EP2497956A1 - Freistrompumpe - Google Patents

Freistrompumpe Download PDF

Info

Publication number
EP2497956A1
EP2497956A1 EP11157262A EP11157262A EP2497956A1 EP 2497956 A1 EP2497956 A1 EP 2497956A1 EP 11157262 A EP11157262 A EP 11157262A EP 11157262 A EP11157262 A EP 11157262A EP 2497956 A1 EP2497956 A1 EP 2497956A1
Authority
EP
European Patent Office
Prior art keywords
impeller
free
flow pump
plate surface
hub body
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.)
Withdrawn
Application number
EP11157262A
Other languages
German (de)
English (en)
French (fr)
Inventor
Jean-Nicolas Favre
Hagen Renger
Michel Grimm
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.)
EGGER PUMPS Tech AG
Original Assignee
EGGER PUMPS Tech AG
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=44303228&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2497956(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by EGGER PUMPS Tech AG filed Critical EGGER PUMPS Tech AG
Priority to EP11157262A priority Critical patent/EP2497956A1/de
Priority to MX2013009982A priority patent/MX2013009982A/es
Priority to DK12705877.4T priority patent/DK2683945T3/en
Priority to CA2828911A priority patent/CA2828911C/en
Priority to JP2013557040A priority patent/JP5993383B2/ja
Priority to US14/003,274 priority patent/US9605678B2/en
Priority to CN201280011965.XA priority patent/CN103477083B/zh
Priority to ES12705877.4T priority patent/ES2557563T3/es
Priority to BR112013022590-4A priority patent/BR112013022590B1/pt
Priority to PCT/EP2012/053261 priority patent/WO2012119877A2/en
Priority to EP12705877.4A priority patent/EP2683945B1/en
Priority to PL12705877T priority patent/PL2683945T3/pl
Publication of EP2497956A1 publication Critical patent/EP2497956A1/de
Withdrawn legal-status Critical Current

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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
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2244—Free vortex
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the present invention relates to a free-flow pump with an impeller, which is spaced from an inlet so that a free passage for solids contained in the pumped liquid between the inlet and the impeller outlet is present, and the impeller bottom through the end face of a in the center of the impeller cantilevered hub body and a lower plate surface is formed, which opens with its maximum depth in the outer periphery of the impeller and is equipped with blades whose open blade end faces adjoin the hub body at its inner end and extending from there to the outer periphery of the impeller.
  • Such free-stream pumps as they are from the EP 0 081 456 A1 are known in the same applicant, are often used in wastewater, which are contaminated in particular with solids.
  • the distance between the impeller and the pump inlet is chosen so that a free flow space between the inlet and the impeller outlet is formed as a passage for a largest eligible ball with a predetermined ball diameter to counteract a risk of clogging by the solid components in the fluid.
  • the invention is therefore based on the object, a free-flow pump of the type mentioned in such a way that the accumulation of flat materials is avoided in front of the surface of rotation of the impeller so that a trouble-free pump delivery can take place.
  • a free-flow pump is proposed in which the bottom of the impeller is at least in the region of the inner third of its radius with respect to the inner end of the blade end faces not more than one-sixth lower than the height difference between the inner end of the blade end faces and the maximum depth of the plate surface.
  • the structural design of the impeller is preferably optimized so that a reduction of the pump efficiency can be kept as low as possible in order to allow the clog-free use of the free-flow pump for a variety of applications.
  • the rotor bottom be at least in the region of the inner half of its radius with respect to the inner end of the blade end sides not more than two-thirds lower than the height difference between the inner end of the blade end faces and the maximum depth of the disc surface. Most preferably, for this reason, the impeller floor in this area is lowered by not more than half of this height difference from the inner end of the blade end faces.
  • the height difference of the disk surface in the middle radial third of the impeller is preferably more than half, more preferably more than two-thirds of the height difference between the inner end of the blade end faces and the maximum depth of the plate surface.
  • An effective flow through the impeller can be achieved in that the plate surface in the direction of the outer circumference of the impeller has a continuously sloping surface portion which extends over at least a third, preferably at least half, of the radius of the impeller. More preferably, the continuously sloping surface portion extends over at least two thirds of the radius of the impeller.
  • the continuously sloping surface section opens into the outer circumference of the impeller.
  • the plate surface may have a substantially flat surface portion which extends at most over the outer two thirds, preferably at most over the outer half, of the radius of the impeller.
  • the flat plate surface along an abrupt increase in height can be connected directly to the front side of the hub body.
  • the disk surface in the middle radial third of the impeller may have a substantially stepped height drop.
  • Area section connects to the front side of the hub body substantially steadily.
  • the convex curvature may contribute to avoiding adhesion of sheet materials in the impeller entry area.
  • contributing to this purpose may be that the open blade end faces substantially adjacent to the end face of the hub body at this.
  • steeper running frontal surfaces are conceivable.
  • a further expedient embodiment of the invention provides that the height of at least two blades increases towards the outer circumference of the impeller. This can contribute to increasing the pump efficiency, since in this way an increased force is applied to the fluid emerging from the impeller in the radial direction.
  • An in Fig. 1 shown free-flow pump 1 has a pump housing 2, which has a front inlet opening 3 and a side outlet opening 4. From the pump housing 2, an impeller chamber 6 is enclosed.
  • an impeller 11 is arranged at a distance from the inlet opening 3 such that a free passage 7 for solids contained in the conveyed liquid toward the outlet opening 4 is present.
  • the impeller 11 comprises a hub body 12 in which a shaft 8 is fixed.
  • the shaft 8 extends along the longitudinal axis 5 in the rear part of the pump housing 2, where it is connected to a drive, not shown.
  • the hub body 12 comprises a windshield 25, through the free surface 24 of which the central portion of the end face 14 of the hub body 12 is formed.
  • the surface 24 of the front screen 25 is formed substantially flat.
  • the windshield 25 has a central bore for receiving a screw 9 and a gentle rounding along its outer edge, to which a radially outer face-side surface portion 13 of the hub body 12 adjoins, which is also flat.
  • the end face 14 of the hub body 12 is thus formed substantially flat and extends over slightly more than one third of the total radius of the impeller eleventh
  • the outer wall 15 of the hub body 12 adjoins the end face 14 of the hub body 12 in a stepwise abrupt manner.
  • the adjoining surface region 15 extends over half of the impeller depth substantially parallel to the longitudinal axis 5 of the pump housing 2 and then opens into a concavely curved region 16.
  • the concave curved surface portion 16 of the hub body 12 extends approximately over the middle third of the radius of the impeller 11 and then reaches its maximum depth with respect to the end face 14 of the hub body 12. From there opens the concave curved portion 16 in a flat surface portion 17, which is substantially perpendicular to the longitudinal axis 5 of the pump housing 2. This flat region 17 extends over the entire outer third of the radius of the impeller 11 and opens into its outer periphery.
  • the plate surface 18 formed by the surface regions 15-17 is equipped with blades 19.
  • the blades 19 each extend, starting from their inner end, on the region 15 of the hub body 12 which is substantially parallel to the longitudinal axis 5, as far as the outer circumference of the rotor 11.
  • the blades 19 have a substantially constant height profile.
  • the height of the blades 19 is slightly smaller than the height difference H between the flat surface region 17 and the connection region of the end face 14 and outer wall 15 of the hub body 12.
  • the Fig. 2 shows a plan view of the end face 14 of the hub body 12 and the surrounding plate surface 18, through which the impeller bottom of the impeller 11 is formed.
  • the open blade end faces 20 of the blades 19 adjoin the connection area between the end face 14 of the hub body 12 and the plate surface 18. From there, the blade end faces 20 are curved to the outer circumference of the impeller 11, wherein their thickness remains constant.
  • the direction of curvature of the blades 19 runs counter to the direction of rotation R of the impeller 1.
  • the Fig. 3 shows a cross-sectional view through the impeller 11 according to section III in Fig. 1 , This corresponds to one
  • the plate surface 18 is in this depth range of the impeller 11 at the same height with the surface portion 15 of the hub body 12, which lies in the middle radial third of the impeller 11.
  • free-flow pump 1 is a pumping liquids that are contaminated with cloths or rags, for example, without blockages of the impeller chamber 6 is possible.
  • the tendency of flat materials to settle on the front of the impeller 11 can be effectively avoided by the described geometry of the impeller 11.
  • a free-flow pump 21 is shown according to a second embodiment.
  • free-flow pump 1 identically formed components are provided with the same reference numerals.
  • the essential difference between the free-flow pump 21 and the above-described free-flow pump 1 is another geometry of its impeller 22. Clogging of the impeller chamber 6 by laminar materials can also be avoided by this impeller geometry and losses in the efficiency of the free-flow pump 21 can be sufficiently low for many applications being held.
  • these are the following structural measures:
  • the impeller 22 comprises a hub body 23, whose end face 24 extends over approximately one third of the radius of the impeller 22.
  • the end face 24 of the hub body 23 is substantially completely formed by the free surface of the front windshield 25, which has a continuous transition to an outwardly lying convex curvature 26 on the outer wall of the hub body 23.
  • the free surface of the windshield 25 consists of the central flat surface portion with the central bore for receiving the screw 9, and the gently rounded outer taper, to which the convex curvature 26 connects to the outer wall of the hub body 23.
  • the middle flat surface portion extends over more than two-thirds of the radius of the windshield 25th
  • the around the front side 24 of the hub body 23 outwardly lying plate surface 28 extends beyond the outer two thirds of the radius of the impeller 22.
  • the plate surface 28 consists of the convex curved surface portion 26 and an adjoining concavely curved surface portion 27, which along the outer wall of the Hub body 23 extend.
  • the convexly curved surface portion 26 corresponds to only about one seventh of the radius of the plate surface 28th
  • the plate surface 28 is equipped with blades 29 whose open blade end faces 30 adjoin the end surface 24 of the hub body 23 at its inner end in the region of its convexly curved connection region 26 to the plate surface 28.
  • the blades 29 extend from there to the outer periphery of the impeller 22.
  • the blades 19 have a constant height profile, with their height in the Substantially corresponds to the height difference H of the concave curved surface portion 27 on the outer circumference of the impeller of the convexly curved terminal portion 26 to the plate surface 28.
  • the maximum depth of the plate surface 28 results from its maximum height difference H from the inlet side closest surface portion of the inner ends of the blade end faces 30.
  • the plate surface 28 thus assumes its maximum depth only along its outer circumference, where the concave curved surface portion 27 opens into the outer periphery of the impeller 22 ,
  • the impeller bottom of the impeller 22 which is formed entirely by the end face 24 of the hub body 23 and the disc surface lying around 28, in its inner radial third only from the front side 24 of the hub body 23.
  • the change in height of the impeller floor in this area thus corresponds to Essentially the height profile of the windshield 25, which in comparison to the height difference H has only a small change in height at its outer edge region.
  • the Fig. 5 shows a plan view of the end face 24 of the hub body 23 and the surrounding plate surface 28, through which the impeller bottom is formed.
  • the Fig. 6 shows a cross-sectional view through the impeller 22 according to section VI in Fig. 4 , This corresponds to a section through the impeller 22 along half the height difference H between the inner end of the blade end faces 20 and the maximum depth of the disc surface 28 with respect to the inner end of the blade end faces 20.
  • the plate surface 28 is in this depth range to half the radius of the impeller 22 within its concave curved surface portion 27th
  • a free-flow pump 32 is shown according to a third embodiment.
  • free-stream pumps 1 identically formed components are provided with the same reference numerals.
  • the free-flow pump 21 essentially corresponds to the above-described free-flow pump 21 with the difference that the blade geometry of the impeller 22 is changed in order to improve the pump efficiency.
  • the impeller 33 of the free-flow pump 32 also comprises height-variable blades 34.
  • the open blade end faces 35 of the vertically variable blades 34 also adjoin the end face 24 of the hub body 23 in the area of its convexly curved connection region 26 at the inner surface at.
  • the blades 34 extend from there to the outer periphery of the impeller 33, wherein its height increases continuously.
  • the maximum height increase 36 of the blades 34 is located in the outer third of the radius of the impeller 33. From there to the outer periphery of the impeller 33, the height increase of the blades 34 is progressively smaller Mass until its height remains substantially constant over the outer tenth of the radius of the impeller 33 away.
  • the height of the blades 34 remains substantially constant over the inner radial half of the impeller floor. Then over the outer radial half of the Laufrad Camills away takes place a rapid increase in height, in which the height of the blades 34 increases by approximately one quarter of the maximum depth of the plate surface 28 with respect to the end face 24 of the hub body 25. As a result, an increase in the delivery head and the pump efficiency is achieved without having to accept disadvantageous clogging properties due to existing in the pumped liquid sheet materials.
  • the Fig. 8 shows a plan view of the impeller 33.
  • the free blade end faces 35 of the height-adjustable blades 34 have substantially the same shape characteristics as the blade end faces 30 of the constant-height blades 29, in particular with respect to their relative spacing to adjacent blades 29 and their curved shape.
  • the intervening arrangement of the height-constant blades 29 pursues the purpose of temporarily freeing the free passage 7 for passing larger solids in the fluid during a impeller rotation.
  • the Fig. 9 shows a cross-sectional view through the impeller 33 according to section IX in Fig. 7 , This corresponds to a section through the impeller 33 along half the height difference H between the inner end of the blade end faces 30, 35 and the maximum depth of the disc surface 28.
  • this section is identical to the equivalent cross-section VI by the impeller 22 of the free-flow pump 21, which in Fig. 4 is shown.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP11157262A 2011-03-08 2011-03-08 Freistrompumpe Withdrawn EP2497956A1 (de)

Priority Applications (12)

Application Number Priority Date Filing Date Title
EP11157262A EP2497956A1 (de) 2011-03-08 2011-03-08 Freistrompumpe
PL12705877T PL2683945T3 (pl) 2011-03-08 2012-02-27 Pompa o swobodnym przepływie
CN201280011965.XA CN103477083B (zh) 2011-03-08 2012-02-27 自流泵
DK12705877.4T DK2683945T3 (en) 2011-03-08 2012-02-27 Fristrømspumpe
CA2828911A CA2828911C (en) 2011-03-08 2012-02-27 Free-flow pump
JP2013557040A JP5993383B2 (ja) 2011-03-08 2012-02-27 自由流れポンプ
US14/003,274 US9605678B2 (en) 2011-03-08 2012-02-27 Free-flow pump
MX2013009982A MX2013009982A (es) 2011-03-08 2012-02-27 Bomba de flujo libre.
ES12705877.4T ES2557563T3 (es) 2011-03-08 2012-02-27 Bomba de flujo libre
BR112013022590-4A BR112013022590B1 (pt) 2011-03-08 2012-02-27 bomba de fluxo livre
PCT/EP2012/053261 WO2012119877A2 (en) 2011-03-08 2012-02-27 Free-flow pump
EP12705877.4A EP2683945B1 (en) 2011-03-08 2012-02-27 Free-flow pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11157262A EP2497956A1 (de) 2011-03-08 2011-03-08 Freistrompumpe

Publications (1)

Publication Number Publication Date
EP2497956A1 true EP2497956A1 (de) 2012-09-12

Family

ID=44303228

Family Applications (2)

Application Number Title Priority Date Filing Date
EP11157262A Withdrawn EP2497956A1 (de) 2011-03-08 2011-03-08 Freistrompumpe
EP12705877.4A Revoked EP2683945B1 (en) 2011-03-08 2012-02-27 Free-flow pump

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP12705877.4A Revoked EP2683945B1 (en) 2011-03-08 2012-02-27 Free-flow pump

Country Status (11)

Country Link
US (1) US9605678B2 (pt)
EP (2) EP2497956A1 (pt)
JP (1) JP5993383B2 (pt)
CN (1) CN103477083B (pt)
BR (1) BR112013022590B1 (pt)
CA (1) CA2828911C (pt)
DK (1) DK2683945T3 (pt)
ES (1) ES2557563T3 (pt)
MX (1) MX2013009982A (pt)
PL (1) PL2683945T3 (pt)
WO (1) WO2012119877A2 (pt)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016016375A1 (de) 2014-07-30 2016-02-04 Basf Se Verfahren zur herstellung von rieselfähigen und lagerstabilen dicarbonsäure-kristallen

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013082717A1 (en) 2011-12-06 2013-06-13 Bachellier Carl Roy Improved impeller apparatus and dispersion method
PL2978975T3 (pl) * 2013-03-28 2019-06-28 Weir Minerals Australia Ltd Wirnik napędzany pompy szlamowej
US9863423B2 (en) 2014-04-14 2018-01-09 Enevor Inc. Conical impeller and applications thereof
US10584713B2 (en) * 2018-01-05 2020-03-10 Spectrum Brands, Inc. Impeller assembly for use in an aquarium filter pump and methods

Citations (6)

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Publication number Priority date Publication date Assignee Title
DE1930566A1 (de) * 1968-06-25 1970-02-05 Wissenschaftlich Tech Zentrum Freistromkreiselpumpe
EP0081456A1 (de) 1981-12-08 1983-06-15 EMILE EGGER & CIE SA Freistrompumpe
GB2136509A (en) * 1983-03-10 1984-09-19 Ebara Corp Vortex pump
EP0649987A1 (en) * 1993-10-22 1995-04-26 Itt Flygt Ab A pump housing for a rotary pump
WO2004065796A1 (de) * 2003-01-17 2004-08-05 Ksb Aktiengesellschaft Freistrompumpe
WO2004065797A1 (de) * 2003-01-17 2004-08-05 Ksb Aktiengesellschaft Freistrompumpe

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AT122689B (de) 1929-03-21 1931-05-11 Carl Vilsmeier Ein- oder mehrstufige Schleuderpumpe.
CH277438A (de) 1949-09-28 1951-08-31 Guebeli Vincent Zentrifugalpumpe.
DE1046502B (de) 1955-02-15 1958-12-11 Roger Bert Zentrifugalpumpe, insbesondere fuer Waschmaschinen
US3167021A (en) * 1963-04-15 1965-01-26 Allis Chalmers Mfg Co Nonclogging centrifugal pump
JPS5133362Y2 (pt) * 1972-04-12 1976-08-19
SE374415B (pt) 1974-04-09 1975-03-03 Stenberg Flygt Ab
JPS5569184U (pt) 1978-11-06 1980-05-13
CA1189632A (en) * 1981-10-22 1985-06-25 Robert Furrer Apparatus for applying solder to a printed-circuit board
DE3147513A1 (de) 1981-12-01 1983-06-09 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Radiales laufrad fuer kreiselpumpen
JPS58160590A (ja) 1982-03-17 1983-09-24 Fuji Electric Co Ltd 渦流ポンプ
DE3544569A1 (de) 1985-12-17 1987-06-19 Klein Schanzlin & Becker Ag Verkleinerung des aussendurchmessers von kreiselpumpenlaufraedern
US5460482A (en) * 1992-05-26 1995-10-24 Vaughan Co., Inc. Centrifugal chopper pump with internal cutter
US5520506A (en) 1994-07-25 1996-05-28 Ingersoll-Rand Company Pulp slurry-handling, centrifugal pump
JP3352922B2 (ja) 1997-09-22 2002-12-03 株式会社荏原製作所 ボルテックス形ポンプ
JP2000240584A (ja) 1999-02-18 2000-09-05 Ebara Corp ボルテックスポンプ
JP2001024591A (ja) 1999-07-07 2001-01-26 Sanyo Electric Co Ltd 光通信装置
JP2001193682A (ja) 2000-01-06 2001-07-17 Ebara Corp ボルテックス形ポンプ
JP2001248591A (ja) * 2000-03-03 2001-09-14 Tsurumi Mfg Co Ltd 水中ポンプの羽根車
CN101021215A (zh) * 2007-03-16 2007-08-22 上海凯泉泵业（集团）有限公司 圆盘通孔型超低比转速离心泵

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1930566A1 (de) * 1968-06-25 1970-02-05 Wissenschaftlich Tech Zentrum Freistromkreiselpumpe
EP0081456A1 (de) 1981-12-08 1983-06-15 EMILE EGGER & CIE SA Freistrompumpe
GB2136509A (en) * 1983-03-10 1984-09-19 Ebara Corp Vortex pump
EP0649987A1 (en) * 1993-10-22 1995-04-26 Itt Flygt Ab A pump housing for a rotary pump
WO2004065796A1 (de) * 2003-01-17 2004-08-05 Ksb Aktiengesellschaft Freistrompumpe
WO2004065797A1 (de) * 2003-01-17 2004-08-05 Ksb Aktiengesellschaft Freistrompumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016016375A1 (de) 2014-07-30 2016-02-04 Basf Se Verfahren zur herstellung von rieselfähigen und lagerstabilen dicarbonsäure-kristallen

Also Published As

Publication number Publication date
US20140003929A1 (en) 2014-01-02
CN103477083A (zh) 2013-12-25
JP2014507600A (ja) 2014-03-27
JP5993383B2 (ja) 2016-09-14
BR112013022590B1 (pt) 2021-02-09
EP2683945B1 (en) 2015-10-21
PL2683945T3 (pl) 2016-06-30
CN103477083B (zh) 2016-04-27
WO2012119877A2 (en) 2012-09-13
MX2013009982A (es) 2014-01-24
US9605678B2 (en) 2017-03-28
CA2828911A1 (en) 2012-09-13
BR112013022590A2 (pt) 2016-12-06
DK2683945T3 (en) 2016-01-25
ES2557563T3 (es) 2016-01-27
CA2828911C (en) 2019-09-24
WO2012119877A3 (en) 2013-05-23
EP2683945A2 (en) 2014-01-15

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