EP1998013A2 - Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen - Google Patents

Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen Download PDF

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Publication number
EP1998013A2
EP1998013A2 EP07425218A EP07425218A EP1998013A2 EP 1998013 A2 EP1998013 A2 EP 1998013A2 EP 07425218 A EP07425218 A EP 07425218A EP 07425218 A EP07425218 A EP 07425218A EP 1998013 A2 EP1998013 A2 EP 1998013A2
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EP
European Patent Office
Prior art keywords
turbine
work fluid
fluid
electric energy
main
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Withdrawn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
EP07425218A
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English (en)
French (fr)
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EP1998013A3 (de
Inventor
Mario Gaia
Roberto Bini
Andrea Duvia
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.)
Turboden SpA
Original Assignee
Turboden SpA
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 Turboden SpA filed Critical Turboden SpA
Priority to EP07425218A priority Critical patent/EP1998013A3/de
Publication of EP1998013A2 publication Critical patent/EP1998013A2/de
Publication of EP1998013A3 publication Critical patent/EP1998013A3/de
Withdrawn legal-status Critical Current

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    • 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
    • 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
    • F01K7/02—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 multiple-expansion type
    • F01K7/025—Consecutive expansion in a turbine or a positive displacement engine

Definitions

  • This invention concerns in general a system for producing electric energy starting from high temperature fumes or gas coming from any type of heat source.
  • the invention concerns an apparatus for generating electric energy with a turbogenerator operating according to the Rankine cycle with organic work fluid (ORC).
  • ORC organic work fluid
  • a system for the production of electric energy of the type taken into consideration basically comprises: a source of fumes or gas at a high temperature, a heat exchanger between the fumes and a thermovector fluid circulating in an intermediate circuit, a heat exchanger between the intermediate thermovector fluid and an organic work fluid for the evaporation of the latter, a turbine (hereafter named the main turbine) fed by the work fluid vapour and connected to an electric generator, a regenerator for the recovery of the thermal content of the work fluid vapour, a condenser of the working fluid before it is recycled.
  • diathermic oil is used as an intermediate thermovector fluid and silicone oil as an operating fluid.
  • the diathermic oil is made to circulate in a coil around which circulate the fumes or gasses at high temperature. Then it heats the operating fluid so as to generate vapour which feeds the turbo-generator.
  • the fluid vapour temperature is usually around 270°C and that of the condensation about 100°C.
  • the output temperature specified is not normally exceeded.
  • the aim of this is to limit the expansion ratio of the turbine, which is often equipped with a small number of stages (for example two) and to avoid too great a difference in length of the blades in the passage from the first to the last stage.
  • one objective of this invention is to create the conditions for lowering the feed pressure of the main turbine compared to the evaporation pressure or otherwise to increase the evaporation pressure to noticeably improve the cycle efficiency.
  • the objective is reached according to the present invention by the adoption on the work fluid path, upstream of the main turbine, of at least one auxiliary turbine in which a pre-expansion of the work fluid is realised and an additional coaxial electric generator, assembled on the auxiliary turbine drive with a high speed rotation shaft aimed at optimising the power extraction from the pre-expansion of the work fluid.
  • the system here proposed basically comprises, in association with a source of high temperature fumes - not shown, a turbogenerator group 10 using organic work fluid running in a relative circuit 11 and, between the fumes source and the turbogenerator, an intermediate circuit for a thermal carrier fluid 12.
  • the turbogenerator group 10 comprises a main turbine 13 with a respective electric generator 13'.
  • the turbine is downstream of the heat exchanger group that comprises a pre-heater 17, an evaporator 14 the work fluid and a possible superheater 15 of the feed vapour of said turbine.
  • the fluid on exiting the main turbine 13 is directed into a work fluid condenser 16 and at least one regenerator 16', using the heat of the vapour to preheat the work fluid.
  • the high temperature fumes by means of a primary heat exchanger - not shown, heat the thermal carrier fluid circulating in the intermediate circuit 12 and are directed immediately to a chimney or through a pre-heater used to pre-heat the comburent air to be fed to the combustor and a possible economizer used to heat a liquid for various purposes - not shown.
  • the heated thermal carrier fluid On exiting the intermediate heat exchanger, the heated thermal carrier fluid is made to circulate, in the direction of the arrows F in Fig. 1 , in the superheater 15, if provided, and in the evaporator 14 to produce the feed vapour of the main turbine 13 before returning in cycle in the intermediate circuit through the pre-heater 17 for the work fluid.
  • the heat exchangers indicated may be set up as separate bodies or may be integrated in a single unit fulfilling the indicated functions.
  • auxiliary turbine 19 which creates a first expansion, or pre-expansion, of the fluid and the output of which is connected to the input of the main turbine.
  • Said auxiliary turbine 19 is equipped with a respective coaxial electric generator 19', assembled on the shaft 20 of the turbine, with a high rotation speed sufficient to optimise the power extraction from the pre-expansion.
  • the electric generator 19' connected to the auxiliary turbine 19 is preferably the permanent magnets type and with a rated capacity sufficiently high to enable operating without the intervention of adjustment devices in all the function field of the main turbine.
  • the auxiliary turbine 19 is preferably equipped with variable section nozzles to optimise its operating to the different loads that is in the presence of varying vapour flow-rate.
  • inlet and discharge volutes 21, 21' - Fig. 3 - designed to keep their volume as small as possible so that the fluid content of these volutes does not increase the overspeed of the main turbine in the case of sudden lack of load, with consequent rapid closure of the input valves to the turbines.
  • the auxiliary turbine 19, besides, must be equipped with a sealing system so as to avoid access of high temperature work fluid into the area the coaxial electric generator turns in.
  • an annular chamber 22 is provided which is isolated with regards to the chamber in which the rotor turns by a labyrinth seal 23 made according to the known techniques and maintained at a pressure close to the one of the condenser 16 thanks to a duct 24 connected to the condenser itself.
  • the cross section of the duct 24 must be such so as to enable the fluid leaking through the labyrinth seal to be transferred to the condenser at an acceptable loss of pressure.
  • the sealing system on the shaft will then have, according to the known technique, a mechanical seal, a further labyrinth seal.
  • a further innovative aspect consists in the injection in the zone of said ring shaped chamber 23, by means of another duct 25, of a small amount of liquid work fluid, correctly filtered, coming from circuit 11 and which evaporating at a pressure close to that of the condenser, guarantees to cool the shaft 20 and adjacent devices.
  • an interesting aspect deriving from the use of the auxiliary turbine is the possibility of using an auxiliary turbine with a few robust blades, for example made by milling from a solid piece in the rotor disk, or by casting, maintaining between the length of the blade and axial chord of the blade a low ratio, for example less than a unit.
  • auxiliary turbine becomes a robust device capable to smooth the flow of vapour fed to the main turbine, above all in relation to the risk of dragging "plugs" of liquid during transient periods.
  • the auxiliary turbine 19 can be made with the discharge volute integrated with the input volute of the main turbine according to the illustrative diagrams in Figs. 4 and 5 .
  • the work fluid circuit downstream of the evaporator and possible superheater, can be equipped with a shunted line 28 with a control valve 28' to bypass the auxiliary turbine 19, both in the case of a breakdown of the latter and for its maintenance, and to feed the main turbine 13 with an increase in delivery.
  • This delivery has a lower pressure compared to the evaporation temperature of the remaining delivery crossing through the main evaporator. Therefore it will be possible to produce a shunted delivery with an exchanger/secondary evaporator with a smaller surface compared to the surface which would be needed for a counter requirement to evaporate the same delivery of work fluid at the pressure of the main evaporator.
  • Said exchanger/secondary evaporator 29 can be fed by a separate pump and pre-heater, positioned in parallel compared with the main evaporator 14, but as an alternative and preferably, as shown in Fig.2 , the secondary evaporator 29 will be fed with the liquid work fluid collected downstream of the pre-heater 17 and appropriately reduced in pressure in a throttle valve 30 upstream of the secondary evaporator.

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)
  • Control Of Turbines (AREA)
EP07425218A 2007-04-16 2007-04-16 Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen Withdrawn EP1998013A3 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07425218A EP1998013A3 (de) 2007-04-16 2007-04-16 Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07425218A EP1998013A3 (de) 2007-04-16 2007-04-16 Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen

Publications (2)

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EP1998013A2 true EP1998013A2 (de) 2008-12-03
EP1998013A3 EP1998013A3 (de) 2009-05-06

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EP07425218A Withdrawn EP1998013A3 (de) 2007-04-16 2007-04-16 Vorrichtung zur Erzeugung von elektrischer Energie unter Verwendung von Hochtemperaturgasen

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Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBS20090224A1 (it) * 2009-12-16 2011-06-17 Turboden Srl Sistema e metodo per la produzione di energia elettrica a partire da sorgenti termiche a temperatura variabile
WO2011093854A1 (en) * 2010-01-27 2011-08-04 United Technologies Corporation Organic rankine cycle (orc) load following power generation system and method of operation
DE102010048292A1 (de) * 2010-10-14 2012-04-19 Rwe Innogy Gmbh Verfahren zum Betrieb eines Niedertemperaturkraftwerks
US20130160448A1 (en) * 2010-06-10 2013-06-27 Turboden S.R.L. Orc plant with a system for improving the heat exchange between the source of hot fluid and the working fluid
CN103195530A (zh) * 2013-03-29 2013-07-10 中国科学院理化技术研究所 带有分离膨胀装置的有机朗肯循环余热回收发电系统
DE102012021326A1 (de) * 2012-10-26 2014-04-30 Voith Patent Gmbh Verfahren zum Erzeugen von elektrischer Energie und Energieerzeugungsanlage
WO2014117074A1 (en) * 2013-01-28 2014-07-31 Echogen Power Systems, L.L.C. Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
CN105247174A (zh) * 2013-05-30 2016-01-13 通用电气公司 废热回收的系统及方法
WO2016032737A1 (en) * 2014-08-28 2016-03-03 Eaton Corporation Optimized performance strategy for a multi-stage volumetric expander
US9284855B2 (en) 2010-11-29 2016-03-15 Echogen Power Systems, Llc Parallel cycle heat engines
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9458738B2 (en) 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US9593597B2 (en) 2013-05-30 2017-03-14 General Electric Company System and method of waste heat recovery
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
CN114542226A (zh) * 2022-02-21 2022-05-27 湖南泛航智能装备有限公司 一种基于orc余热回收用的透平膨胀发电系统及优化方法
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system
US12331664B2 (en) 2023-02-07 2025-06-17 Supercritical Storage Company, Inc. Waste heat integration into pumped thermal energy storage
US12516855B2 (en) 2022-10-27 2026-01-06 Supercritical Storage Company, Inc. High-temperature, dual rail heat pump cycle for high performance at high-temperature lift and range

Citations (2)

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WO2004102082A2 (en) 2003-05-09 2004-11-25 Recurrent Resources Method and apparatus for acquiring heat from multiple heat sources
WO2008101711A2 (de) 2007-02-25 2008-08-28 Deutsche Energie Holding Gmbh Mehrstufiger orc-kreislauf mit zwischenenthitzung

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DE3261410D1 (en) * 1981-04-03 1985-01-17 Bbc Brown Boveri & Cie Combined steam and gas turbine power plant
FI913367A0 (fi) * 1991-07-11 1991-07-11 High Speed Tech Ltd Oy Foerfarande och anordning foer att foerbaettra nyttighetsfoerhaollande av en orc-process.
DE69938039T2 (de) * 1999-07-23 2009-01-22 Exergy, Inc., Hayward Methode und Anlage zur Umwandlung von Wärme in nützliche Energie
CN100406685C (zh) * 2003-04-30 2008-07-30 株式会社东芝 中压蒸汽轮机、蒸汽轮机发电厂及其运转方法

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
WO2004102082A2 (en) 2003-05-09 2004-11-25 Recurrent Resources Method and apparatus for acquiring heat from multiple heat sources
WO2008101711A2 (de) 2007-02-25 2008-08-28 Deutsche Energie Holding Gmbh Mehrstufiger orc-kreislauf mit zwischenenthitzung

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US9458738B2 (en) 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US9115605B2 (en) 2009-09-17 2015-08-25 Echogen Power Systems, Llc Thermal energy conversion device
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
ITBS20090224A1 (it) * 2009-12-16 2011-06-17 Turboden Srl Sistema e metodo per la produzione di energia elettrica a partire da sorgenti termiche a temperatura variabile
WO2011093854A1 (en) * 2010-01-27 2011-08-04 United Technologies Corporation Organic rankine cycle (orc) load following power generation system and method of operation
US20130160448A1 (en) * 2010-06-10 2013-06-27 Turboden S.R.L. Orc plant with a system for improving the heat exchange between the source of hot fluid and the working fluid
US9016063B2 (en) * 2010-06-10 2015-04-28 Turboden S.R.L. ORC plant with a system for improving the heat exchange between the source of hot fluid and the working fluid
DE102010048292A1 (de) * 2010-10-14 2012-04-19 Rwe Innogy Gmbh Verfahren zum Betrieb eines Niedertemperaturkraftwerks
US9410449B2 (en) 2010-11-29 2016-08-09 Echogen Power Systems, Llc Driven starter pump and start sequence
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US9284855B2 (en) 2010-11-29 2016-03-15 Echogen Power Systems, Llc Parallel cycle heat engines
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
DE102012021326A1 (de) * 2012-10-26 2014-04-30 Voith Patent Gmbh Verfahren zum Erzeugen von elektrischer Energie und Energieerzeugungsanlage
DE102012021326B4 (de) * 2012-10-26 2014-05-15 Voith Patent Gmbh Verfahren zum Erzeugen von elektrischer Energie und Energieerzeugungsanlage
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
WO2014117074A1 (en) * 2013-01-28 2014-07-31 Echogen Power Systems, L.L.C. Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
CN103195530A (zh) * 2013-03-29 2013-07-10 中国科学院理化技术研究所 带有分离膨胀装置的有机朗肯循环余热回收发电系统
CN103195530B (zh) * 2013-03-29 2015-04-15 中国科学院理化技术研究所 带有分离膨胀装置的有机朗肯循环余热回收发电系统
US9593597B2 (en) 2013-05-30 2017-03-14 General Electric Company System and method of waste heat recovery
CN105247174A (zh) * 2013-05-30 2016-01-13 通用电气公司 废热回收的系统及方法
US9587520B2 (en) 2013-05-30 2017-03-07 General Electric Company System and method of waste heat recovery
WO2016032737A1 (en) * 2014-08-28 2016-03-03 Eaton Corporation Optimized performance strategy for a multi-stage volumetric expander
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system
CN114542226A (zh) * 2022-02-21 2022-05-27 湖南泛航智能装备有限公司 一种基于orc余热回收用的透平膨胀发电系统及优化方法
CN114542226B (zh) * 2022-02-21 2024-05-14 湖南泛航智能装备有限公司 一种基于orc余热回收用的透平膨胀发电系统及优化方法
US12516855B2 (en) 2022-10-27 2026-01-06 Supercritical Storage Company, Inc. High-temperature, dual rail heat pump cycle for high performance at high-temperature lift and range
US12331664B2 (en) 2023-02-07 2025-06-17 Supercritical Storage Company, Inc. Waste heat integration into pumped thermal energy storage

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