EP4062037A1 - Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur - Google Patents

Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur

Info

Publication number
EP4062037A1
EP4062037A1 EP20807787.5A EP20807787A EP4062037A1 EP 4062037 A1 EP4062037 A1 EP 4062037A1 EP 20807787 A EP20807787 A EP 20807787A EP 4062037 A1 EP4062037 A1 EP 4062037A1
Authority
EP
European Patent Office
Prior art keywords
pressure
exhaust gas
heat exchanger
steam
low
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Withdrawn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
EP20807787.5A
Other languages
German (de)
English (en)
Inventor
Alexander Deierling
Wei Jin
Jürgen KLEBES
Sven SALDEN
Bernd SCHÄTZLER
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.)
Mitsubishi Power Europe GmbH
Cnud Efco Operations Sa
Original Assignee
Mitsubishi Power Europe GmbH
Cnud Efco Operations Sa
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 Mitsubishi Power Europe GmbH, Cnud Efco Operations Sa filed Critical Mitsubishi Power Europe GmbH
Publication of EP4062037A1 publication Critical patent/EP4062037A1/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Withdrawn legal-status Critical Current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
    • 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
    • F01K23/103—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 afterburner in exhaust boiler
    • 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
    • F01K7/16—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 only of turbine type
    • F01K7/18—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 only of turbine type the turbine being of multiple-inlet-pressure type

Definitions

  • Waste heat recovery system for the use of thermal energy recovered from exhaust gas flows to generate electricity by means of steam
  • the invention is directed to a waste heat recovery system for using thermal energy recovered from exhaust gas flows to generate electricity by means of water vapor in a steam power plant.
  • WO 2012/048706 A2 discloses the use of waste heat from a flat glass furnace to generate steam and electricity in a steam power plant, with at least parts of the exhaust gas flow being fed to a superheater connected to the water-steam circuit of the steam power plant.
  • Waste heat recovery systems based on a single-pressure water-steam cycle with a net efficiency of approx. 16 - 18% and an organic Rankine cycle (ORC) with a net efficiency of approx. 12 - 20% known, whereby the organic Rankine cycle (ORC) comprises heat transfer via a separate thermal oil heat recovery system and power generation via the ORC cycle.
  • ORC organic Rankine cycle
  • the invention is therefore based on the object of creating a solution with which the net efficiency of a waste heat recovery system can be improved when using thermal energy recovered from exhaust gas flows to generate electricity by means of water vapor in a steam power plant.
  • the waste heat recovery system according to the invention for the use of thermal energy recovered from exhaust gas flows to generate electricity by means of water vapor in a steam power plant is characterized in that the waste heat recovery system comprises at least two steam-generating heat exchangers through which one of two separate exhaust gas flows flows, which on the steam side are converted into a common water-steam Circuit of the steam power plant, which has a steam turbine set with a connected generator for generating electricity, are integrated, from which one, in particular second, of the two exhaust gas streams flows through at least one heat exchanger, which is designed as a high pressure heat exchanger, in particular high pressure superheater, or as medium pressure heat exchanger, in particular medium pressure superheater, or as low pressure heat exchanger, in particular low pressure superheater, and from the other, in particular first, of the two exhaust gas flows at least a heat exchanger is flowed through, which is designed as a high-pressure heat exchanger, in particular a high-pressure evaporator, and on the steam side is in line connection with the high-pressure
  • the advantage results from the fact that two separate exhaust gas flows are used. These preferably have different energy levels, in particular different temperatures.
  • Medium pressure heat exchangers in particular medium pressure preheaters, or as Low-pressure heat exchanger, in particular low-pressure preheater, is formed and the other, in particular first, of the two exhaust gas flows flows through at least one further heat exchanger, which is used as a high-pressure heat exchanger, in particular high-pressure preheater, or as a medium-pressure heat exchanger, in particular
  • Low pressure preheater is formed, which the invention provides in an embodiment.
  • each of the two exhaust gas flows to flow through a plurality of heat exchangers from the group of preheaters and / or evaporators and / or superheaters, which are connected in series with respect to the exhaust gas flow direction and which are in the feed water line and / or on the steam side are involved in the water-vapor cycle.
  • a particularly advantageous embodiment of the waste heat recovery system according to the invention is characterized in that the waste heat recovery system comprises at least four steam-generating heat exchangers, each of which has one of two exhaust gas streams flowing through it, which are integrated on the steam side into a common water-steam circuit of the steam power plant, which has a steam turbine set with at least one low-pressure and a high-pressure turbine and a connected generator for generating electricity, two of these four heat exchangers are designed as high-pressure heat exchangers and two as low-pressure heat exchangers, and one high-pressure heat exchanger and one low-pressure heat exchanger are each traversed by one of the two exhaust gas streams, the two of which are each of the same Exhaust gas flow through the heat exchangers of the high pressure heat exchanger in relation to the flow direction of this respective exhaust gas flow upstream of the low pressure heat exchanger is ordered, and the two high-pressure heat exchangers and the two low-pressure heat exchangers are each connected in series on the steam side and the high-pressure heat exchanger of the two high
  • one of the two exhaust gas flows is a first exhaust gas flow and if the high-pressure heat exchanger through which this first exhaust gas flow flows is a high-pressure evaporator integrated into a high-pressure part of the feed water line of the water-steam circuit and the first exhaust gas flow from this flowed through low-pressure heat exchanger is a low-pressure evaporator integrated into a low-pressure part of the feedwater line of the water-steam cycle.
  • This offers the possibility of overheating the steam formed in this pair of heat exchangers in the second pair of heat exchangers through which the other exhaust gas flow flows and thereby achieving a particularly effective increase in the net efficiency of the waste heat recovery system.
  • the invention therefore provides that one of the two exhaust gas flows is a second exhaust gas flow and that the high pressure heat exchanger through which this second exhaust gas flow flows is a high pressure superheater and the low pressure heat exchanger through which this second exhaust gas flow flows is a low pressure superheater.
  • the invention further provides that one or both of the two exhaust gas streams each have an upstream of the respective at least one heat exchanger, in particular the respective high pressure heat exchanger, with respect to the flow direction of this respective exhaust gas stream
  • Gas burner or gas booster is assigned, which is in line connection with the respective exhaust gas flow and which generates a hot exhaust gas that can be added to the respective exhaust gas flow to increase its temperature via this line connection upstream of the respective at least one heat exchanger, in particular the respective high-pressure heat exchanger.
  • the exhaust gas flows used are expediently those from one or more industrial plants, so that the invention further provides that the two exhaust gas flows are parts of a split exhaust gas flow or two separately extracted exhaust gas flows from one or more industrial plants.
  • the other, in particular the first, exhaust gas flow can have a temperature of 350 ° C - 850 ° C preferably from 420 ° C to 550 ° C
  • the one, in particular second, exhaust gas stream can have a temperature of 350 ° C to 850 ° C, preferably after admixing exhaust gas from the gas burner or gas booster, a temperature of 550 ° C to 1100 ° C, in particular a temperature between 600 ° C and 900 ° C, whereby the invention is also characterized in a further embodiment.
  • the at least one heat exchanger through which the one, in particular the second, exhaust gas flow flows is a high-pressure heat exchanger or the heat exchangers through which the one, in particular the second, exhaust gas flow comprises a high-pressure heat exchanger , which generates water vapor at a pressure of 70-100 bar and a temperature of 510 ° C - 540 ° C and feeds it into the water-steam cycle, and if the at least one heat exchanger through which the one, in particular the second exhaust gas stream flows, is a low-pressure heat exchanger or one of the heat exchangers through which the one, in particular the second, exhaust gas stream flows
  • the two respective pairs each consisting of a high-pressure heat exchanger and a low-pressure heat exchanger in combination with other heat exchangers integrated into the water-steam cycle, can advantageously be combined in separate system units.
  • the invention further provides that the low-pressure evaporator is part of a system unit through which the other, in particular the first, exhaust gas flow flows and which, in relation to the flow direction of this other, in particular the first, exhaust gas flow upstream of the low-pressure evaporator, enters the high-pressure part of the feedwater line of the Water-steam circuit integrated first high-pressure preheater and downstream of the low-pressure evaporator comprises a low-pressure evaporator integrated into the low-pressure part of the feedwater line of the water-steam circuit.
  • the low-pressure superheater and the high-pressure superheater are components of a further system unit through which the one, in particular the second, exhaust gas flow flows and which, with regard to the flow direction of this, one, in particular the second, exhaust gas flow downstream of the low-pressure superheater one in the Comprises high pressure part of the feed water line of the water-steam circuit integrated second high-pressure preheater.
  • the invention further proposes that the waste heat recovery system together with at least one further, with regard to the arrangement and integration of its heat exchanger in the water-steam Circuit, preferably identical to the waste heat recovery system, another waste heat recovery system, which is integrated into the water-steam cycle in parallel to the waste heat recovery system and in which at least one heat exchanger, preferably one high-pressure heat exchanger and one low-pressure heat exchanger, is flowed through by one of two further exhaust gas streams is interconnected with a heat recovery system for generating electricity by means of steam.
  • the waste heat recovery system together with at least one further, with regard to the arrangement and integration of its heat exchanger in the water-steam Circuit, preferably identical to the waste heat recovery system, another waste heat recovery system, which is integrated into the water-steam cycle in parallel to the waste heat recovery system and in which at least one heat exchanger, preferably one high-pressure heat exchanger and one low-pressure heat exchanger, is flowed through by one of two further exhaust gas streams is interconnected with a heat recovery system for generating electricity by
  • the waste heat recovery system or the heat recovery system formed from it or with it is expediently designed in such a way that it or the heat recovery system formed therewith generates an electrical output of 2-70 MW ei by means of a generator connected to the steam turbine set or several generators connected to the steam turbine set.
  • Waste heat recovery systems arise in particular when the exhaust gas flows and / or the further exhaust gas flows are those of one or more sinter cooling systems or one or more furnace systems or one or more glass furnaces, in particular one or more float glass or container glass systems, which ultimately also makes the invention excels.
  • FIG. 1 The invention is explained in more detail below with reference to the single FIGURE, FIG. 1.
  • Each waste heat recovery system 9.1 and 9.2 has seven heat exchangers 1 - 7, each designed as high-pressure or low-pressure heat exchangers, namely a high-pressure evaporator (HP EVA 1) 1, a first high-pressure preheater (HP ECO 1) 2, a low-pressure evaporator (LP EVA 1).
  • HP EVA 1 high-pressure evaporator
  • HP ECO 1 first high-pressure preheater
  • LP EVA 1 low-pressure evaporator
  • a low pressure preheater (LP ECO 1) 4 a high pressure superheater (HP SH 1) 5, a low pressure superheater (LP SH 1) 6 and a second High pressure preheater (HP ECO 2) 7.
  • the first high pressure preheater (HP ECO 1) 2 is combined with the low pressure evaporator (LP EVA 1) 3 and the low pressure preheater (LP ECO 1) 4 each in a system unit 18.
  • the high-pressure superheater (HP SH 1) 5, the low-pressure superheater (LP SH 1) 6 and the second high-pressure preheater (HP ECO 2) 7 are each combined in a further system unit 19.
  • the heat exchanger high pressure evaporator (HP EVA 1) 1, first high pressure preheater (HP ECO 1) 2, low pressure evaporator (LP EVA 1) 3 and low pressure preheater (LP ECO 1) 4 of the waste heat recovery system 9.1 are in relation to a first exhaust gas stream 10a flowing through these heat exchangers 1 - 4 Connected in series.
  • This first exhaust gas flow 10a flows through these heat exchangers 1 - 4 in the order high pressure evaporator (HP EVA 1) 1, first high pressure preheater (HP ECO 1) 2, low pressure evaporator (LP EVA 1) 3 and low pressure preheater (LP ECO 1) 4.
  • the first exhaust gas stream 10a is discharged via a chimney.
  • Waste heat recovery system 9.2 flows through a second exhaust gas stream 11a.
  • the heat exchanger high pressure superheater (HP SH 1) 5, low pressure superheater (LP SH 1) 6 and second high pressure preheater (HP ECO 2) 7 of the waste heat recovery system 9.1 are connected in series with respect to a second exhaust gas flow 10b flowing through these heat exchangers 5-7.
  • This second exhaust gas flow 10b flows through these heat exchangers 5 - 7 in the order high pressure superheater (HP SH 1) 5, low pressure superheater (LP SH 1) 6 and second high pressure preheater (HP ECO 2) 7.
  • the second exhaust gas flow is also 10b discharged through a chimney.
  • Waste heat recovery system 9.2 flows through a second exhaust gas stream 11b.
  • the respective second exhaust gas flow 10b, 11b is in line connection upstream of the respective heat exchanger high pressure superheater (HP SH 1) 5 with a gas burner or gas booster 8, viewed in the exhaust gas flow direction, in which a fuel is burned and its hot exhaust gas is at least partially mixed with the respective first exhaust gas stream 10a, 11a.
  • HP SH 1 heat exchanger high pressure superheater
  • the heat exchangers low-pressure preheater (LP ECO 1) 4, low-pressure evaporator (LP EVA 1) 3 and low-pressure superheater (LP SH 1) 6 of the waste heat recovery system 9.1 and the other waste heat recovery system 9.2 are connected in series with respect to the water-steam circuit 15 and with the low-pressure part 17b the feed water line 17 of the water-steam circuit 15 connected.
  • the feed water is preheated in the low-pressure preheater (LP ECO 1) 4, then evaporated in the low-pressure evaporator (LP EVA 1) 3 and finally superheated in the low-pressure superheater (LP SH 1) 6.
  • the superheated steam emerging from the low-pressure superheater (LP SH 1) 6 is directed to a low-pressure turbine 14b of the steam turbine set 14 arranged in the water-steam circuit 15.
  • the waste heat recovery system 9.1 and the further waste heat recovery system 9.1 itself are connected in parallel with respect to the water-steam circuit 15.
  • the heat exchangers first high-pressure preheater (HP ECO 1) 2 and second high-pressure preheater (HP ECO 2) 7 of the waste heat recovery system 9.1 and the further waste heat recovery system 9.2 are initially connected in parallel with the high-pressure part 17a of the feedwater line 17 of the water-steam circuit with regard to the water-steam circuit 15. Circuit 15 connected and then connected in series with the high pressure evaporator (HP EVA 1) 1 and the high pressure superheater (HP SH 1) 5 connected.
  • the feed water is in the first high pressure preheater (HP ECO 1) 2 of the waste heat recovery system 9.1 by means of the first exhaust gas flow 10a or in the first high pressure preheater (HP ECO 1) 2 of the further waste heat recovery system 9.2 by means of the first exhaust gas flow 11a and in the second high pressure preheater (HP ECO 2) 7 the waste heat recovery system 9.1 preheated by means of the second exhaust gas flow 10b or in the second high-pressure preheater (HP ECO 2) 7 of the further waste heat recovery system 9.2 by means of the second exhaust gas flow 11 b.
  • the feed water heated in this way is then evaporated in the respective high pressure evaporator (HP EVA 1) 1 and finally superheated in the respective high pressure superheater (HP SH 1) 5.
  • the superheated steam emerging from the high-pressure superheater (HP SH 1) 5 is directed to a high-pressure turbine 14 a of the steam turbine set 14 arranged in the water-steam circuit 15.
  • the waste heat recovery system 9.1 and the further waste heat recovery system 9.2 itself are connected in parallel with respect to the water-steam circuit 15.
  • the waste heat recovery system 9.1 and the further waste heat recovery system 9.2 are therefore connected in parallel with respect to the water-steam circuit 15, i.e. they are located in the same water-steam circuit 15, but use the waste heat from different exhaust gas flows.
  • the waste heat recovery system 9.1 uses the waste heat from the exhaust gas flows 10a, 10b and the further waste heat recovery system 9.2 uses the waste heat from the exhaust gas flows 11a, 11b.
  • Waste heat recovery system 9.1 flow through, it concerns parts of a split exhaust gas flow or two separately withdrawn exhaust gas flows of one or more Industrial plants.
  • the first and second exhaust gas streams 11a, 11b which flow through the further exhaust gas recovery system 9.2, are parts of a split exhaust gas stream or two separately withdrawn exhaust gas streams from one or more industrial systems, this industrial system or industrial systems preferably being / are different from the one whose Exhaust gas flow or exhaust gas flows 10a, 10b flows through / flow through the waste heat recovery system 9.1.
  • the water-steam circuit 15 comprises, downstream of the steam turbine set 14, a condenser 13 and a feed water tank 12, the degassing device of which is connected to a steam line of the steam turbine set 14.
  • the feed water line 17 branches off from the feed water tank 12.
  • the first exhaust gas flow 10a of the waste heat recovery system 9.1 and the first exhaust gas flow 11a of the further waste heat recovery system 9.2 each have a temperature of 350.degree. C.-850.degree. C., preferably 420.degree. C.-550.degree.
  • the second exhaust gas flow 10b of the waste heat recovery system 9.1 and the second exhaust gas flow 11b of the further waste heat recovery system 9.2 each have a temperature of 350 ° C - 850 ° C, preferably after admixing exhaust gas from the gas burner or gas booster 8 a temperature of 550 ° C - 1100 ° C, in particular a temperature between 600 ° C and 900 ° C.
  • the respective first exhaust gas flow 10a, 11a in each case forms a larger volume flow than the respective second exhaust gas flow 10b, 11b.
  • this is only an exemplary design.
  • the waste heat recovery system 9.1 or the heat recovery system 9 formed from the two waste heat recovery systems 9.1 and 9.2 is designed in such a way that an electrical output of 2-70 MW ei can be generated by means of the at least one steam turbine set 14 and the at least one generator 16 arranged on it.
  • the exhaust gas flows 10a, 10b and / or the further exhaust gas flows 11a, 11b preferably originate from exhaust gas flows of one or more sinter cooling systems or one or more furnace systems or one or more glass furnaces, in particular one or more float glass or container glass systems.
  • the respective first exhaust gas stream 10a, 11a is passed from an industrial system or an industrial process to a respective high-pressure evaporator (HP EVA 1) 1, which feeds the existing exhaust gas treatment systems, here as De-NO x - E-filter specified, is connected upstream.
  • HP EVA 1 high-pressure evaporator
  • the respective first exhaust gas stream 10a, 11a is passed into a respective high pressure economizer / high pressure evaporator (HP ECO 1) 2 and then into a respective low pressure evaporator (LP EVA 1) 3.
  • the respective heat exchangers 1 - 4 i.e. the respective low-pressure economizer / low-pressure evaporator (LP ECO 1) 4 as well as the respective first high-pressure economizer / high-pressure evaporator (HP ECO 1) 2, the respective low-pressure evaporator (LP EVA 1) 3 and the respective high-pressure evaporator (HP EVA 1) 1 are used to preheat or evaporate the feed water.
  • the feed water is pumped from the hot water tank of the condenser 13 into the feed water tank 12 for ventilation.
  • the degassing is preferably implemented by preheated feed water coming from one or both of the respective low-pressure economizer (s) / low-pressure evaporator (s) (LP ECO 1) 4 so as not to use any steam from the steam extraction of the steam turbine set 14.
  • This feed water extraction is marked in FIG. 1 with "SP”. Steam is withdrawn from the steam turbine set 14 only to start up the process or the heat recovery system 9.
  • the degassed feed water is transferred via low pressure feed water pumps in the low pressure part 17b of the feed water line 17 to the respective low pressure economizer / low pressure evaporator (LP ECO 1) 4 and Pumped via the high pressure feed water pumps in the high pressure part 17a of the feed water line 17 to the respective first high pressure economizer / high pressure evaporator (HP ECO 1) 2 and to the respective second high pressure economizer / high pressure evaporator (HP ECO 2) 7.
  • the preheated feed water is then passed to the respective low-pressure evaporator (LP EVA 1) 3 and to the respective high-pressure evaporator (HP EVA 1) 1, where it is evaporated in each case.
  • the saturated low-pressure and high-pressure steam is then transferred to the respective high-pressure superheater (HP SH 1) 5 or to the respective Low-pressure superheater (LP SH 1) 6 passed, where it is superheated in each case.
  • the superheated low-pressure steam and the superheated high-pressure steam are each fed to the corresponding turbine stages 14a, 14b of the steam turbine set 14 for generating electricity by means of the connected generator 16.
  • the steam is expanded in the steam turbine set 14, condensed in the condenser 13 and finally collected in the hot water space of the condenser 13. It is then pumped to the feed water tank 12 and the water-steam cycle begins again.
  • the waste heat of the respective first exhaust gas stream 10a, 11a is only used for preheating and evaporation of the feed water.
  • the overheating in the respective high-pressure superheater (HP SH 1) 5 or the respective low-pressure superheater (LP SH 1) 6 is implemented by using the respective second exhaust gas flow 10b, 11b and / or, if necessary, by additional firing by means of the gas booster 8.
  • the main components of the heat recovery system 9 are one or more multi-pressure waste heat recovery systems 9.1, 9.2 with one or more associated internal or external gas booster (s) 8, a multi-stage steam turbine or a multi-stage steam turbine set 14 and a condenser 13, which is used as a wet cooling tower or as air-cooled condenser can be performed with or without additional water cooling.
  • the steam turbine set 14 is designed as a condensation or counter-pressure steam turbine or steam turbine set.
  • the system usually comprises several Balance-of-Plant (BoP) systems such as steam piping systems, condensate systems, feed water systems or closed cooling water systems, etc., which are not shown in detail.
  • BoP Balance-of-Plant
  • waste heat recovery systems 9.1, 9.2 can be used, with the high pressure (HP) and medium pressure (MP) as well as low pressure (LP) steam lines of the individual waste heat recovery systems 9.1, 9.2 being merged and converted into corresponding HP, MP and LP stages of the steam turbine set 14 are performed, a medium pressure (MP) stage not being shown in the exemplary embodiment.
  • HP high pressure
  • MP medium pressure
  • LP low pressure
  • the respective waste heat recovery systems are 9.1 or the respective waste heat recovery systems are 9.1, 9.2 or the respective
  • Heat recovery system 9 in one or - if several exhaust gas sources can be used - embedded in several flue gas lines and thus exhaust gas flows of an industrial process or several industrial processes. If there are flue gas cleaning systems in the ducts, the respective heat recovery system 9 can be installed in front of and behind the flue gas cleaning systems to be ordered.
  • the construction of the respective waste heat recovery systems 9.1, 9.2 is unique and specially designed for the application described, since its main components can be functionally divided into several system units 18, 19.
  • 1 for an industrial application with existing flue gas cleaning systems comprises, for example, a system unit in each of the two waste heat recovery systems 9.1, 9.2, which consists of the high-pressure evaporator (HP EVA 1) 1, the system unit 18, which consists of the first high pressure preheater (HP ECO 1) 2, the low pressure evaporator (LP EVA 1) 3 and the low pressure preheater (LP ECO 1) 4, and the system unit 19, which consists of the high pressure superheater (HP SH 1) 5, the low pressure superheater (LP SH 1) 6 and the second high-pressure preheater (HP ECO 2) 7 and, if applicable, the internal or external gas booster 8.
  • Plant units and the respective heat recovery system 9 with its plant unit and plant components can be adapted to the respective industrial environment or its exhaust gas parameters. This means that in each case different system units or system components to a respective waste heat recovery system 9.1, 9.2 or a respective
  • Heat recovery system 9 can be combined or that heat exchangers such as HP / LP ECO or HP / LP EVA or the gas charging can be moved between the various system units and system components in order to ensure the highest possible efficiency.
  • overheating can be implemented in the following ways: Using the waste heat in the exhaust gas flow;
  • Additional firing via a gas booster that can be fired with natural gas, biogas, furnace gas or hydrogen;

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

Dans une installation de récupération de chaleur perdue (9.1) pour utiliser l'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur dans une centrale électrique à vapeur, l'objet de l'invention est de créer une solution par laquelle l'efficacité nette d'une installation de récupération de chaleur perdue peut être améliorée lorsque l'énergie thermique récupérée à partir de flux de gaz d'échappement est utilisée pour la production d'énergie au moyen de vapeur dans une centrale électrique à vapeur. Selon l'invention, cet objectif est atteint en ce que l'installation de récupération de chaleur perdue (9.1) comprend au moins deux échangeurs de chaleur générant de la vapeur (1, 5 ; 3, 6) à travers chacun desquels deux flux de gaz d'échappement (10a, 10b) s'écoulent, séparés les uns des autres, lesdits échangeurs de chaleur étant intégrés côté vapeur dans un circuit d'eau-vapeur commun (15) de la centrale électrique à vapeur. Un des deux flux de gaz d'échappement (10b) s'écoule à travers au moins un échangeur de chaleur réalisé sous la forme d'un échangeur de chaleur haute pression (5) ou d'un échangeur de chaleur moyenne pression ou d'un échangeur de chaleur basse pression (6) et l'autre des deux flux de gaz d'échappement (10a) s'écoule à travers au moins un échangeur de chaleur réalisé sous la forme d'un échangeur de chaleur haute pression (1) et qui, côté vapeur, est relié par une conduite à l'échangeur de chaleur haute pression (5) à travers lequel un flux de gaz d'échappement (10b) s'écoule ou l'échangeur de chaleur est réalisé sous la forme d'un échangeur de chaleur moyenne pression et qui, côté vapeur, est relié par une conduite à l'échangeur de chaleur moyenne pression à travers lequel s'écoule un flux de gaz d'échappement (10b) ou l'échangeur de chaleur est réalisé sous la forme d'un échangeur de chaleur basse pression (3) et qui, côté vapeur, est relié par une conduite à l'échangeur de chaleur basse pression (6) à travers lequel s'écoule un flux de gaz d'échappement (10b).
EP20807787.5A 2019-11-22 2020-11-20 Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur Withdrawn EP4062037A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19211031 2019-11-22
PCT/EP2020/082951 WO2021099597A1 (fr) 2019-11-22 2020-11-20 Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur

Publications (1)

Publication Number Publication Date
EP4062037A1 true EP4062037A1 (fr) 2022-09-28

Family

ID=68887199

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20807787.5A Withdrawn EP4062037A1 (fr) 2019-11-22 2020-11-20 Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur

Country Status (2)

Country Link
EP (1) EP4062037A1 (fr)
WO (1) WO2021099597A1 (fr)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879616A (en) * 1973-09-17 1975-04-22 Gen Electric Combined steam turbine and gas turbine power plant control system
US4099374A (en) * 1976-04-15 1978-07-11 Westinghouse Electric Corp. Gasifier-combined cycle plant
JP3913328B2 (ja) * 1997-08-26 2007-05-09 株式会社東芝 コンバインドサイクル発電プラントの運転方法およびコンバインドサイクル発電プラント
US7107774B2 (en) * 2003-08-12 2006-09-19 Washington Group International, Inc. Method and apparatus for combined cycle power plant operation
US20100180567A1 (en) * 2009-01-16 2010-07-22 General Electric Company Combined Power Augmentation System and Method
DE102011053909A1 (de) 2010-09-26 2012-03-29 Get Glass Engineering Gmbh Verfahren und Einrichtung zur Einspeisung von Prozessabgasen und zur Regelung der Abgasvolumenmenge zur Verbesserung der Ofendruckstabilisierung bei Glasschmelz- und Leuterprozessen in Querflammenwannen mit Regenerativheizungen
EP3133255B1 (fr) * 2015-08-20 2023-04-26 General Electric Technology GmbH Centrale electrique a cycle combine

Also Published As

Publication number Publication date
WO2021099597A1 (fr) 2021-05-27

Similar Documents

Publication Publication Date Title
EP2347102B1 (fr) Procédé de fonctionnement d'un circuit thermodynamique et circuit thermodynamique
DE19513285B4 (de) Turbinen-Antrieb für Kesselspeisepumpe / Speisewasser-Leitungssystem
EP0591163B1 (fr) Installation combinee a turbines a gaz et a vapeur
AT517535B1 (de) Dampfkraftwerk
EP2409003A2 (fr) Dispositif et procédé de production de vapeur avec un rendement élevé
CH702163A2 (de) Verfahren zur Steigerung der Leistungsabgabe eines Gas- und Dampf-Kombikraftwerks während ausgewählter Betriebszeiträume.
DE102018123663A1 (de) Brennstoffvorwärmsystem für eine Verbrennungsgasturbine
DE102009013570A1 (de) Kraftwerksanlage mit zwei Kreisläufen sowie ein Verfahren zum Betrieb einer Kraftwerksanlage
EP1425079B1 (fr) Procede et dispositif de degazage thermique de la substance active d'un processus a deux phases
CH645433A5 (de) Kombinierte gasturbinen-dampfkraftanlage.
WO2007144285A2 (fr) Centrale à vapeur
EP0158629B1 (fr) Cycle à vapeur pour installation énergétique à vapeur
WO2021099597A1 (fr) Installation de récupération de chaleur perdue pour l'utilisation d'énergie thermique récupérée à partir de flux de gaz d'échappement pour la production d'énergie au moyen de vapeur
EP2305964A1 (fr) Centrale à vapeur
EP3728800B1 (fr) Centrale électrique
EP3810907B1 (fr) Recirculation des gaz d'échappement dans des installations de turbines à gaz et à vapeur
DE10052414A1 (de) Verfahren zum Betreiben einer Energieumwandlungseinrichtung sowie Vorrichtung zur Durchführung eines solchen Verfahrens
EP2559867A1 (fr) Procédé de production d'énergie électrique à l'aide d'une centrale électrique combinée et centrale électrique combinée destinée à l'exécution du procédé
DE2648576C2 (de) Gas-Dampfturbinenanlage
DE1050609B (de) Eine Gasturbinen und eine Dampfturbmenanlage umfassende Warmekraftanlage
DE102008057490B4 (de) Kombiniertes Gas- und Dampfturbinenkraftwerk und Verfahren zum Betrieb
WO2009000846A2 (fr) Procédé et dispositif pour faire fonctionner un générateur de vapeur
DE102015118098A1 (de) Verfahren zur Speisewasservorwärmung eines Dampferzeugers eines Kraftwerks
DE102013219166A1 (de) Ansaugluftvorwärmsystem
DE102021203730A1 (de) Erzeugung von elektrischer Energie aus Wasserstoff und Sauerstoff

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20220523

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20230110