EP3704356A1 - Procédé et dispositif servant à convertir une énergie thermique en une énergie mécanique ou électrique - Google Patents

Procédé et dispositif servant à convertir une énergie thermique en une énergie mécanique ou électrique

Info

Publication number
EP3704356A1
EP3704356A1 EP19730251.6A EP19730251A EP3704356A1 EP 3704356 A1 EP3704356 A1 EP 3704356A1 EP 19730251 A EP19730251 A EP 19730251A EP 3704356 A1 EP3704356 A1 EP 3704356A1
Authority
EP
European Patent Office
Prior art keywords
line
heat
steam
medium
mixer
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Withdrawn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
EP19730251.6A
Other languages
German (de)
English (en)
Inventor
Jürgen KRAIL
Georg Beckmann
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.)
Fachhochschule Burgenland GmbH
Original Assignee
Fachhochschule Burgenland 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 Fachhochschule Burgenland GmbH filed Critical Fachhochschule Burgenland GmbH
Publication of EP3704356A1 publication Critical patent/EP3704356A1/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Withdrawn legal-status Critical Current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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • 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
    • F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
    • F01K19/10—Cooling exhaust steam other than by condenser; Rendering exhaust steam invisible
    • 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/36—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of positive-displacement type
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/38—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type

Definitions

  • the invention relates to a method and a device for increasing the energy efficiency in Clausius-Rankine cycles.
  • heat is efficiently converted into mechanical or electrical energy using circulating media.
  • Circulation media (used in the so-called Organic Rankine Cycle "ORC" processes) .
  • Circulation media usually have a higher vapor pressure and a lower enthalpy of vaporization than water / steam and could better use the available heat source; In many cases, these circulation media are guided in hermetically closed circuits. Most of these
  • Circulation media belong to the “dry” or "drying"
  • Fig. 1 shows a corresponding circuit diagram, based on an ORC process, according to the prior art, which, for example, for use in geothermal
  • thermo water geothermal water
  • Production bore (1) passes through a filter (2) and a thermal water line (3) in the steam generator (4), where this gives off its heat and is cooled; the cooled
  • the connecting channel (17) connects on the side of the thermal water, the evaporator (16) and the preheater (14).
  • the steam produced in the steam generator (4), saturated or at most slightly overheated, is a
  • Overheating (with respect to the temperature and the heat content) in itself, is derived via the exhaust steam line (20), cooled in the recuperator (12) to just below its saturation temperature and passes through the cold exhaust steam line (21) in the
  • recuperator (12) aside, it would be possible to extract an additional amount of heat from the thermal water, which increases the power to be dissipated at the exhaust-steam condenser (8), so that no increase in efficiency can be achieved.
  • the example shows the application in geothermal power plants, but can, in an analogous manner instead of the thermal water, other (liquid, vapor and gaseous) heat transfer medium, for.
  • thermal water other (liquid, vapor and gaseous) heat transfer medium
  • hot water streams from large condensate networks or hot heat transfer oil flows from heat recovery systems, exhaust, hot air or compressed air streams to use for
  • the patent DE 10 2012 220 188 B4 shows z. B. how a symbiotic ORC process for using the
  • Intercooling in compressor stations can be used to drive the performance of such compressor stations
  • organic fluid-derived HD and LP vapors are expanded in sitting on a common shaft turbines. It would be conceivable, even a single heat flow (eg thermal water) to flow first through the HD and then through the LP boiler, whereby the desired further cooling of the
  • Turbine or the expansion machine require; about the Availability and application of such a turbine or
  • Patents disclose thermodynamic systems in the subcritical process management, so that in these
  • the object of the invention is to provide the energy and cost efficiency of the Rankine cycle cycle
  • the invention describes a method for increasing the
  • Circulation medium evaporated in a steam generator with heat absorption from the heat source and, where appropriate, superheated and this steam via a main steam line a
  • Expansion machine or turbine for generating the mechanical energy is supplied, there expands and condenses the exhaust steam of the expansion machine or turbine with the release of residual heat outside the cycle, characterized
  • the method is characterized in that the circulating medium is water or steam or carbon dioxide or else another inorganic chemical compound; that the circulating medium ethanol or another
  • the circulation medium is a synthetic circulatory medium; that the circulation medium is a mixture consisting of two or more components; that the circulation medium is a mixture with a lowered freezing point, ie an antifreeze mixture, such. Water and glycol or ethanol; that the circulation medium is a zeotropic mixture which distils apart during heat uptake; that the circulation medium is a sorptive mixture which desorbs the volatile component during heat absorption and absorbs it during mixing; that the circulating medium belongs to the dry class, which in an expansion away from the wet steam area; that the circulation medium is operated subcritically in a steam generator and the steam generator (4) heating surfaces for
  • the number of branches (24) is greater than the number of mixers (31) ( Figures 2, 8); in that at least one mixer, preferably the medium-pressure mixer (31MD), has two or more admixed inlets, preferably the two admixed inlets (32 b and 32 c) (FIGS. 2, 8); in that the mixer (31) has a nozzle or a nozzle group (34) with which the branched stream is introduced into the interior of the mixer (FIG. 4); in that the mixer (31) has filling bodies (36), which via a trickling device (37) with the branched-off stream
  • Circuit process outputs (Fig. 2, Fig. 8); that the heat exchanger (28ND) in the connection line (25ND) to the low pressure mixer (31ND) the overheating and the
  • branches (24b and / or 24c) are made by distributors and / or collectors (43) of the preheater (14), its heating surface packs (42) or its connecting lines ( Figure 7); that branches (24b and / or 24c) from the mantle space of
  • Bypass return line (46) is supplied to the main stream (Fig. that the throughput and the state of the sequence (30) of the
  • Connection path (25) by the feed pump (27), or the heat exchanger (28), or the armature (29) is controlled such that the state in the cold exhaust duct (21) comes to rest near the saturation line ( Figure 3).
  • the throughput of the inflow to the connecting line (25) is regulated via the bypass branch (44) and the bypass control flap (45) such that the temperature of the circulating medium in the bypass return line (46) and in a return line (5) of the heat carrier is almost the same ( Fig. 10); that the branch (24 b and / or 24 c) takes place at the location where the preheat temperature at this branch is equal to or higher than the steam saturation temperature in the exhaust steam line (20MD).
  • the invention describes an energy conversion device for increasing the energy efficiency in Clausius-Rankine cycle processes for the use of heat from heat sources,
  • Circular process is made available and converted there into mechanical or electrical energy, in which a condensate of a circulating medium via a condensate line fed to a condensate pump and is pressurized by this, this cycle medium in a steam generator below
  • Heat absorption from the heat source evaporated and optionally superheated and this steam is supplied via a steam line expansion machine or turbine for generating the mechanical energy, there expands and condenses the exhaust steam of the expansion machine or turbine with the release of residual heat outside the cycle, characterized
  • At least one branch (24) is provided, which is a current from the main stream of the
  • Mixer (31) opens, which the branched stream with the exhaust steam from the exhaust steam line (20) of the expansion machine or the turbine (19), provided via the steam supply line (33), mixed and this mixed stream over the
  • Circuit process is continued and continued (Fig. 2, Fig. 8).
  • the device comprises a steam generator (4) with heating surfaces for preheating (14), for evaporation (16) and optionally for overheating of the circulation medium and the
  • Circulation medium is operated subcritically in the steam generator (Fig. 2, Fig. 8); the device has a steam generator (4) with heating surfaces for preheating (14) and for reheating (16) the circulating medium and the circulating medium in the steam generator is operated supercritically (FIG. 2); that the feed line (11) to the boiler feed line (13), optionally via a valve and or a branch (24a) closes ( Figure 8, Fig. 2); the number of branches (24) is greater than the number of mixers (31) ( Figures 2, 8); in that at least one mixer, preferably the medium-pressure mixer (31MD), has two or more admixed inlets, preferably the two admixed inlets (32 b and 32 c) (FIGS.
  • the device has a steam generator (4) with heating surfaces for preheating (14) and for reheating (16) the circulating medium and the circulating medium in the steam generator is operated supercritically (FIG. 2); that the feed line (11) to the boiler feed line (13), optionally via
  • the mixer (31) has a nozzle or a nozzle group (34) with which the branched stream is introduced into the interior of the mixer (FIG. 4); in that the mixer (31) has filling bodies (36) which, via the sprinkling device (37), are connected to the diverted stream
  • Circuit process outputs (Fig. 2, Fig. 8); that the heat exchanger (28ND) in the connection line (25ND) to the low pressure mixer (31ND) the overheating and the
  • branches (24b and / or 24c) are made by distributors and / or collectors (43) of the preheater (14), its heating surface packs (42) or its connecting lines ( Figure 7); that branches (24b and / or 24c) from the mantle space of
  • Bypass return line (46) is supplied to the main stream (Fig. 10); that the throughput and the state of the sequence (30) of the
  • Connection path (25) by the feed pump (27), or the heat exchanger (28), or the armature (29) is controlled such that the state in the cold exhaust duct (21) comes to rest near the saturation line ( Figure 3).
  • the flow rate of the inflow to the connecting section (25) is regulated via the bypass branch (44) and the bypass control flap (45) such that the temperature of the circulating medium in the bypass return line (46) and in the return line (5) of the heat carrier is almost the same ( Fig. 10); that the branch (24 b and / or 24 c) takes place at the location where the preheat temperature at this branch is equal to or higher than the steam saturation temperature in the exhaust steam line (20MD).
  • Fig. 1 shows the known, practiced and already described prior art in ORC processes.
  • Fig. 2 shows an exemplary, simplified
  • FIGS. 7 to 10 show advantageous integrations of
  • FIG. 8 shows an overall process flow diagram with a steam generator in which the circulating medium is guided on the shell side.
  • Fig. 2 shows the scheme of the invention
  • Circular process the cycle according to the invention has no Recuperator, however, some components are similar to the ORC cycle process of the current state of the art. in the
  • the mixer (31) has
  • the mixer on the main flow side, a steam supply line (33) for the exhaust steam and a steam discharge line (35) for the cold exhaust steam; on the side of the branched stream, the mixer usually has a
  • a medium-pressure mixer (31MD) between the exhaust steam line (20MD) and the cold exhaust steam line (21MD) is provided.
  • the significant increase in energy efficiency is due to the fact that the mixed branched stream completely evaporates at the expense of overheating in the main stream, and a higher vapor stream for expansion is available to the medium pressure turbine (19MD), resulting in more power at the medium pressure turbine.
  • Turbine (19MD) leads. This effect can be increased by the
  • Preheating temperature at this branch is less than or equal to the steam saturation temperature in the exhaust steam line (20MD). In a further increased preheating of the
  • Utilization of a heat exchanger (28), can take place after the throttling valve (29) or in the mixer (31) itself an additional relaxation steam generation, which can provide a further increase in energy efficiency.
  • the cyclic process according to the invention is also suitable for supercritical process control; in this supercritical operation on the steam generator side, by the choice of a corresponding circulation medium and the steam generator pressure, the fürlauf redesign (14, 15, 16) mentally in one
  • Heat transfer medium and the circulation medium is the lowest.
  • An additional efficiency-increasing measure is to remove the overheated exhaust steam from the exhaust steam line (20ND)
  • Abdampfkondensator (8) which is a capacitor with a
  • Heat exchanger surface is to supply. To this positive To explain the effect, one must include the design of the affected apparatus: with the proposed arrangement to avoid the poor heat transfer of the overheated
  • the resulting increase in energy efficiency of the above measures can be estimated at 10 to 15%.
  • the desuperheating in the mixer (31ND) before the surface condenser can of course be increased and also a (partial)
  • Connecting piece (25ND) contains a heat exchanger (28ND), which heat (eg. To the environment or to a
  • downstream surface condensation in the exhaust steam condenser (8) can be dispensed with.
  • Evaporator takes place on the heat carrier side an exhaust gas condensation, even more efficiency increases are possible.
  • FIG. 3 shows the
  • thermodynamic properties of the selected cyclic medium characterized by its thermodynamic properties
  • the condition of the circulating medium of the saturated steam line away, that is superheated, it is in the present case and a "dry" circulating medium, such as.
  • the drawn, clockwise curve already outlines the characteristics of the cycle, with its respective states (temperature, pressure and entropy) of the circulation medium.
  • the circulation medium of the boiler feed line (13) is preheated in the preheaters (14) up to the boiling limit, in the
  • the high-pressure turbine (19HD) expands the live steam to the exhaust steam condition in the exhaust steam line (20MD); Since the example shown is a circulating medium of the "dry" fluid class, the steam overheats during the expansion.
  • the overheating of the exhaust steam from the medium pressure exhaust steam line (20MD) is overheated Mitteltik- mixer (31MD) by the controlled admixing of the branched stream of the branch (24c), which over the inlet (26c), the connecting line (25c), the outlet (30c) and the admixing inlet (32c) is reduced to the maximum extent so that the steam condition in the cold exhaust steam line (21MD) comes close to the saturated steam line.
  • the low-pressure mixer (31ND) manages the desuperheating of this exhaust steam from the low-pressure exhaust steam line (20ND), also by mixing in a branched-off flow, which comes from the condensate line (9).
  • the branched stream from the branch (24ND) passes via the inlet (26ND) of the connecting line (25ND) to its outlet (30ND), which merges into the admixing inlet (32ND); there - again simplistic - within this connecting section no heat exchanger
  • the amount of branched stream is preferably controlled so that the vapor state on the cold low pressure exhaust stream (21ND) substantially
  • the branched stream can also be branched off from the feed line (11), ie after the condensate pump (10), at an increased pressure, from the branch (24a); This was not shown separately in the present diagram, since the curves and states are nearly identical to those of the illustrated diagram.
  • the mixers (31) can be designed differently, as the following examples show:
  • FIG. 4 shows an embodiment of the mixer (31), with a steam supply line (33) adjoining the exhaust steam line (20), and a steam outlet (35), which opens into the cold exhaust steam line (21), the branched stream being via the outlet (30) of the connecting line (25) reaches the mixing inlet (32) of the mixer and is brought there via a nozzle or a nozzle group (34) in the interior of the mixer.
  • Fig. 5 shows an embodiment of the mixer as a trickle, with a steam supply line (33), a Zumischeintritt (32), with
  • the actual mixer (31) can also be followed by a liquid separator (40) for reducing the wetness or for prolonging the contact time.
  • This liquid separator can, for. B. as
  • Moist collecting cyclone or as a "demister”, with a wire mesh packing to catch moisture drops
  • Liquid is discharged via a liquid drain (41) and preferably added to the main stream of the process or recycled.
  • the branches can also be performed differently, such.
  • B the high-pressure branch (24HD) shown in FIG. 2, which the steam wetness from the (wet)
  • branched stream always equal the states in the main stream at the branch).
  • the heat carrier is guided on the tube side and the circulation medium on the jacket side, as shown in FIG. 8, then the branches (24b and 24c) are formed on the jacket of the preheater (14), in the form of removal nozzles.
  • At least one mixer is provided.
  • Fig. 9 shows a variant, in particular to Fig. 7. It may in fact structurally and operationally advantageous if the
  • the branched stream of the circulation medium in the branch (24) before the condensate pump (10) is removed, with the feed pump (27) to the heat exchanger ( 28), and brought via a fitting (29) to the outlet (30) of the connecting section (25) .
  • the outlet (30) of the connecting section (25) is advantageously connected to the medium-pressure mixer (31MD).
  • Fig. 10 shows a variant of Fig. 9, with the same
  • thermodynamic effect and the same invention features.
  • bypass branch (44), and possibly via a bypass control flap (45) is removed.
  • the cooled heat transfer medium is via the bypass return line (46) possibly the main flow of the
  • Mixer for the printing levels HD, MD or ND

Landscapes

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

Abstract

L'invention vise à améliorer l'efficacité en termes d'énergie et de coûts de processus fonctionnant selon le cycle de Clausius Rankine, en particulier pour l'utilisation de chaleur à basse température et à éviter les inconvénients des processus connus. Des embranchements (24) sont prévus dans la partie d'absorption de la chaleur du processus cyclique, lesquels dévient des flux du flux principal du fluide circulant, relient ceux-ci à des mixeurs (31), dans lesquels les flux déviés sont mélangés à de la vapeur d'échappement issue de conduits (20) de vapeur d'échappement des machines d'expansion ou des turbines (19), et lesdits flux de vapeur mélangés sont transférés dans le processus cyclique par l'intermédiaire de conduits de vapeur d'échappement à froid (21). Il résulte une hausse significative de l'efficacité en termes d'énergie lors de l'utilisation de fluides circulants de la classe « asséchante ». Les flux ajoutés s'évaporent totalement au détriment de la surchauffe dans le flux principal. Un flux de vapeur plus important est fourni aux fins de l'expansion à la turbine à pression moyenne (19MD), ce qui donne lieu à une puissance décuplée sur les turbines allant de 10 à 15 %.
EP19730251.6A 2018-05-29 2019-05-28 Procédé et dispositif servant à convertir une énergie thermique en une énergie mécanique ou électrique Withdrawn EP3704356A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA154/2018A AT521050B1 (de) 2018-05-29 2018-05-29 Verfahren zur Steigerung der Energieeffizienz in Clausius-Rankine-Kreisprozessen
PCT/AT2019/060179 WO2019227117A1 (fr) 2018-05-29 2019-05-28 Procédé et dispositif servant à convertir une énergie thermique en une énergie mécanique ou électrique

Publications (1)

Publication Number Publication Date
EP3704356A1 true EP3704356A1 (fr) 2020-09-09

Family

ID=66857589

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19730251.6A Withdrawn EP3704356A1 (fr) 2018-05-29 2019-05-28 Procédé et dispositif servant à convertir une énergie thermique en une énergie mécanique ou électrique

Country Status (3)

Country Link
EP (1) EP3704356A1 (fr)
AT (1) AT521050B1 (fr)
WO (1) WO2019227117A1 (fr)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH665451A5 (de) * 1983-07-19 1988-05-13 Bbc Brown Boveri & Cie Verfahren zum reinigen und entgasen des kondensates/speisewassers im kreislauf einer stromerzeugungsanlage.
US5531073A (en) * 1989-07-01 1996-07-02 Ormat Turbines (1965) Ltd Rankine cycle power plant utilizing organic working fluid
DE4409197A1 (de) * 1994-03-17 1995-09-21 Siemens Ag Verfahren und Einrichtung zur solaren Dampferzeugung
US5555731A (en) 1995-02-28 1996-09-17 Rosenblatt; Joel H. Preheated injection turbine system
US7185736B2 (en) * 2003-08-25 2007-03-06 Fisher Controls International Llc. Aerodynamic noise abatement device and method for air-cooled condensing systems
WO2008125827A2 (fr) * 2007-04-13 2008-10-23 City University Appareil et procédé à cycle de rankine organique
US8544274B2 (en) 2009-07-23 2013-10-01 Cummins Intellectual Properties, Inc. Energy recovery system using an organic rankine cycle
US8752381B2 (en) * 2010-04-22 2014-06-17 Ormat Technologies Inc. Organic motive fluid based waste heat recovery system
US9074491B2 (en) * 2012-09-05 2015-07-07 General Electric Company Steam cycle system with thermoelectric generator
DE102012220188B4 (de) 2012-11-06 2015-05-13 Siemens Aktiengesellschaft Integrierter ORC-Prozess an zwischengekühlten Kompressoren zur Erhöhung des Wirkungsgrades und Verringerung der erforderlichen Antriebsleistung durch Nutzung der Abwärme
EP3118424B1 (fr) 2015-07-16 2020-05-20 Orcan Energy AG Reglages de processus orc par pulverisation d'un fluide non evapore
DE102015118098A1 (de) * 2015-10-23 2017-04-27 Mitsubishi Hitachi Power Systems Europe Gmbh Verfahren zur Speisewasservorwärmung eines Dampferzeugers eines Kraftwerks
MX2018014295A (es) * 2016-06-17 2019-03-14 Siemens Ag Recirculacion de condensacion de agua.

Also Published As

Publication number Publication date
AT521050B1 (de) 2019-10-15
AT521050A4 (de) 2019-10-15
WO2019227117A1 (fr) 2019-12-05

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