US20110315095A1 - Continuous evaporator - Google Patents

Continuous evaporator Download PDF

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Publication number
US20110315095A1
US20110315095A1 US13/254,196 US201013254196A US2011315095A1 US 20110315095 A1 US20110315095 A1 US 20110315095A1 US 201013254196 A US201013254196 A US 201013254196A US 2011315095 A1 US2011315095 A1 US 2011315095A1
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US
United States
Prior art keywords
steam generator
evaporator
steam generation
tubes
generation tubes
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.)
Abandoned
Application number
US13/254,196
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English (en)
Inventor
Jan Brückner
Joachim Franke
Gerhard Schlund
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.)
Siemens AG
Original Assignee
Siemens 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
Application filed by Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRUECKNER, JAN, SCHLUND, GERHARD, FRANKE, JOACHIM
Publication of US20110315095A1 publication Critical patent/US20110315095A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D7/00—Auxiliary devices for promoting water circulation
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the invention relates to a once-through evaporator for a horizontally constructed waste heat steam generator with a first evaporator heating surface which incorporates a number of first steam generation tubes, the arrangement of which is essentially vertical and through which the flow is from the bottom to the top, and another second evaporator heating surface, which on the flow substance side is connected downstream from the first evaporator heating surface, which incorporates a further number of second steam generation tubes the arrangement of which is essentially vertical and through which the flow is from the bottom to the top.
  • the heat contained in the expanded working substance or heating gas from the gas turbine is utilized for the generation of steam for the steam turbine.
  • the heat transfer is effected in a waste heat steam generator connected downstream from the gas turbine, in which it is usual to arrange a number of heating surfaces for the purpose of preheating water, for steam generation and for superheating steam.
  • the heating surfaces are connected into the water-steam circuit of the steam turbine.
  • the water-steam circuit usually incorporates several, e.g. three, pressure stages, where each of the pressure stages can have an evaporator heating surface.
  • a design as a once-through steam generator For the steam generator connected downstream on the heating gas side from the gas turbine as a waste heat steam generator, several alternative design concepts can be considered, namely a design as a once-through steam generator, or a design as a recirculatory steam generator.
  • a once-through steam generator the heating up of steam generation tubes, which are provided as evaporation tubes, results in the flow substance being evaporated in a single pass through the steam generation tubes.
  • the water which is fed around the circulation is only partially evaporated during its passage through the evaporator tubes. After the steam which has been generated has been separated off, the water which has not yet been evaporated is then fed once more to the same evaporator tubes for further evaporation.
  • a once-through steam generator is not subject to any pressure limitations.
  • a high live steam pressure favors a high thermal efficiency, and hence low CO 2 emissions from a fossil-fuel fired power station.
  • a once-through steam generator has a simple construction and can thus be manufactured at particularly low cost.
  • the use of a steam generator, designed in accordance with the once-through principle, as the waste heat steam generator for a combined cycle gas turbine plant is therefore particularly favorable for the achievement of a high overall efficiency for the combined cycle gas turbine plant together with simple construction.
  • a once-through steam generator which is designed as a waste heat steam generator can basically be engineered in one of two alternative forms of construction, namely as a vertical construction or as a horizontal construction.
  • a once-through steam generator with a horizontal construction is then designed so that the heating substance or heating gas, for example the exhaust gas from the gas turbine, flows through it in an approximately horizontal direction, whereas a once-through steam generator with a vertical construction is designed so that the heating substance flows through it in an approximately vertical direction.
  • a once-through steam generator with a horizontal construction can be manufactured with particularly simple facilities, and with particularly low manufacturing and assembly costs.
  • the steam generation tubes of an evaporator heating surface are exposed, depending on their positioning, to greatly differing heating. It is thereby possible that an unstable flow arises, in particular in the steam generation tubes which are upstream on the flow substance side, and this can endanger the operational reliability of the waste heat steam generator.
  • the object underlying the invention is thus to specify a waste heat steam generator of the type identified above which has a particularly high operational reliability together with a particularly simple construction.
  • first steam generation tubes are designed in such a way that the mean mass flow density which is established in the first steam generation tubes when operating at full load does not fall below a prescribed minimum mass flow density.
  • the invention then starts from the consideration that it would be possible to achieve a particularly high operational reliability by a dynamic stabilization of the flow in the first steam generation tubes.
  • a pulsating, oscillatory type of flow is to be avoided.
  • a flow of this type arises in particular in those first steam generation tubes which are located at the heating gas side exit from the first evaporator heating surface, and which experience comparatively limited heating.
  • These tubes contain a flow substance with a comparatively high proportion of water. Because of the greater proportionate weight of the flow substance in these tubes, the through-flow in these tubes is reduced, partly to the point of stagnation. For the purpose of avoiding this effect, it would be possible to provide chokes or pressure equalization lines, but these would mean a comparatively more expensive construction.
  • the parameters of the steam generation tubes in the first evaporator heating surface should be directly modified. This can be achieved by designing the first steam generation tubes in such a way that the mean mass flow density through the first steam generation tubes which is established when operating at full load does not fall below a prescribed minimum mass flow density.
  • the value of the prescribed minimum mass flow density is 100 kg/m 2 s. That is, a design of the steam generation tubes to achieve such a choice of mass flow density leads to a particularly good dynamic stabilization of the flow in the first steam generation tubes, and hence to particularly reliable operation of the steam generator.
  • the geodetic pressure loss should therefore be reduced as a proportion of the overall pressure loss.
  • the internal diameter of the first steam generation tubes is advantageously chosen in such a way that the mean mass flow density which is established in the first steam generation tubes when operating at full load does not fall below the prescribed minimum mass flow density, by which means the overall pressure loss is increased by raising the frictional pressure loss.
  • the internal diameter of the first steam generation tubes is then between 15 and 35 mm. That is, a choice of internal diameter in this range determines the volume of the first steam generation tubes to be such that the geodetic pressure loss in the steam generation tubes is so low that the mass flow density does not fall below prescribed minimum, i.e. it is no longer possible for stagnation or pulsation of the flow to occur. By this means, particularly reliable operation of the steam generator is ensured.
  • a number of first steam generation tubes are connected one after another on the heating gas side as rows of tubes.
  • This makes it possible to use as an evaporator heating surface a larger number of steam generation tubes connected in parallel, which means a better heat input from the enlarged surface.
  • the steam generation tubes which are arranged one after another in the direction of flow of the heating gas are differently heated.
  • the flow substance is comparatively weakly heated.
  • the first evaporator heating surface is connected downstream on the heating gas side from the second evaporator heating surface.
  • the second evaporator heating surface which is connected downstream on the flow substance side and is thus designed to further heat up a flow substance which has already been evaporated, also lies in a comparatively strongly heated region of the heating gas duct.
  • a once-through evaporator of this type can expediently be used in a waste heat steam generator, and the waste heat steam generator used in a combined cycle gas turbine plant.
  • the steam generator downstream on the heating gas side from a gas turbine it is advantageous to connect the steam generator downstream on the heating gas side from a gas turbine.
  • a supplementary heat source can expediently be arranged behind the gas turbine, to raise the heating gas temperature.
  • the advantages achieved by the invention consist, in particular, in the fact that designing the first steam generation tubes in such a way that the mean mass flow density established in the first steam generation tubes when operating at full load does not fall below a prescribed minimum mass flow density achieves a dynamic stabilization of the flow, and thus particularly reliable operation of the waste heat steam generator.
  • FIGURE in the drawing shows a simplified representation of a longitudinal section through a steam generator with a horizontal construction.
  • the once-through steam generator 1 for the waste heat steam generator 2 shown in the FIGURE is connected downstream from a gas turbine, not shown here in more detail, on its exhaust gas side.
  • the waste heat steam generator 2 has a surrounding wall which forms a heating gas duct 5 through which the exhaust gas from the gas turbine can flow in an approximately horizontal direction as heating gas, as indicated by the arrows 4 .
  • Arranged in the heating gas duct 5 is a number of evaporator heating surfaces 8 , 10 , designed according to a once-through principle. In the exemplary embodiment shown in FIG. 1 , each of two evaporator heating surfaces 8 , 10 is shown, but a larger number of evaporator heating surfaces could also be provided.
  • Each of the evaporator heating surfaces 8 , 10 shown in the FIGURE incorporates a number of rows of tubes, 11 and 12 respectively, each in the nature of a nest of tubes, arranged behind each other in the direction of the heating gas.
  • Each row of tubes 11 , 12 incorporates in turn a number of steam generation tubes, 13 and 14 respectively, in each case arranged beside each other in the direction of the heating gas, of which in each case only one can be seen for each row of tubes 11 , 12 .
  • the first steam generation tubes 13 of the first evaporator heating surface 8 which are arranged approximately vertically and connected in parallel so that a flow substance W can flow through them, are here connected on their output sides to an outlet collector 15 which is common to them.
  • the second steam generation tubes 14 of the second evaporator heating surface 10 which are also arranged approximately vertically and connected in parallel so that a flow substance W can flow through them, are also connected on their output sides to an outlet collector 16 which is common to them.
  • the steam generation tubes 14 of the second evaporator heating surface 10 are connected downstream from the steam generation tubes 13 of the first evaporator heating surface 8 , via a downpipe 17 .
  • the evaporation system formed by the evaporator heating surfaces 8 , 10 can have admitted to it the flow substance W which, in a single pass through the evaporation system, is evaporated and after it emerges from the second evaporator heating surface 10 is fed away as steam D.
  • the evaporation system formed by the evaporator heating surfaces 8 , 10 is connected into a steam turbine's water-steam circuit, which is not shown in more detail.
  • the water-steam circuit of the steam turbine has connected into it a number of other heating surfaces 20 , indicated schematically in the FIGURE.
  • the heating surfaces 20 could be, for example, superheaters, medium-pressure evaporators, low-pressure evaporators and/or preheaters.
  • the first steam generation tubes 13 are now designed in such a way that the mass flow density does not fall below a minimum prescribed for full load operation as 100 kg/m 2 s. Here, their internal diameter is between 15 mm and 35 mm. By this means, stagnation of the flow in the first steam generation tubes 13 is avoided. A standing column of water with the formation of steam bubbles, and a resulting oscillatory type of pulsating through-flow, is prevented. By this means, the mechanical loading on the waste heat steam generator 2 is reduced, and particularly reliable operation is guaranteed at the same time as a simple construction.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Heat Treatment Of Water, Waste Water Or Sewage (AREA)
US13/254,196 2009-03-09 2010-02-05 Continuous evaporator Abandoned US20110315095A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009012322.9 2009-03-09
DE102009012322.9A DE102009012322B4 (de) 2009-03-09 2009-03-09 Durchlaufverdampfer
PCT/EP2010/051425 WO2010102865A2 (de) 2009-03-09 2010-02-05 Durchlaufverdampfer

Publications (1)

Publication Number Publication Date
US20110315095A1 true US20110315095A1 (en) 2011-12-29

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ID=42557788

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US13/254,196 Abandoned US20110315095A1 (en) 2009-03-09 2010-02-05 Continuous evaporator

Country Status (15)

Country Link
US (1) US20110315095A1 (es)
EP (1) EP2438351B1 (es)
JP (1) JP2012519830A (es)
KR (1) KR20110128849A (es)
CN (1) CN102575839A (es)
AU (1) AU2010223498A1 (es)
BR (1) BRPI1013252A2 (es)
CA (1) CA2754667A1 (es)
DE (1) DE102009012322B4 (es)
ES (1) ES2661041T3 (es)
PL (1) PL2438351T3 (es)
RU (1) RU2011140817A (es)
TW (1) TWI529350B (es)
WO (1) WO2010102865A2 (es)
ZA (1) ZA201106010B (es)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110052796A1 (en) * 2009-08-25 2011-03-03 Von Ardenne Anlagentechnik Gmbh Method and device for producing stoichiometry gradients and layer systems
US20110197830A1 (en) * 2008-09-09 2011-08-18 Brueckner Jan Continuous steam generator
US20110315094A1 (en) * 2009-03-09 2011-12-29 Brueckner Jan Continuous Evaporator

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010061186B4 (de) 2010-12-13 2014-07-03 Alstom Technology Ltd. Zwangdurchlaufdampferzeuger mit Wandheizfläche und Verfahren zu dessen Betrieb
DE102011004272A1 (de) * 2011-02-17 2012-08-23 Siemens Aktiengesellschaft Durchlaufverdampfer
DE102011004276A1 (de) * 2011-02-17 2012-08-23 Siemens Aktiengesellschaft Durchlaufverdampfer
DE102011004271A1 (de) * 2011-02-17 2012-08-23 Siemens Aktiengesellschaft Durchlaufdampferzeuger für die indirekte Verdampfung insbesondere in einem Solarturm-Kraftwerk
DE102011006390A1 (de) * 2011-03-30 2012-10-04 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers und zur Durchführung des Verfahrens ausgelegter Dampferzeuger
CN110274216A (zh) * 2019-07-10 2019-09-24 上海核工程研究设计院有限公司 一种直流蒸汽发生器用节流元件

Citations (11)

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US3712371A (en) * 1969-11-11 1973-01-23 Shell Oil Co Method for heat recovery from synthesis gas
US3842904A (en) * 1972-06-15 1974-10-22 Aronetics Inc Heat exchanger
US5706766A (en) * 1993-09-30 1998-01-13 Siemens Aktiengesellschaft Method of operating a once-through steam generator and a corresponding steam generator
US5967097A (en) * 1996-01-25 1999-10-19 Siemens Aktiengesellschaft Once-through steam generator and a method of configuring a once-through steam generator
US6189491B1 (en) * 1996-12-12 2001-02-20 Siemens Aktiengesellschaft Steam generator
US6250257B1 (en) * 1996-11-06 2001-06-26 Siemens Aktiengesellschaft Method for operating a once-through steam generator and once-through steam generator for carrying out the method
US20040149239A1 (en) * 2001-06-08 2004-08-05 Joachim Franke Steam generator
US6957630B1 (en) * 2005-03-31 2005-10-25 Alstom Technology Ltd Flexible assembly of once-through evaporation for horizontal heat recovery steam generator
US20060075977A1 (en) * 2003-01-31 2006-04-13 Joachim Franke Steam generator
US20060124077A1 (en) * 2002-11-22 2006-06-15 Gerhard Weissinger Continuous steam generator with circulating atmospheric fluidised-bed combustion
US20060192023A1 (en) * 2001-08-31 2006-08-31 Joachim Franke Method for starting a steam generator comprising a heating gas channel that can be traversed in an approximately horizontal heating gas direction and a steam generator

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ATE117420T1 (de) * 1991-04-18 1995-02-15 Siemens Ag Durchlaufdampferzeuger mit einem vertikalen gaszug aus im wesentlichen vertikal angeordneten rohren.
CA2294710C (en) * 1997-06-30 2007-05-22 Siemens Aktiengesellschaft Waste heat steam generator
US5924389A (en) * 1998-04-03 1999-07-20 Combustion Engineering, Inc. Heat recovery steam generator
EP1398564A1 (de) * 2002-09-10 2004-03-17 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Dampferzeugers in liegender Bauweise sowie Dampferzeuger zur Durchführung des Verfahrens
DE102005023082B4 (de) * 2005-05-13 2014-05-28 Alstom Technology Ltd. Durchlaufdampferzeuger
US7243618B2 (en) * 2005-10-13 2007-07-17 Gurevich Arkadiy M Steam generator with hybrid circulation

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3712371A (en) * 1969-11-11 1973-01-23 Shell Oil Co Method for heat recovery from synthesis gas
US3842904A (en) * 1972-06-15 1974-10-22 Aronetics Inc Heat exchanger
US5706766A (en) * 1993-09-30 1998-01-13 Siemens Aktiengesellschaft Method of operating a once-through steam generator and a corresponding steam generator
US5967097A (en) * 1996-01-25 1999-10-19 Siemens Aktiengesellschaft Once-through steam generator and a method of configuring a once-through steam generator
US6250257B1 (en) * 1996-11-06 2001-06-26 Siemens Aktiengesellschaft Method for operating a once-through steam generator and once-through steam generator for carrying out the method
US6189491B1 (en) * 1996-12-12 2001-02-20 Siemens Aktiengesellschaft Steam generator
US20040149239A1 (en) * 2001-06-08 2004-08-05 Joachim Franke Steam generator
US20060192023A1 (en) * 2001-08-31 2006-08-31 Joachim Franke Method for starting a steam generator comprising a heating gas channel that can be traversed in an approximately horizontal heating gas direction and a steam generator
US7281499B2 (en) * 2001-08-31 2007-10-16 Siemens Aktiengesellschaft Method for starting a steam generator comprising a heating gas channel that can be traversed in an approximately horizontal heating gas direction and a steam generator
US20060124077A1 (en) * 2002-11-22 2006-06-15 Gerhard Weissinger Continuous steam generator with circulating atmospheric fluidised-bed combustion
US20060075977A1 (en) * 2003-01-31 2006-04-13 Joachim Franke Steam generator
US6957630B1 (en) * 2005-03-31 2005-10-25 Alstom Technology Ltd Flexible assembly of once-through evaporation for horizontal heat recovery steam generator

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110197830A1 (en) * 2008-09-09 2011-08-18 Brueckner Jan Continuous steam generator
US9267678B2 (en) * 2008-09-09 2016-02-23 Siemens Aktiengesellschaft Continuous steam generator
US20110315094A1 (en) * 2009-03-09 2011-12-29 Brueckner Jan Continuous Evaporator
US20110052796A1 (en) * 2009-08-25 2011-03-03 Von Ardenne Anlagentechnik Gmbh Method and device for producing stoichiometry gradients and layer systems
US8563084B2 (en) * 2009-08-25 2013-10-22 Von Ardenne Anlagentechnik Gmbh Method and device for producing stoichiometry gradients and layer systems

Also Published As

Publication number Publication date
TWI529350B (zh) 2016-04-11
ZA201106010B (en) 2012-09-26
TW201040463A (en) 2010-11-16
EP2438351A2 (de) 2012-04-11
JP2012519830A (ja) 2012-08-30
AU2010223498A1 (en) 2011-09-29
CN102575839A (zh) 2012-07-11
WO2010102865A3 (de) 2012-06-07
ES2661041T3 (es) 2018-03-27
BRPI1013252A2 (pt) 2016-04-05
KR20110128849A (ko) 2011-11-30
DE102009012322B4 (de) 2017-05-18
WO2010102865A2 (de) 2010-09-16
RU2011140817A (ru) 2013-04-20
PL2438351T3 (pl) 2018-05-30
EP2438351B1 (de) 2017-11-29
DE102009012322A1 (de) 2010-09-16
CA2754667A1 (en) 2010-09-16

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