EP1429858A1 - Procede et dispositif de degazage thermique - Google Patents

Procede et dispositif de degazage thermique

Info

Publication number
EP1429858A1
EP1429858A1 EP02765176A EP02765176A EP1429858A1 EP 1429858 A1 EP1429858 A1 EP 1429858A1 EP 02765176 A EP02765176 A EP 02765176A EP 02765176 A EP02765176 A EP 02765176A EP 1429858 A1 EP1429858 A1 EP 1429858A1
Authority
EP
European Patent Office
Prior art keywords
water
steam
volume
pressure
drum
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Withdrawn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
EP02765176A
Other languages
German (de)
English (en)
Inventor
Erhard Liebig
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.)
General Electric Technology GmbH
Original Assignee
Alstom Schweiz 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 Alstom Schweiz AG filed Critical Alstom Schweiz AG
Publication of EP1429858A1 publication Critical patent/EP1429858A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F01K23/106—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 with water evaporated or preheated at different pressures in exhaust boiler
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D19/00—Degasification of liquids
    • B01D19/0005—Degasification of liquids with one or more auxiliary substances
    • 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 present invention relates to a method according to the preamble of claim 1. It also relates to a device for carrying out the method according to the invention.
  • the water-steam cycle of a steam power plant or a combined cycle power plant essentially comprises a boiler or waste heat boiler as a steam generator, a steam turbine, a condenser, a feed water tank / degasser, as well as pumps and pipes. It is a system with very high cleanliness requirements for the work equipment as well as a special water-chemical procedure to reduce corrosion and deposits.
  • the waste heat boiler of a combination system consists of up to 3 pressure levels for steam generation at different pressure levels.
  • a pressure stage includes an economizer or preheater and an evaporator, and possibly also a steam drum and a superheater.
  • the working fluid must be degassed, which can be done, for example, by a thermal process. Degassing of the working fluid is particularly important if the system was at ambient pressure or was open, in particular after revisions or during cold starts. Degassing is also important when large amounts of make-up water flow in.
  • thermal degassing takes place either in the condenser, in the feed water tank / degasser, or by means of a degasser placed on the low-pressure drum.
  • the latter two variants are investment-intensive due to the additional components required.
  • there is an energy disadvantage in these variants due to the need for heating steam for heating a liquid that is slightly undercooled by 5 - 20 K to saturation temperature. The higher the pressure level of the degasser, the greater this disadvantage.
  • EP 0 359 735 B1 proposes a waste heat steam generator in which the steam drum is provided with integrated thermal degassing, and which steam drum, in addition to the function of separating the water / steam mixture, also has the function of storing the Has feed water.
  • the patent specification does not contain any information as to how this integrated thermal degassing is designed or which means for degassing are made available. The figure only shows that it could be a trickle degasser attached.
  • Degassing is not absolutely necessary during the entire operating life of the system if the systems are functioning properly and the systems operating in the vacuum area are leak-tight. For this reason, it does not make sense to ensure permanent good degassing in the case of high investments and constant loss of performance. Rather, it makes more sense to ensure adequate degassing by taking additional measures in the event of special conditions or the implementation of limited-time operations, but to operate the system without this additional degassing during normal operation.
  • the essence of the invention is therefore to realize an integrated thermal degassing, which is based on using the already existing two-phase system consisting of steam and water for degassing.
  • a two-phase mixture is generated from the separately available steam and water phases, which in turn flows into the water volume of the steam system.
  • the degassing is guaranteed to a certain extent by means of an internal steam-water circulation system.
  • This surprisingly simple, yet efficient type of degassing can also be retrofitted to existing condensers, feed water tanks, steam drums and other tanks with few modifications.
  • the simplicity of the solution therefore means that the investment is low compared to the usual degassing variants.
  • the method is characterized in that the water is sucked out of the water volume of a container by means of at least one pump, that is to say a forced circulation is brought about.
  • the water drawn in from the water volume can preferably be conveyed through at least one water jet operated as a jet pump, steam being drawn in from the steam volume of the steam system to form the two-phase mixture through the at least one water jet.
  • a major advantage of this concept is that forced circulation by means of a motor-driven pump can only be guaranteed for the water.
  • the steam is sucked in and mixed with the water using the water jet.
  • Other special devices for sucking in the steam and for mixing the steam with the water are not required.
  • the steam content of the two-phase mixture which flows into the water volume of the steam system is in the range from 2 to 5%.
  • the steam bubble diameters and the injection locations are preferably set in such a way that a residence time of the steam bubbles in the water in the range from 5 to 8 seconds results in an ascent height in the water of at least 60 cm.
  • the two-phase mixture is advantageously introduced into the water volume of the steam system via nozzles arranged below the water level, preferably near the bottom of the container, in particular two-substance nozzles, two-phase nozzles, at a particularly favorable excess pressure of 1 to 2 bar injected, wherein a plurality of nozzles or nozzle pipes is preferably arranged for better mixing.
  • the steam system is a steam system of a waste heat boiler, specifically a steam system consisting of at least one steam drum with at least one evaporator and preferably at least one economizer connected upstream
  • a steam system consisting of at least one steam drum with at least one evaporator and preferably at least one economizer connected upstream
  • the steam volume is the steam volume of the steam drum and the water volume is the water volume of the same steam drum.
  • such a steam drum can also advantageously take over the function of storing the feed water.
  • the steam drum is a low-pressure steam drum, in particular a steam drum of a circulation evaporator with a steam content at the outlet of the evaporator in the range from 10 to 15%.
  • Another preferred embodiment of the method is characterized in that the functions of degassing and the separation of steam and water to be implemented within the steam drum are spatially separated by a corresponding arrangement of both the nozzles and the inlets coming from the evaporator.
  • the steam drum then has a water inlet, an inflow connection for water to the evaporator and a return flow connection for water and steam from the evaporator, a steam outlet, and a gas outlet.
  • the two-phase mixture flows out via nozzles, preferably on the side of the gas outlet, into the water volume and the two-phase mixture coming from the evaporator is preferably introduced into the steam drum on the side of the steam outlet.
  • a preferred embodiment of a device for carrying out the method is characterized in that the feed water inlet from the economizer and the feed water outlet on the steam drum are arranged opposite one another, with additional flow obstacles, baffles, being advantageously arranged in the water volume, which promote mixing of the water and one Prevent direct flow through the steam drum.
  • the gas outlet and the steam outlet on the steam drum can be arranged opposite one another, in particular additional devices in the Steam volumes are arranged, which favor a directed flow of the expelled gases and the steam generated.
  • the evaporator is arranged in the waste heat boiler through which hot exhaust gases from an exhaust gas generator flow, and the system consisting of exhaust gas generator and waste heat boiler is regulated in such a way that the steam generation in the evaporator corresponds to the requirements of the degassing. With such a special driving style, the steam losses are reduced or avoided.
  • the same goal of reducing or avoiding steam losses can be achieved by partially or completely bypassing the economizer.
  • By getting significantly subcooled water into the steam drum some or all of the steam generated in the evaporator is used to preheat the feed water.
  • the system of evaporator and steam drum then works partially or completely as a preheater.
  • the circulation system for example the emitter system for thermal degassing of the water of the steam system, can be switched off under the condition of a degassing that is not required; in this case the circulation pump is not in operation.
  • Figure 1 is a schematic representation of a combined cycle power plant.
  • Fig. 2 shows a longitudinal section of the low-pressure steam drum with means for thermal
  • FIG. 3 shows a section through a condenser with means for thermal degassing
  • FIG. 4 shows a feed water tank with means for thermal degassing.
  • FIG. 1 shows the schematic representation of a combined cycle power plant, on the basis of which the design of the degassing according to the invention is to be explained.
  • the same reference numerals are used to describe the device and the method, for example, for a line (e.g. feed water line) and the medium flowing therein (e.g. feed water).
  • a line e.g. feed water line
  • the medium flowing therein e.g. feed water
  • the system shown in FIG. 1 is, for example, a so-called single-shaft system, in which the gas turbine group GA and steam turbine group DA with the generator G are on a shaft W.
  • the generator G is arranged between the gas turbine group GA and the steam turbine group DA.
  • An automatically acting clutch K is arranged in the shaft train between steam turbine group DA and generator G, which ensures power transmission when the steam turbine is running at least synchronously with the generator and the gas turbine group.
  • the heat contained in the exhaust gas 7 of the gas turbine group GA is used in a waste heat boiler 8 to generate steam.
  • the water supplied to the waste heat boiler 8 is preheated in this waste heat boiler 8, evaporated and possibly overheated.
  • the steam generated in the waste heat boiler 8 serves to drive the steam turbine group DA.
  • the steam expanded in the steam turbine group DA, waste steam 10, is condensed in the condenser 11 and fed again to the waste heat boiler 8.
  • the gas turbine group GA consists of a compressor 1, a combustion chamber 2 and a turbine 3.
  • intake air 4 is compressed in a compressor 1, then supplied to the combustion chamber 2 as combustion air 5, and the hot gas 6 that is produced there is fed to the turbine 3 managed and processed.
  • the exhaust gas 7 of the gas turbine group is fed to the waste heat boiler 8 and used there to generate steam for operating the steam turbine group DA. After the waste heat boiler 8, the exhaust gas 7 is released into the environment via a chimney 9.
  • Compressor 1, combustion chamber 2 and turbine 3 are combined under the term of gas turbine group GA.
  • a gas turbine group can have multiple combustion chambers and multiple turbines. For example, in the case of gas turbine groups with sequential combustion, a high-pressure combustion chamber with a high-pressure turbine is followed by a low-pressure combustion chamber with a low-pressure turbine.
  • a gas turbine group can also have a plurality of compressors.
  • the steam turbine group DA is shown in simplified form as a steam turbine. It can also be a multi-unit system of various designs consisting of high, medium and low pressure parts.
  • the waste heat boiler 8 is fed from the condenser 11 by means of the condensate pump 13 via the feed water line 14 into the low-pressure (LP) preheater or economizer 15.
  • the actuator 16 in the feed water line 14 is open and the actuator 17 in the bypass line 18 is closed ,
  • the feed water conveyed into the waste heat boiler 8 by means of the condensate pump 13 has a temperature of typically 20 to 45 ° C. (water-cooled condenser) or 30 to 55 ° C. (air-cooled condenser).
  • the feed water is preheated in the low-pressure economizer 15.
  • the feed water preheated in the low-pressure economizer 15 is fed to the low-pressure steam drum 21 via the feed water line 19 and the actuator 20.
  • the low pressure steam drum 21 is connected to the low pressure evaporator 22.
  • the low-pressure steam drum 21 is followed by a low-pressure superheater 23, to which the low-pressure live steam line 24 connects, which leads to the steam turbine group DA.
  • feed water 29 can be conveyed to further pressure stages of the waste heat boiler 8 by means of a further feed water pump 26 via a further feed water line 25, a further actuator 27 and a further economizer 28.
  • the low-pressure steam drum 21 takes over the additional function of the feed water tank in this case.
  • the steam generated in the waste heat boiler 8 in the further pressure stages is fed to the steam turbine group DA via the corresponding high pressure (HD) or medium pressure (MD) live steam lines 30, 31.
  • the steam turbine group DA the steam is expanded to perform work.
  • the exhaust steam 10 of the steam turbine group DA is condensed in the condenser 11.
  • the condensate is fed again to the waste heat boiler 8 by means of the condensate pump 13 via the feed water line 14.
  • the feeding of further pressure stages of the waste heat boiler 8 can alternatively also take place directly from the condenser 11.
  • the low-pressure economizer 15, the low-pressure steam drum 21, the low-pressure evaporator 22 and the low-pressure superheater 23 together form a low-pressure steam system working on one pressure stage.
  • the pipe systems (economizer, evaporator, superheater) arranged for heat transfer from the exhaust gas 7 of the gas turbine group to the feed water or steam in the waste heat boiler 8 are referred to as heating surfaces.
  • the water is fed back to the evaporator, while the steam reaches the steam turbine group directly or via a superheater that may be present.
  • the flow through the evaporator can be designed as a natural circulation or forced circulation.
  • the individual pressure stages of the waste heat boiler can also be designed according to the principle of the once-through evaporator.
  • the described or illustrated arrangement of the low-pressure economizer 15 at the exhaust-side end of the waste heat boiler 8 and the omission of a separate feed water tank / degasser is typical of a gas-fired gas turbine group.
  • the low-pressure economizer 15 can be bypassed to avoid dew point corrosion at the exhaust-side end of the waste heat boiler 8 when switching to the fuel oil. This is done by opening the actuator 17 in the bypass line 18 and closing the actuator 16 in the feed water line 14.
  • the condensate pump 13 provides the interface between the condensate and the feed water system. For this reason, the mass flow until it enters the condensate pump 13 is referred to as condensate. The mass flows from the outlet from the condensate pump 13 are then referred to as feed water.
  • the feed water is degassed in the low-pressure steam drum 21.
  • the process of degassing in the low-pressure steam drum 21 is explained in more detail with reference to the longitudinal section of the low-pressure steam drum 21 shown in FIG.
  • the feed water coming from the low-pressure economizer 15 via the feed water line 19 and the actuator 20 enters the steam drum 21 via the feed water inlet 32.
  • the feed water conveyed via the feed water line 25 to the further pressure stages of the waste heat boiler 8 exits the LP steam drum 21 via the feed water outlet 33.
  • flow obstacles, baffles 47 are arranged which prevent a direct flow through the drum and intensify the mixing of the water in the water volume 37 of the drum.
  • water is conveyed into the low-pressure evaporator 22 by a circulation pump 22a.
  • the returning medium is separated into steam and water in the drum.
  • the separated steam flows over dehumidifiers or steam dryers, not shown, but familiar to the person skilled in the art, to the steam outlet 34, and from there to the Niederuck superheater.
  • Different chemicals are usually contained in certain amounts in the water in the drum 21 to prevent or reduce corrosion and deposits.
  • the thermal degassing of the drum water is based in the present case on a decreasing gas solubility with increasing temperature at constant pressure.
  • the gas solubility is zero in the saturated state.
  • the water In order to drive the gases out of the drum water as completely as possible, the water should be at the saturation temperature as much as possible and also be thoroughly mixed. To improve the escape of the gases from the drum water, this water should have the largest possible surface in relation to the steam. This is achieved by the largest possible standing water surface or by means of suitable measures for distributing the water in the steam or the steam in the water.
  • the term of the two-component nozzle 41 also used in the following is a fixed term familiar to the expert. Since a water-steam mixture is not a mixture of two substances but a mixture of two phases of one substance, the technically exact term would be a two-phase nozzle.
  • the rate of ascent of the vapor bubble after leaving the two-component nozzle 41, the vapor bubble diameter, the water level height, etc. are in complex dependencies.
  • Advantageous for the degassing and the secured vapor bubble rise is a vapor bubble diameter, which ensures a dwell time of the vapor bubbles in the water of 5 to 8 seconds at an ascent height (height difference between the two-substance nozzle 41 and the water surface) of more than 0.6 m. Avoid too large vapor bubbles because they have a smaller surface area and rise too quickly. Steam bubbles that are too small lead to foaming and should therefore also be avoided.
  • the two-component nozzles 41 are preferably operated with an excess pressure of 1 to 2 bar. Due to the steam flowing through the water at boiling temperature or only slightly below it, dissolved gases are expelled from the water and discharged via the gas outlet 35.
  • the functions of degassing and the separation of steam and water are in the illustrated example by a corresponding arrangement of the nozzles 41 on the side of the gas outlet 35 and the introduction of the two-phase mixture coming from the evaporator 22 into the steam drum on the side the steam outlet 34, spatially separated.
  • the arrangement of feed water inlet 32 and feed water outlet 33 as well as gas outlet 35 and steam outlet 34 in connection with the flow obstacles 47 in water volume 37 and devices in steam volume 36 leads from feed water inlet side 32 to feed water outlet side 33 both in water volume 37 and in steam volume 36 to a gas depletion.
  • the drum 21 also has the function of a feed water reservoir can be achieved, a specific mixing of the content water can be effected by flow obstacles arranged in the water volume 37. A direct flow through the steam drum 21 from the feed water inlet 32 to the feed water outlet 33 is prevented, which increases the residence time of the water in the steam drum 21 and thus the degassing effect.
  • the low pressure systems of modern waste heat boilers typically work with the evaporator / steam drum system in a pressure range from 5 to 7 bar, up to a maximum of 10 bar, and thus at temperatures from 150 to 165 ° C up to a maximum of around 180 ° C. Due to the overpressure prevailing in the degassing system, gas discharge from the low-pressure steam drum 21 via the gas outlet 35 into the surroundings is possible in principle without auxiliary systems. Since steam also leaves the LP steam drum 21 with the gas, the gases can be discharged into the environment or into the condenser 11 to avoid steam and water losses.
  • the entire system is preferably regulated and operated in such a way that the steam generation in the evaporator 22 corresponds to the requirements of the degassing.
  • This is advantageously achieved by partially or completely bypassing the low-pressure economizer 15 and operating the low-pressure steam drum 21 and low-pressure evaporator 22 system as feed water preheaters.
  • the steam generated in the low-pressure evaporator 22 thus serves primarily to heat the feed water flowing into the low-pressure steam drum 21.
  • all of the steam generated by the low-pressure evaporator 22 is used to preheat the feed water in the steam drum 21.
  • the degassing is particularly important if, for example, standstills or special modes of operation (addition of make-up water) lead to an increased gas content in the water-steam cycle WDKL have led.
  • the radiator system 38 is not operated. In a preferred embodiment of the method, the combination system is therefore operated with discontinuous degassing.
  • the feed water flows into the drum via the preheater, economizer 15, and low-pressure saturated steam is generated for possibly further overheating and for feeding into the steam turbine.
  • the gas outlet 35 of the drum is then closed in a manner known per se by a shut-off device in such a way that no steam can escape.
  • the system is operated with degassing.
  • the bypass of the economizer is regulated in such a way that at least a predominant part of all the steam generated in the evaporator 22 is used for preheating the feed water; if necessary, a shut-off device (not shown) can also close the low-pressure live steam line or the flow path from the steam outlet 34 of the drum to the low-pressure superheater.
  • the steam turbine is then temporarily operated without additional low-pressure live steam, which temporarily reduces the overall efficiency, but media losses in the water-steam cycle are prevented.
  • the low pressure evaporator system is temporarily operated as a feed water tank with an integrated degasser and preheater function. During start-up or for a certain time afterwards, the LP steam system can be operated in the degassing mode to maintain the water-chemical driving style. Downstream steam systems or pressure stages (as indicated in FIG. 1) are supplied with degassed feed water from the LP steam drum 21. In the case of pressure stages connected in parallel, with separate supply of the steam systems or pressure stages, for example from the condenser 11, the low-pressure evaporator system can be operated in the form of a bypass degasser.
  • the method for degassing according to the invention can also be carried out, for example, in a condenser or in a feed water tank.
  • a condenser with integrated thermal degassing is shown schematically in FIG. 3.
  • Relaxed steam 10 flows into the steam volume 36 of the condenser.
  • the heat exchange surfaces of the condenser are flowed around and through on the one hand by the steam and on the other hand by coolant 12, for example air or cooling water.
  • coolant 12 for example air or cooling water.
  • the condensate is returned to the circuit via the condensate line 14 and the condensate pump 13.
  • the nozzles 41 are arranged in the water volume; In the manner described above, a pump 39 conveys condensate from the water volume 39 to the water jet 40, where steam is drawn in from the steam volume 36 and mixed with the water. The water-steam mixture flows through the nozzles 41 into the water volume 37 and drives out dissolved gases there from the condensate.
  • FIG. 4 finally shows a separate feed water container 42 which is provided for carrying out the method according to the invention.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un procédé de dégazage thermique de l'eau d'un système à vapeur, en particulier d'une chaudière de récupération (8). De préférence, ce système à vapeur comprend un tambour à vapeur (21), un économiseur monté en amont (15) et au moins un évaporateur (22). L'objectif de l'invention est d'obtenir un dégazage économique, efficace et simple d'un point de vue structurel. A cet effet, de l'eau provenant d'au moins un volume d'eau (37) est aspirée, puis est mélangée à de la vapeur issue d'un volume de gaz (36), et le mélange à deux phases ainsi obtenu s'écoule dans ledit volume d'eau (37).
EP02765176A 2001-09-14 2002-09-02 Procede et dispositif de degazage thermique Withdrawn EP1429858A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH17012001 2001-09-14
CH170101 2001-09-14
PCT/IB2002/003570 WO2003024559A1 (fr) 2001-09-14 2002-09-02 Procede et dispositif de degazage thermique

Publications (1)

Publication Number Publication Date
EP1429858A1 true EP1429858A1 (fr) 2004-06-23

Family

ID=4565959

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02765176A Withdrawn EP1429858A1 (fr) 2001-09-14 2002-09-02 Procede et dispositif de degazage thermique

Country Status (3)

Country Link
US (1) US7074259B2 (fr)
EP (1) EP1429858A1 (fr)
WO (1) WO2003024559A1 (fr)

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WO2023011843A1 (fr) 2021-08-05 2023-02-09 Messer Se & Co. Kgaa Dispositif et procédé pour séparer des mélanges de fluides

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EP2199547A1 (fr) * 2008-12-19 2010-06-23 Siemens Aktiengesellschaft Générateur de vapeur pour récupérer la chaleur et procédé de fonctionnement amélioré d'un générateur de vapeur pour récupérer la chaleur
DE102012217514A1 (de) * 2012-09-27 2014-03-27 Siemens Aktiengesellschaft Gas- und Dampfturbinenanlage mit Speisewasser-Teilstrom-Entgaser
CN108474268B8 (zh) * 2015-12-22 2021-01-19 西门子能源美国公司 联合循环动力装置中的烟囱能量控制
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Publication number Priority date Publication date Assignee Title
WO2023011843A1 (fr) 2021-08-05 2023-02-09 Messer Se & Co. Kgaa Dispositif et procédé pour séparer des mélanges de fluides
DE102021004050A1 (de) 2021-08-05 2023-02-09 Messer Se & Co. Kgaa Vorrichtung und Verfahren zum Trennen von Fluidgemischen

Also Published As

Publication number Publication date
US20040187687A1 (en) 2004-09-30
US7074259B2 (en) 2006-07-11
WO2003024559A1 (fr) 2003-03-27

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