surpression (11), la zone en dépression (10) étant étanchéifiée par rapport à la zone en surpression (11), au moyen d'au moins deux fentes d'étanchéité (19, 20) axialement à distance l'une de l'autre, qui sont ménagées entre la roue à aubes (7) et au moins un élément fixe de pompe (23), notamment le corps de pompe (2) et/ou un élément d'insertion (24). L'invention est caractérisée en ce que les fentes d'étanchéité (19, 20) se présentent sous la forme de fentes axiales disposées axialement entre la roue à aubes (7) et l'élément de pompe (23), s'étendant en direction périphérique ainsi qu'en direction radiale, dont la largeur de fente (s) est inférieure à la distance radiale (a) de la roue à aubes (7) par rapport à tous les éléments disposés à distance radiale de la roue à aubes (7).
EP11723310.6A 2010-06-16 2011-05-09 Pompe centrifuge double flux Not-in-force EP2582983B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010023931A DE102010023931A1 (de) 2010-06-16 2010-06-16 Doppelflutige Kreiselpumpe
PCT/EP2011/057396 WO2011157485A1 (fr) 2010-06-16 2011-05-09 Pompe centrifuge double flux

Publications (2)

Publication Number Publication Date
EP2582983A1 true EP2582983A1 (fr) 2013-04-24
EP2582983B1 EP2582983B1 (fr) 2016-03-30

Family

ID=44365041

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11723310.6A Not-in-force EP2582983B1 (fr) 2010-06-16 2011-05-09 Pompe centrifuge double flux

Country Status (9)

Country Link
US (1) US20130156545A1 (fr)
EP (1) EP2582983B1 (fr)
JP (1) JP5857042B2 (fr)
KR (1) KR101737665B1 (fr)
CN (1) CN103080556B (fr)
DE (1) DE102010023931A1 (fr)
DK (1) DK2582983T3 (fr)
ES (1) ES2569878T3 (fr)
WO (1) WO2011157485A1 (fr)

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Also Published As

Publication number Publication date
DE102010023931A1 (de) 2011-12-22
CN103080556A (zh) 2013-05-01
JP5857042B2 (ja) 2016-02-10
US20130156545A1 (en) 2013-06-20
ES2569878T3 (es) 2016-05-12
WO2011157485A1 (fr) 2011-12-22
CN103080556B (zh) 2016-07-13
EP2582983B1 (fr) 2016-03-30
KR101737665B1 (ko) 2017-05-18
JP2013532252A (ja) 2013-08-15
KR20130131213A (ko) 2013-12-03
DK2582983T3 (en) 2016-05-02

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