WO2008067855A2 - Procédé et dispositif d'augmentation de la puissance et du rendement d'un processus de centrale orc - Google Patents

Procédé et dispositif d'augmentation de la puissance et du rendement d'un processus de centrale orc Download PDF

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Publication number
WO2008067855A2
WO2008067855A2 PCT/EP2007/000918 EP2007000918W WO2008067855A2 WO 2008067855 A2 WO2008067855 A2 WO 2008067855A2 EP 2007000918 W EP2007000918 W EP 2007000918W WO 2008067855 A2 WO2008067855 A2 WO 2008067855A2
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WO
WIPO (PCT)
Prior art keywords
superheater
orc
heat exchanger
evaporator
heat
Prior art date
Application number
PCT/EP2007/000918
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German (de)
English (en)
Other versions
WO2008067855A3 (fr
Inventor
Joachim Kümmel
Original Assignee
Kuemmel Joachim
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 Kuemmel Joachim filed Critical Kuemmel Joachim
Priority to DE112007002289T priority Critical patent/DE112007002289A5/de
Publication of WO2008067855A2 publication Critical patent/WO2008067855A2/fr
Publication of WO2008067855A3 publication Critical patent/WO2008067855A3/fr

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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
    • 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
    • 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
    • F01K23/101—Regulating means specially adapted therefor
    • 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
    • F01K25/106—Ammonia
    • 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
    • F01K25/14—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 using industrial or other waste gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F22B31/04—Heat supply by installation of two or more combustion apparatus, e.g. of separate combustion apparatus for the boiler and the superheater respectively
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/18—Controlling superheat temperature by by-passing steam around superheater sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
    • F24T10/00—Geothermal collectors
    • 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
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/10—Geothermal energy

Definitions

  • the invention relates to a method for increasing the power and efficiency of an ORC power plant process according to the preamble of claim 1 and to an apparatus for increasing the power and efficiency of an ORC power plant process according to the preamble of claim 16.
  • the ORC (Organic Rankine Cycle) process is a thermodynamic cyclic process, and in ORC plants, thermal energy is converted into electricity at temperatures and pressures far below the levels commonly found in conventional steam power plants.
  • low-boiling vapors such as hydrocarbons, such as butane, pentane, propane, and hexane
  • NT heat low-temperature heat
  • MT heat medium-temperature heat
  • HT heat high-temperature heat
  • Fig. 7 exemplifies the circuit of a known geothermal ORC power plant in combination with a gas turbine power plant.
  • a combustion chamber 2 is preceded by an air compressor 3, and on the same shaft 5, a gas turbine 1 and a generator 4 generating current are arranged.
  • the exhaust gas 7 formed in the combustion chamber 2 is supplied to a heat recovery steam boiler 6, and the generated steam passes into a steam turbine 14, which sits in this example on a common shaft 15 of an ORC turbine 8 and an ORC generator 9.
  • the ORC turbine 8 is fed with the working medium vapor from an ORC evaporator 10.
  • the heat is supplied by thermal water 18, which at a temperature of about 100 ° to 165 ° C heat exchanger surfaces 11 fed in the evaporator 10, wherein heat to the compressed, liquid working fluid, such as liquid hydrocarbons, is discharged, so that the working fluid evaporates.
  • the cooled thermal water 19 is discharged at a temperature of about 80 ° C.
  • the ORC cycle is functionally closed after the ORC turbine 8 by a condenser 13 and a compression device 12, for example a recirculation pump.
  • Such geothermal power plants which emit low-temperature heat, have relatively low efficiencies due to the low enthalpy difference.
  • the ratio of investment costs and yield of electricity often does not reach the limit of economy.
  • NT waste heat from chemical, metallurgical and process engineering processes for example, cement plants
  • MT heat is also available for an ORC power plant, it is usually decoupled with the aid of a carrier medium, for example thermal oil, and coupled into the ORC evaporator.
  • the invention is based on the invention of providing a method and a device with which both the power and the efficiency of an ORC power plant process are significantly increased in order to achieve the required economy.
  • an ORC working fluid such as hydrocarbons of the general formula C n H mi without the interposition of a heat transfer medium, such as.
  • a heat transfer medium such as.
  • thermal oil to evaporate with NT heat and in addition by MT heat and / or HT heat and also to overheat the working medium vapors in the range of MT and / or HT heat.
  • the liquid and compressed working medium of the ORC plant is split into at least two waste heat streams, which produce a have different temperature level, preheated, evaporated and superheated.
  • a hot gas generator fired, for example, with bio-oil can be installed, whereby it can be integrated, for example, into an MT exhaust gas flow.
  • the method according to the invention for increasing the power and efficiency in the ORC power plant process is based on a circulating ORC working fluid which evaporates after compression in an evaporator with the aid of a low-temperature heat source and condenses after expansion in an ORC turbine in a condenser becomes.
  • the working medium vapor of the evaporator which may for example have about 145 ° C., is supplied to a superheater and superheated.
  • the superheated hot steam is fed to the ORC turbine for power generation.
  • the superheater is arranged separately and connected on the input side with the ORC evaporator via a steam line for the working medium vapor and the output side with the ORC turbine via a hot steam line for the superheated working medium vapor.
  • the ORC evaporator with a larger NT heat source such as thermal water
  • a heat extraction can also be done from smoke or process gases of a process plant as well as by direct evaporation of the liquid working fluid or by means of a thermal oil-heat extraction.
  • the superheater at least in two stages and to supply the working medium vapor from the evaporator to a first superheater stage and to a second superheater stage.
  • the working medium vapor is overheated and finally overheated in the second superheater stage.
  • a bypassing of the first superheater stage is provided, which may have a three-way valve and a bypass line.
  • Hydrocarbons for example butane, pentane, propane, hexane, or halogenated hydrocarbons, for example chlorocarbons, can advantageously be used as ORC working fluids.
  • Hydrogen or perfluoropentane, or ammonia are used and are evaporated using a low-temperature heat source in a temperature range of about 100 ° to 300 ° C.
  • the overheating of the working medium vapor in the superheater stages can be done by smoke or process gases or by heat radiation, with MT and / or HT heat sources can be used with a temperature of 300 ° C to a maximum of 800 ° C.
  • the heat exchanger surfaces are provided for preheating at least a subset of the recirculating, condensed and compressed working fluid.
  • the heat exchanger surfaces are connected downstream of the superheater stages for preheating and at least partial evaporation of the working fluid, the amount of exhaust gas supplied to the heat exchanger can be cooled lower than is possible for example in a heat extraction by means of thermal oil or steam.
  • the usable for electricity generation, decoupled Abissennenge is thus greater.
  • waste heat can be used in a heat exchanger system with migratory pinch point, with a corresponding control system optimizes the use of waste heat and contributes to increasing the efficiency of the system.
  • the pinch point PP is the smallest temperature difference between the cooling curves of the MT heat and the warm-up curves of the ORC working fluid.
  • control of this three-way valve for optimizing performance can be advantageously carried out with the aid of a control system, in particular a NC control system, for example a so-called split-range power controller, which is operatively designed as a follow-up control and divided control pulses of, for example, 4 to 16 mA for a three-way valve is formed between the two superheater stages and 16 to 20 mA for the three-way valve for the division or displacement of the amounts of working medium to be evaporated.
  • a control system in particular a NC control system, for example a so-called split-range power controller, which is operatively designed as a follow-up control and divided control pulses of, for example, 4 to 16 mA for a three-way valve is formed between the two superheater stages and 16 to 20 mA for the three-way valve for the division or displacement of the amounts of working medium to be evaporated.
  • a gas turbine in addition to thermal water, exhaust gases from other processes and MT heat-emitting plant, a gas turbine, a chemical, metallurgical or process engineering process and / or a fired with oil, gas or biomass hot gas generator can be used as NT heat source can.
  • a heat of condensation of the hot gases can be used in the heat exchanger surfaces for preheating or evaporation.
  • the Beitsstoff superheater used noble fuel quantity in the form of oil, gas or bio-fuel is emitted with high efficiency, since in the form of fuels additionally used energy no heat of condensation is lost.
  • the overall efficiency of the ORC system is thereby significantly increased and, depending on the temperature level of the NT heat source, rises from 9% to 13% to approximately 16% to 20%.
  • the efficiencies can be further increased by means of a directly fired superheater or by a hot gas generator connected upstream of the superheater stages and the heat exchanger surfaces.
  • Fig. 1 shows the basic circuit of an ORC power plant according to the invention
  • Fig. 3 shows the T-Q diagram of the ORC power plant according to the invention
  • FIG. 4 shows the circuit and flow diagram of a geothermal ORC power plant with coupling of the heat from a gas turbine plant
  • Fig. 5 is a circuit and flow diagram of a diesel engine power plant with an inventive integration of an ORC power plant and
  • Fig. 6 shows the circuit and flow diagram of FIG. 5 with an alternative
  • FIG. 1 shows an ORC power plant with an ORC turbine 8, a connected ORC generator 9, an evaporator 10 and a condenser 13, and a circulating ORC working fluid.
  • the ORC working fluid which, after expansion in the ORC turbine 8 in the condenser 13, which here is an air condenser, is liquefied and, via a compression device 12, for example a recirculation pump, in a working fluid line 22 as a subset to the evaporator 10. reached, with the aid of a low-temperature heat source 18, 19, which is thermal water in this embodiment, evaporated and then passes through a steam line 20 in a superheater 25th
  • the division of the compressed working fluid takes place in this embodiment by means of a second three-way valve 32 so that controllable subsets of the working fluid via a first line 22.1 the evaporator 10 and a second line 22.2 heat exchanger surfaces 24 for preheating and / or at least partial evaporation can be supplied.
  • a connecting line 23 the preheated or evaporated to the heat exchanger surfaces 24 working fluid enters the evaporator 10 and then via the steam line 20 in the superheater 25th
  • the superheater 25 is divided into a first superheater stage 25.1 and a second superheater stage 25.2, and a first three-way valve 31 enables steam temperature control by partial bypassing the first superheater stage 25.1. In this way, it can be ensured that the second superheater stage 25.2 is always supplied with the total amount of working medium vapor for a final superheating of the working medium vapor in all load cases. At the same time, the heat exchanger surface 24 can be acted upon by a larger, adjustable amount of heat.
  • the superheater 25 and the heat exchanger surface 24 for preheating and at least partial evaporation of at least a subset of the working fluid are arranged in this embodiment in an exhaust gas heat exchanger 26, which flows through, for example, exhaust gases 7 of a gas turbine power plant (see also Fig. 4) for direct extraction of MT heat becomes.
  • the heat exchanger surfaces 24 for preheating at least a subset of the compressed working fluid with respect to the flow direction of the exhaust gases 7 the superheater stages 25.1, 25.2 downstream.
  • the first superheater stage 25.1 is connected downstream for overheating the compressed working medium vapor of the second superheater stage 25.2, which serves for final superheating.
  • the working medium hot steam passes at a temperature of about 190 ° to 210 ° C in the ORC turbine 8 and is discharged by means of the generator 9.
  • a controllable, plant-specific amount of working fluid can be preheated and evaporated.
  • the decoupled waste heat quantity that can be used for electricity generation becomes larger.
  • FIGS. 2 and 3 show the cooling curves (TWT) with their areas of preheating (TE) 1 evaporation (Tv) and overheating (TUE) and their smallest temperature difference, which is referred to as pinch point (PP).
  • TWT cooling curves
  • TE preheating
  • Tv evaporation
  • TUE overheating
  • PP pinch point
  • T E i working medium preheater temperature which also indicates the decoupled preheating heat
  • Tv 2 working medium evaporator temperature which also indicates the decoupled heat of vaporization
  • T E2 working medium preheater temperature which also indicates the decoupled preheating heat.
  • the TQ diagram shows the change in the heat recordings and the temperature curves in the event that the heat absorption in the ORC evaporator 10 by a value X has decreased.
  • Such thermal power reduction in the ORC evaporator 10 may be due to temporary changes in the thermal water levels and / or temperatures, or from salt deposits on the ORC evaporator heating surfaces
  • the working medium vapor production can be increased by the amount by which the heat absorption of the working medium superheater stages 25.1, 25.2 in the ORC evaporator 10 decreases.
  • the corresponding division or displacement of the amounts of working medium to be evaporated from the ORC evaporator 10 into the heat exchanger surfaces 24 of the exhaust gas heat exchanger 26 is controlled by means of the second three-way valve 32.
  • Fig. 4 shows the circuit and flow diagram of a geothermal ORC power plant, in which an exhaust gas heat exchanger 26 of a gas turbine power plant with a gas turbine 1, a combustion chamber 2, an air compressor 3, a generator 4 and a common shaft 5 power and efficiency is integrated increasing ,
  • the ORC plant again consists of the main components evaporator 10, ORC turbine 8 with generator 9, condenser 13 and compression device 12, for example recirculation pump.
  • the geothermal heat of thermal water as NT heat source 18, 19 is supplied to the evaporator 10 and discharged as cooled thermal water 19.
  • the quantity distribution is effected by a second three-way valve 32 which is connected downstream of the recirculation pump and which is regulated by a control device, for example an NC power regulator 33.
  • the superheater 25 in turn consists of a first superheater stage 25.1 for preheating and a second superheater stage 25.2 for the final superheating of the working medium vapor supplied in a steam line 20.
  • the first superheater stage 25.1 can be partially loaded by the control device 33 depending on the operation, while the second Overheater stage 25.2 is always supplied with the entire working medium vapor quantity.
  • a power regulator such as a so-called split-range power regulator, which acts as a follow-up to the three-way valves 31, 32, for example, by divided control pulses of 4 to 16 mA for the first three-way valve 31 for the superheater stages 25.1, 25.2 and 16 to 20 mA for the second three-way valve 32 for the quantitative distribution of the compressed working fluid.
  • FIG. 5 shows the circuit and flow diagram of a diesel engine power plant 41, 42 with the integration of an ORC turbogenerator 8, 9 by means of a waste heat recovery plant 40 for the ORC working fluid.
  • the waste heat recovery plant 40 has heat exchanger surfaces 44 for preheating the condensed in the condenser 13 and compressed by means of the compression device 12 ORC working fluid, which passes through the working medium line 22 to the heat exchanger surfaces 44 and after preheating and partial evaporation via a connecting line 23 of an ORC evaporation 36th is supplied.
  • the heat exchanger surfaces 44 upstream of the MT and / or HT heat source with respect to the flow direction are heat exchanger surfaces or heating surfaces 43 for evaporating the working medium guided in a forced circulation with the ORC evaporation drum 36.
  • a circulation pump 37 is arranged in the forced circulation system.
  • the working medium vapor passes from the ORC evaporation drum 36 via a steam line 20 into a first superheater stage 45. 1, which is designed to be passable by means of a bypass line 27 and a first three-way valve 31.
  • a hot gas generator 46 Upstream of the waste heat recovery plant 40 is a hot gas generator 46, in which a second superheater stage 45.2 is integrated for the final superheating of the working medium vapor. From this final superheater stage 45.2, the superheated steam passes via a superheated steam line 21 to the ORC turbine 8.
  • cooled flue gases 47 are injected into the hot gas generator 46 via a recirculation channel 48 in order to reduce the hot gas temperature before the second superheater stage 45.2 or the final superheater of the working medium to approximately 650 ° C., maximum 780 ° C. This counteracts a cracking operation of the superheated working medium vapor and prolongs the life of the recirculating ORC working fluid.
  • the exhaust gases 38 of the diesel engine 41 pass through an engine exhaust duct 39 into an exhaust gas collector 49, which is also supplied with the hot gases 35 from the hot gas generator 46.
  • An effective-fine fine-tuning takes place with the aid of a control system 51 which regulates the admission of the first superheater stage 45.1 and the fuel supply 50 for the hot gas generator 46 as a function of the turbine output.
  • the efficiency of the diesel engine power plant is increased from about 40% to 42% to 45% to 52% by the invented combined hot gas generator - ORC technology.
  • Fig. 6 shows in principle the system according to Fig. 5 and has the same reference numerals for identical features.
  • the evaporator heat exchanger surfaces 43 are connected as a continuous evaporator. In this way, an optimization of the pinch point (PP) situation described in connection with FIGS. 2 and 3 and a reduction of the flue gas temperature in the exhaust pipe 53 can be achieved.
  • PP pinch point
  • the system according to FIG. 6 enables a further increase in the efficiency of an ORC power plant process. Associated with this are an improvement in economic efficiency and a wider utilization of the available MT, NT and HT heat.

Abstract

L'invention concerne un procédé et un dispositif d'augmentation de la puissance et du rendement d'un processus de centrale ORC (cycle de rankine organique). Selon l'invention, un fluide de travail ORC essentiellement évaporé à l'aide d'une source de chaleur basse température, est surchauffé à l'aide d'une source de chaleur moyenne température et/ou d'une source de chaleur haute température. La surchauffe de la vapeur de fluide de travail est réalisée dans un surchauffeur séparé, divisé en au moins un premier étage de surchauffeur partiellement alimenté en fluide de travail, et un deuxième étage de surchauffeur entièrement alimenté en fluide de travail. Le dispositif selon l'invention comporte également des surfaces d'échange thermique pour le préchauffage et/ou l'évaporation au moins partielle du fluide de travail condensé. Une alimentation optimisée des étages de surchauffeur et des surfaces d'échange thermique permet d'augmenter le rendement de 9 à 13 % à au moins 16 à 20 %.
PCT/EP2007/000918 2006-12-06 2007-02-02 Procédé et dispositif d'augmentation de la puissance et du rendement d'un processus de centrale orc WO2008067855A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002289T DE112007002289A5 (de) 2006-12-06 2007-02-02 Verfahren und Vorrichtung zur Erhöhung von Leistung und Wirkungsgrad eines ORC-Kraftwerkprozesses

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057448.6 2006-12-06
DE102006057448A DE102006057448A1 (de) 2006-12-06 2006-12-06 Verfahren zur Erhöhung von Leistung und Wirkungsgrad im ORC-Kraftwerksprozess

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WO2008067855A2 true WO2008067855A2 (fr) 2008-06-12
WO2008067855A3 WO2008067855A3 (fr) 2008-12-18

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CN105115330A (zh) * 2015-08-31 2015-12-02 天津大学 利用工业余热驱动orc系统的相变蒸发器
CN105927300A (zh) * 2016-05-09 2016-09-07 辽宁工程技术大学 一种自调节预热温度的有机朗肯循环发电系统及发电方法
US20180209305A1 (en) * 2009-07-01 2018-07-26 Mark W. Miles Integrated System for Using Thermal Energy Conversion

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BE1018869A3 (nl) * 2009-08-26 2011-10-04 Schutter Rotterdam B V Productieproces met conversie van afvalwarmte uit meervoudige afvalwartebronnen.
BE1018868A3 (nl) * 2009-08-26 2011-10-04 Schutter Rotterdam B V Inrichting voor de conversie van afvalwarmte van een productieproces naar elektrische energie.
EP2455658B1 (fr) * 2010-11-17 2016-03-02 Orcan Energy AG Procédé et dispositif d'évaporation de fluides de travail organiques
CN102121405A (zh) * 2011-02-28 2011-07-13 无锡三达环保科技有限公司 轧钢板车间加热炉低品位烟气有机郎肯循环余热发电系统
CN102168590A (zh) * 2011-03-15 2011-08-31 中国电力工程顾问集团西南电力设计院 一种利用烟气余热有机碳氢混合物汽轮机发电系统
CN103161527B (zh) * 2013-01-29 2015-02-04 南京瑞柯徕姆环保科技有限公司 蒸汽朗肯-有机朗肯联合循环发电装置
EP2801758A1 (fr) * 2013-05-06 2014-11-12 Siemens Aktiengesellschaft Générateur de vapeur à récupération de chaleur comprenant des surfaces de chauffe pouvant être en partie désactivées
DE102013114265B4 (de) * 2013-12-18 2015-07-09 GMK Gesellschaft für Motoren und Kraftanlagen mbH ORC-Anlage mit Rezirkulationskreislauf und Verfahren zum Betreiben einer derartigen ORC-Anlage
CN103790732B (zh) * 2014-02-19 2015-07-08 山东青能动力股份有限公司 中高温烟气余热双工质联合循环发电装置
CN106855249A (zh) * 2017-03-10 2017-06-16 孙立宇 一种防止烟气露点腐蚀的余热回收系统

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DE10008125A1 (de) * 1999-02-22 2001-08-23 Frank Eckert Vorrichtung zur Energieumwandlung mittels eines kombinierten Gasturbinen-Dampfkreisprozesses
FR2877074A1 (fr) * 2004-10-27 2006-04-28 Egci Pillard Sa Dispositif de combustion pour ensemble comprenant une turbine a gaz et une chaudiere a recuperation

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US20180209305A1 (en) * 2009-07-01 2018-07-26 Mark W. Miles Integrated System for Using Thermal Energy Conversion
CN105115330A (zh) * 2015-08-31 2015-12-02 天津大学 利用工业余热驱动orc系统的相变蒸发器
CN105927300A (zh) * 2016-05-09 2016-09-07 辽宁工程技术大学 一种自调节预热温度的有机朗肯循环发电系统及发电方法

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