EP3971396A1 - Dampferzeuger mit einspritzkühlern - Google Patents

Dampferzeuger mit einspritzkühlern Download PDF

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Publication number
EP3971396A1
EP3971396A1 EP20196335.2A EP20196335A EP3971396A1 EP 3971396 A1 EP3971396 A1 EP 3971396A1 EP 20196335 A EP20196335 A EP 20196335A EP 3971396 A1 EP3971396 A1 EP 3971396A1
Authority
EP
European Patent Office
Prior art keywords
fluid
temperature
vapor
superheater
steam
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Withdrawn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
EP20196335.2A
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English (en)
French (fr)
Inventor
Peter Simon Rop
Antonius Goossen
Peter Witte
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.)
Siemens Energy Global GmbH and Co KG
Original Assignee
Siemens Energy Global GmbH and Co KG
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 Siemens Energy Global GmbH and Co KG filed Critical Siemens Energy Global GmbH and Co KG
Priority to EP20196335.2A priority Critical patent/EP3971396A1/de
Priority to KR1020237012731A priority patent/KR20230069191A/ko
Priority to JP2023540985A priority patent/JP2023541492A/ja
Priority to US18/245,426 priority patent/US20230358396A1/en
Priority to PCT/EP2021/072139 priority patent/WO2022058091A1/en
Priority to EP21762395.8A priority patent/EP4214405A1/de
Publication of EP3971396A1 publication Critical patent/EP3971396A1/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • 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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
    • F22G5/123—Water injection apparatus

Definitions

  • the invention relates to a steam generator and a steam generation system.
  • the invention is about the protection of the steam generator and a further steam turbine against rapidly increase of steam temperature and the efficient heat transfer from a hot gas to an evaporation medium.
  • a power plant often combines a gas turbine with a steam turbine to create electrical energy with the best efficiency.
  • a steam generator is used to convert the hot gas from the gas turbine into hot steam for the steam turbine.
  • the common steam generator comprises first a hot gas path from a hot gas input to a waste gas output. Inside the hot gas path several heat exchangers are arranged, starting form an economizer at the waste gas output side over a series of further heat exchangers up to a superheater at the hot gas output side. The temperature of the fluid flowing through the heat exchangers increases from one heat exchanger to the next, whereby the economizer is feed with cold water and a hot steam is leaving the superheater.
  • Gas turbines enables a quick response to the request for electrical energy with the result of a rapidly increase of the temperature of the hot gas leaving the gas turbine. Without protection methods the quick temperature change bears the risk of too high thermal stress especially at the steam turbine.
  • a common solution is to arrange attemperators within the connection piping from the steam generator to the steam turbine.
  • the attemperator is used to inject water into the hot steam after the superheater.
  • a further disadvantage of common systems is the problem, that the control of the attemperator is very sensitive. To prevent overshoot due to the sensitive control of the steam temperature by opening/closing a valve in the cold-water line to the attemperator it is commonly necessary to keep a further distance between the actual temperature / temperature change during the operation, especially at startup of the turbine and the admissible temperature / temperature change.
  • the task for the current invention is therefore to enable a good and fast adjustability of the hot steam temperature and further protect the piping of the superheater at the output side and further the piping to the steam turbine against rapid temperature changes.
  • a generic kind of a steam generator has a casing with a hot gas path inside passing through the casing from a hot gas input to a waste gas output.
  • the steam generator comprises serval heat exchangers, which are arranged at least partially inside the hot gas path.
  • a superheater as one of the heat exchangers is arranged close to the hot gas input.
  • the superheater comprises a superheater output as connection to further facilities, e.g. a steam turbine, to deliver a flow of hot steam.
  • the superheater further comprises a superheater input.
  • a first heat exchanger is arranged. This comprises analog a first output and a first input.
  • the first output is in connection with the superheater input.
  • a second heat exchanger is arranged within the hot gas path. This comprises analog a second output and a second input. Here the second output is in connection with the first input.
  • a third heat exchanger is arranged within the hot gas path. This comprises analog a third output and a third input.
  • the third output is in connection with the second input.
  • a fourth heat exchanger is arranged within the hot gas path. This comprises analog a fourth output and a fourth input.
  • the fourth output is in connection with the third input.
  • a fifth heat exchanger in the series next to the fourth heat exchanger or even further heat exchangers in the series each comprising a fluid input and a fluid output, which are connected in the series of heat exchangers.
  • an economizer is arranged. This comprises analog an economizer output and an economizer input.
  • the economizer output is in connection with the fluid input of the last heat exchanger.
  • the economizer input is in connection with a source of cold fluid.
  • water is used as fluid, but other fluids which could be evaporated could also be used.
  • the superheater and the heat exchangers and the economizer are arranged immediate and/or in the respective sequence to each other inside the hot gas path.
  • other features or other heat exchanges which are not connected along the series of heat exchanges according the generic solution, could be arranged within the hot gas path and also between the heat exchangers of the generic solution.
  • the superheater and the heat exchangers and the economizer are connected directly to each other. It is also possible, that further devices, e.g. other heat exchangers or vessels, are arranged in between the superheater and/or the heat exchangers and/or the economizer according the generic solution. But the preferred solution provides a direct connection from the superheater to the first heat exchanger and a direct connection from the first heat exchanger to the second heat exchanger and so on until the last heat exchanger in the series is connected to the economizer.
  • Each of the superheater and the heat exchanges and the economizer comprise a fluid input, with is connected to a further heat exchanger or another part of the steam generator.
  • fluid e.g. water and/or steam
  • the fluid input is connected to one or more distribution pipes to split the fluid flow into different pipes.
  • Each of the superheater and the heat exchanges and the economizer further comprises several heat exchange tubes, each connected to one of the respective distribution pipes.
  • the heat exchange tubes are arranged at least partially, in particular complete, inside the hot gas path. In operation the flow of hot gas along the hot gas path passing the heat exchangers leads to a transfer of heat from the hot gas to the fluid, e.g.
  • each of the heat exchange tubes is connected to a collection pipe, where each of the superheater and the heat exchanges and the economizer comprises one or more collection pipes to collect the hot fluid from the heat exchange tubes.
  • the collection pipes are in connection with a fluid output, which serves as connection to a further heat exchanger or other facilities, e.g. a steam turbine.
  • the steam generator further comprises a distribution piping to distribute a certain kind of fluid.
  • This first attemperator comprises a connection to a distribution piping, wherein in the connection to the distribution piping a first valve is arranged to control the flow from the distribution piping to the first attemperator.
  • This second attemperator comprises also a connection to a distribution piping, wherein in the connection to the distribution piping a second valve is arranged to control the flow from the distribution piping to the second attemperator.
  • This third attemperator comprises also a connection to a distribution piping, wherein in the connection to the distribution piping a third valve is arranged to control the flow from the distribution piping to the third attemperator.
  • This fourth attemperator comprises also a connection to a distribution piping, wherein in the connection to the distribution piping a fourth valve is arranged to control the flow from the distribution piping to the fourth attemperator.
  • the distribution piping is in connection with the economizer output. To enable a control of the temperature and the flow rate through the distribution piping a further connection from the distribution piping to the source of cold fluid is available.
  • Each of the attemperators comprises one or more fluid nozzles to introduce a cooling fluid, e.g. water, into the steam flowing through the attemperator, e.g. the connection from one heat exchanger to the next heat exchanger or superheater in the series.
  • the fluid nozzle itself is connected with the distribution piping as a cooling fluid supply for the attemperators.
  • the flow of the cooling fluid from the distribution piping to the fluid nozzles could be controlled by the usage of respective fluid valves.
  • the steam generation is enhanced by adding extra fluid in the evaporator section, shortening the traveling time, improving the response time, and without increasing ex-ergy loss since the attemperator fluid is added in a boiling environment and thus the fluid temperature remains constant.
  • a last valve is arranged between the input of the last heat exchanger before the economizer and the economizer output. This enables the control of the flow of the fluid into the last heat exchangers.
  • a fluid supply valve is arranged at the economizer input or at the economizer output. This enables the control of the flow of fluid through the economizer.
  • a bypass to the economizer could be used.
  • a fluid bypass valve is arranged within the connection from the distribution piping to the source of cold fluid in the advantageous solution.
  • a main attemperator is arranged in the superheater output. This attemperator is also connected to the distribution piping with a main valve arranged within this connection. This enables a precise control of the steam temperature, especially at the start of a steam turbine.
  • Attemperators within at least two collection pipes of a heat exchanger and/or preferably in the superheater. It is in particular advantageous to arrange an attemperator within each existing collection pipe of a heat exchanger respectively superheater.
  • Attemperators in the collection pipes it is possible to enable a beneficial control of the temperature of the hot fluid, e.g. steam, at the output of the heat exchanger respectively superheater with a fast response to a change of the heat input. Further the fluid output line could be protected against a rapid temperature change. As result, especially an increase of the lifetime could be expected and in the best case a limitation of start-ups of the steam generator could be omitted.
  • the hot fluid e.g. steam
  • the solution with the attemperators in the collection pipes is the best compromise between the effort to implement the cooling solution and the protection against thermal stress.
  • each of the attemperator with the distribution piping, wherein it is possible to connect all attemperators of one heat exchanger respectively superheater with one fluid valve, which controls the cooling fluid flow to all of the attemperators at the same time.
  • each of the fluid valve is used to control the flow of cooling fluid to at least one attemperator.
  • the second approach it leads to the possibility to control the temperature of the steam at the output of each of the collection pipes separately.
  • the highest temperatures inside the heat exchangers could be expected at the upstream side (with regard to the flow of the hot gas through the steam generator) at the hot gas input. Therefore, it is advantageous, if the arrangement of at least two attemperators within the collection pipes is used at the superheater, especially if it is arranged as the first heat exchanger starting at the hot gas input.
  • the inventive steam generator enables an inventive steam generating system, which comprises the inventive steam generator according to the forgoing description.
  • the steam generating system comprises a control system.
  • the control system is in connection with the fluid valve to control the opening position of each of the fluid valves.
  • valves of the number of valves could be controlled in groups at the same time dependent from each other.
  • control system is able to control the fluid valves stepwise so that the strength of the flow of fluid from the distribution piping to the respective attemperator corresponds to the needs.
  • the steam generating system further comprises a temperature determination system, wherein the temperature determination system comprises a temperature sensor. With the temperature sensor, the temperature determination system is able to determine at least the temperature of the hot steam leaving one of the heat-exchangers respectively the superheater or the temperature of the piping at the fluid output.
  • the temperature determination system should be able to determine the actual temperature of the fluid at the fluid output of the heat exchanger respectively superheater.
  • a temperature sensor inside the fluid output could be applied.
  • the preferred embodiment comprises at least one further temperature sensor. This could be additional to a first temperature sensor a second temperature sensor, which is able to measure the temperature of the steam and/or of the piping before or after a second attemperator, e.g. at the second output at the second heat-exchanger.
  • a third temperature sensor is preferable able to measure the temperature of the steam and/or of the piping before or after the third attemperator.
  • control system is then enabled to control the different fluid valves separately depending on the different temperatures at the respective attemperators.
  • a vapor determination system is necessary.
  • the vapor determination system must be possible to determine at least one share of vapor in the fluid inside the piping before and/or after one of the attemperators.
  • the share of vapor could be calculated on the other side of the attemperator (it the measuring of the share of vapor is arranged upstream it could be determined for the downstream side and vice versa).
  • control system is then enabled to control the different fluid valves separately depending on the share of vapor at the respective attemperators .
  • the steam generation system combines the first and second embodiment with a temperature determination system and a vapor determination system.
  • the steam generating system enables with the control system the control of the fluid valves dependent on the measured temperatures respective temperature changes and dependent on the analyzed share of vapor at the attemperators.
  • the new steam generation system as described before enables a new inventive method to control the steam generation system.
  • Dependent on the determination system used different implementations are possible.
  • the steam generation system comprising a temperature determination system in a first step it is necessary to determine the actual temperature at a fluid output of the heat-exchanger. As already explained, this could be the temperature of the piping itself or the temperature of the fluid inside the piping. In the first case it should be possible to estimate the temperature of the fluid and in the second case it should be possible to estimate the temperature of the piping.
  • the actual temperature has to be compared with a predetermined value.
  • At least one fluid valve is controlled dependent on the outcome of the comparison between the actual temperature / temperature change and the predetermined value.
  • the control system can compare the determined actual temperature or temperature change with a predetermined value and dependent on the result, mainly if the actual temperature or an actual temperature change exceeds the predetermined value, the control system is able to control at least one fluid valve of the several fluid valves.
  • the predetermined value could be a maximum allowable temperature. If the actual temperature exceeds the maximum temperature an opening of a fluid valve will lead to an introduction of cooling fluid into the steam and therefore a lowering of the temperature of the fluid and the piping.
  • the introduction of the cooling fluid, e.g. water, into the fluid (steam, hot water) at the output of the heat exchanger respectively superheater is only necessary under certain circumstances, especially if there is a threat of a too high temperature or especially a too fast increase of the temperature.
  • the cooling fluid e.g. water
  • a maximum temperature change could be used as predetermined value. If the increase of the main temperature goes beyond the maximum temperature change an opening of at least one fluid valve is triggered. This will reduce of even stop a further increase of the temperature of the steam and the piping.
  • both limits could be used in combination to analyze an inadmissible temperature or the danger of reaching an inadmissible temperature.
  • control system With the input from the temperature determination system the control system should be able to calculate the necessary reaction to protect the steam generating system and subsequent facilities from overheating or a too fast heat increase. Therefore, the control system must be connected with the fluid valves. On exceeding a predetermined value, the control system can open one or more of the fluid valves accordingly.
  • a maximum temperature could be used. It is also possible to use a maximum allowable temperature change as predetermined value.
  • a predetermined value as a maximum temperature dependent to the actual temperature change.
  • a predefined dependence of the maximal temperature to the temperature change could be defined with for example a higher maximal temperature if the temperature change is small and a lower maximal temperature if the temperature change is large.
  • a maximum temperature change dependent on the actual temperature could be used.
  • a greater maximum temperature change could be allowed at lower temperatures and a smaller maximum temperature change at higher temperatures.
  • faster temperature changes could be allowed with a faster increase of the power output and protective smaller temperature changes are applied if the temperature reaches relevant material limits.
  • the temperature of the fluid at the fluid output and/or the temperature of the fluid output is relevant to trigger the control system and further to trigger the opening the fluid valve in case of exceeding the predetermined value to protect the facilities.
  • the characteristic curve could be a predefined maximum temperature, which chances the value depending on a temperature change.
  • the characteristic curve is in this case predefined.
  • the control system uses the characteristic curve, which leads to predetermined value which is different dependent from the actual temperature change.
  • a trend analysis for the actual temperature it is possible to perform a trend analysis for the actual temperature. Therefore, the actual temperature needs to be recorded for a period. With this data of past temperatures and the current temperature a predictive temperature could be calculated. This leads to the possibility to compare not only the actual temperature with the predetermined value but also the predictive temperature and further the predictive temperature with the predetermined value. Also, a difference could be determined. With this information a further anticipatory driving of the fluid vales is possible.
  • the advantageous method uses a steam generation system, which is enabled to determine the temperature / temperature change at all fluid outputs at all heat-exchangers respectively the superheater. This leads to the possibility to compare all actual temperatures / temperature changes with respective predetermined values and to control the fluid valves dependent to the comparison both each fluid valve dependent to the respective comparison and also dependent to the comparison for other than the respective attemperator.
  • the fluid valves are opened dependent on the distance between the current situation and the allowable situation. So, if the difference is available, then it is further advantageous, to open a number of fluid valves of the several fluid valves dependent on the calculated difference.
  • the "to be opened fluid valves" could be chosen according further rules.
  • the protecting the steam generator could be improved and/or the efficiency could be increased, if there are not only an on-off state of the fluid vale.
  • the at least one fluid valve could be opened stepwise for example dependent on the difference between the actual temperature or temperature change and the predetermined value. Analog, the fluid valves to be triggered could also be chosen according further rules.
  • a further advantageous method to operate the steam generator system is enabled.
  • a main temperature change respectively a first temperature change respectively a second temperature change (and so on) could be determined.
  • the calculation of the difference enables in the next step to control the respective fluid valve and preferably also the other fluid valve dependent on the determined difference in a stepwise manner.
  • the temperature respectively the temperature changes is recorded over a period.
  • the difference between the last actual temperature respectively temperature change respectively and the corresponding previously determined predicted value could be calculated.
  • the difference between the predicted value and the corresponding predetermined value could be calculated.
  • the number of fluid valve are opened and/or the fluid valves are opened stepwise dependent from the comparison or preferably the calculated difference. This enables the anticipatory control of the steam temperature.
  • the new steam generation system as described before enables also a second inventive method to control the steam generation system. Therefore, again a steam generating system according to any of the preceding description is necessary.
  • This second method includes the steps: With the steam generation system comprising a vapor determination system in a first step it is necessary to determine the actual share of vapor of the fluid flowing through the piping before or after an attemperator.
  • Analog the usage of the determined temperatures the actual share of vapor has to be compared with a predetermined value.
  • control system is enabled to control at least one fluid valve.
  • the predetermined value could be a maximum or minimum allowed share of vapor.
  • the predetermined value could be the target share of vapor. If a maximum allowed share of vapor is set an (further) opening of the fluid valve could be triggered, if the actual share of vapor is exceeding the maximum allowed share of vapor. On the other hand, an (further) closing of the fluid valve could be triggered, if the share of vapor is below the predefined minimum share of vapor.
  • At least one fluid valve is opened dependent on the determined difference between the actual share of vapor and the respective predetermined value, e.g. the target share vapor.
  • an additional a share of vapor at a further attemperator could be determined. It is particular advantageous, if the share of vapor at all attemperators could be determined.
  • the same advantageous solutions apply as for the method with the temperature determination system. Therefore, it is advantageous, if the fluid valves could be opened stepwise and/or in groups.
  • the predetermined value represents a share of vapor of at least 60% at the output of the respective heat exchanger (determined at the location before the following attemperator). It is particularly advantageous, if the share of vapor is at least 75%.
  • the predetermined value is advantageous a share of vapor of not more than 90%. It is particularly advantageous, if the predetermined value is a share of vapor of not more than 85%.
  • Analog to the method to control the steam generation system comprising a temperature determination system is the advantageous features are also beneficial to apply them to the method to control the steam generation system comprising a vapor determination system.
  • the predetermined value could be a defined share of vapor. It is also possible to use the change of the share of vapor to control the fluid valves. Next, a difference between the actual share of vapor and a predefined share of vapor could be used to determine the necessary to act on at least one fluid valve. Also, a trend analysis could be used.
  • the vapor share is recorded over a period.
  • the share of vapor is known within the piping before or after at least one attemperator and with the knowing of the mass flow through at least one heat exchanger or the evaporator it should be possible to estimate the mass flow through the steam generator. But it is in particular advantageous, if the share of vapor is known at all attemperators and if the mass flow is known to the evaporator and also through the distribution piping to each of the attemperators. Then a precise determination of the mass flow and the share of vapor at each heat exchanger respective the superheater could be determined to enable the control system to determine the best setting for the fluid valve could be found to archive a high efficiency with lowering the risk of thermal damage.
  • the figure 1 shows schematically a power plant 07 with a gas turbine 09 and a steam turbine 08 and further as main part of the invention the steam generator 01.
  • the steam generator 01 comprises hot gas path 02 pass through the steam generator 01 from in hot gas input side to a waste gas output side.
  • the gas turbine 09 delivers - while enabling the generation of electrical energy with a generator - a flow of hot gas to the hot gas input side of the steam generator 01. After passing through the hot gas path 02 the previous hot gas will leave the steam generator 01 with a reduced temperature as waste gas at the waste gas output side.
  • the steam generator 01 comprises further several heat exchangers 11, which 11 are arranged at least partly within a hot gas path 02.
  • an evaporation fluid e.g. water/steam
  • the first heat exchanger along the hot gas path starting from the upstream hot gas input side is a so-called superheater 11A - see also fig 2 .
  • the fluid output line 12 is in connection with the steam turbine 02 to enable the further generation of electrical energy.
  • the gas turbine 09 increases its output of hot gas very quickly. This leads to the high increase of the heat input into the steam inside the superheater 11. This leads to high thermal stress at the steam turbine 08 and also at the piping inside the steam generator 01, e.g. the fluid output 17, and also for the piping from the steam generator 01 to the steam turbine 08.
  • FIG. 1 An example for the inventive steam generator 01 is shown schematically in figure 2 with a number of heat exchangers 11 and attemperators 22.
  • the steam generator 01 comprises as main part a casing with a hot gas path 02.
  • the hot gas path 02 extends from an input opening, where hot gas 03 is brought into the hot gas path 02. While crossing the steam generator 01 the gas cools down and leaves as waste gas 04 at an output side the hot gas path 02.
  • the steam generator comprises further several heat exchangers 11A-G. Those are arranged in this example adjacent to each other, whereby they could be also arranged with other elements in-between or in another order.
  • the heat exchanger close to the hot gas input is a so-called superheater 11A.
  • It 11A comprises a superheater fluid input 13A, wherein a superheater fluid output 17A of the superheater 11A delivers a stream of hot steam 05 and is connected with the steam turbine 08.
  • a first heat exchanger 11B is arranged next to the superheater 11A.
  • This 11B comprises analog a first fluid input 13B and a first fluid output 17B, whereby the first output 17B is connected with the superheater input 13A.
  • a second heat exchanger 11C is arranged next to the first heat exchanger 11B .
  • This 11B comprises analog a second fluid input 13C and a second fluid output 17C, whereby the second output 17C is connected with the first input 13B.
  • a third heat exchanger 11D is arranged next to the second heat exchanger 11C.
  • This 11D comprises analog a third input 13D and a third output 17D, whereby the third output 17D2 is connected with the second input 13C.
  • a fourth heat exchanger 11E is arranged next to the third heat exchanger 11D.
  • This 11E comprises analog a fourth input 13E and a fourth output 17E, whereby the fourth output 17E is connected with the third input 13D.
  • a fifth heat exchanger 11F is arranged next to the fourth heat exchanger 11E.
  • This 11F comprises analog a fifth input 13F and a fifth output 17F, whereby the fifth output 17F is connected with the fourth input 13E.
  • an economizer 11G is arranged.
  • This 11G comprises analog an economizer fluid input 13G and an economizer fluid output 17G.
  • the economizer output 17G is connected with the fifth input 13F.
  • Each of the superheater 11A and heat-exchangers 11B-11F enables and the economizer 11G enable the transfer of the heat from the hot gas 03 onto the fluid steam crossing the respective superheater 11A and heat-exchangers 11A-11F and economizer 11G.
  • On the respective fluid input 13 a fluid steam with a less high temperature and with a lower share of vapor is supplied. After the heat transfer the fluid stream leaves the respective fluid output 17 with a higher temperature and with a higher share of vapor.
  • the economizer input 13G is connected with a source of cold fluid 24. This is regular cold water.
  • a fluid supply valve 25 is arranged within the connection from the source of cold fluid 24 to the economizer input 13G.
  • the cold fluid from the source of cold fluid 24 should be heated in the economizer 11G by the usage of the remaining heat within the gas flowing through the hot gas path 02 up to a preferred temperature close the evaporation temperature but not exceeding this point. As result a hot, not evaporated fluid leaves the economizer 11G at the economizer output 17G.
  • a bypass line connects the source of cold fluid 24 with connection from the economizer output 17G to the last fluid input 13F. It is obvious, that further a fluid bypass valve 27 is necessary to control the flow of cold fluid through the bypass.
  • a main fluid valve 26 is arranged at the last fluid input 13F.
  • an attemperator 22F, 22D, 22C, 22B is arranged.
  • each of them 22 is connected with a distribution piping 21 to supply the respective attemperator 22 with a flow of not evaporated fluid.
  • the distribution piping 21 is then further connected with the economizer output 17G and through the bypass to the source of cold fluid 24 to guarantee a fluid "free of vapor" in the distribution piping 21.
  • the arrangement of a main valve 26 at the input of the last heat exchanger 11F also affects the flow of fluid from the economizer 11A into the distribution piping 21. Further the flow of fluid from the source of cold 24 fluid through the bypass to the distribution piping 21 is controlled by a fluid bypass valve 27 within the bypass.
  • a main attemperator 22A is arranged at the superheater output 17A.
  • This attemperator 22A is also connected with the distribution piping 21, whereby a fluid valve 23A is arranged to control the flow of fluid from the distribution piping 21 into the main attemperator 22A.
  • FIG. 3 An exemplary solution for an advantage implementation of the invention in further detail at a heat exchanger/superheater 11 is shown in Fig. 3 .
  • the relevant part of the steam generator 01 is pictured with the section of the hot gas path 02 and the arrangement of one heat exchanger 11.
  • the heat exchanger 11B-11F or superheater 11A comprises a piping with the fluid input 13, which 13 is in connection with forgoing heat exchanger (not shown in this figure). From the fluid input 13 two (exemplary) distribution pipes 14.1 and 14.2 branches off. Several heat exchangers tubes 15 are each connected to one of the distribution pipes 14. On the other end of the heat exchange tubes 18 collection pipes 16.1 and 16.2 are arranged, which 16 then are in connection with the fluid output 17.
  • a fluid steam 12 with a lower temperature is supplied to the fluid supply line 13.
  • the steam flows through the distribution pipes 14 into the heat exchange tubes 15, where the heat is transferred from the hot gas inside the hot gas path 02 onto the fluid steam inside the heat exchange tubes 15.
  • the hot fluid steam is collected in the collection pipes 16 and transferred to the fluid output 17 and leaves the heat exchanger/superheater 11 as fluid steam 18 with a higher temperature.
  • Attemperators 22.1, 22.2 are arranged. Therefore, in this advantage solution an attemperator 22.1 22.1 and 22.2 is arranged within each of the collection pipes 16.1 and 16.2.
  • the attemperators 22 are supplied with a cooling fluid, e.g. water, from the distribution piping 21.
  • a cooling fluid e.g. water
  • 11 represents any of the superheater 11A or heat-exchangers 11B-11F or economizer 11G (same with the fluid input 13, fluid output 17).
  • 22 represents any attemperator 22A-22B or 22.1 or 22.2 (same with the fluid valves 23)

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP20196335.2A 2020-09-16 2020-09-16 Dampferzeuger mit einspritzkühlern Withdrawn EP3971396A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP20196335.2A EP3971396A1 (de) 2020-09-16 2020-09-16 Dampferzeuger mit einspritzkühlern
KR1020237012731A KR20230069191A (ko) 2020-09-16 2021-08-09 감온기가 있는 증기 발생기
JP2023540985A JP2023541492A (ja) 2020-09-16 2021-08-09 過熱低減器を有する蒸気発生器
US18/245,426 US20230358396A1 (en) 2020-09-16 2021-08-09 Steam generator with attemperators
PCT/EP2021/072139 WO2022058091A1 (en) 2020-09-16 2021-08-09 Steam generator with attemperators
EP21762395.8A EP4214405A1 (de) 2020-09-16 2021-08-09 Dampferzeuger mit einspritzkühlern

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20196335.2A EP3971396A1 (de) 2020-09-16 2020-09-16 Dampferzeuger mit einspritzkühlern

Publications (1)

Publication Number Publication Date
EP3971396A1 true EP3971396A1 (de) 2022-03-23

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EP20196335.2A Withdrawn EP3971396A1 (de) 2020-09-16 2020-09-16 Dampferzeuger mit einspritzkühlern
EP21762395.8A Pending EP4214405A1 (de) 2020-09-16 2021-08-09 Dampferzeuger mit einspritzkühlern

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US (1) US20230358396A1 (de)
EP (2) EP3971396A1 (de)
JP (1) JP2023541492A (de)
KR (1) KR20230069191A (de)
WO (1) WO2022058091A1 (de)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0828808A (ja) * 1994-07-19 1996-02-02 Babcock Hitachi Kk 廃熱回収ボイラ装置およびその制御方法
DE19734862A1 (de) * 1997-08-12 1999-02-18 Bernd Gericke Wärmekraftwerk mit einer Gasturbine und einem Dampferzeuger für eine Mehrdruck-Dampfturbine
US20050274113A1 (en) * 2004-06-11 2005-12-15 Takaaki Sekiai Steam temperature control system, method of controlling steam temperature and power plant using the same
WO2008152205A1 (en) * 2007-06-15 2008-12-18 Åf-Consult Oy Combustion plant and method for the combustion
US20160040549A1 (en) * 2013-04-10 2016-02-11 Siemens Aktiengesellschaft Method for flexible operation of a power plant
US20180371956A1 (en) * 2015-12-22 2018-12-27 Siemens Energy, Inc. Stack energy control in combined cycle power plant

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0828808A (ja) * 1994-07-19 1996-02-02 Babcock Hitachi Kk 廃熱回収ボイラ装置およびその制御方法
DE19734862A1 (de) * 1997-08-12 1999-02-18 Bernd Gericke Wärmekraftwerk mit einer Gasturbine und einem Dampferzeuger für eine Mehrdruck-Dampfturbine
US20050274113A1 (en) * 2004-06-11 2005-12-15 Takaaki Sekiai Steam temperature control system, method of controlling steam temperature and power plant using the same
WO2008152205A1 (en) * 2007-06-15 2008-12-18 Åf-Consult Oy Combustion plant and method for the combustion
US20160040549A1 (en) * 2013-04-10 2016-02-11 Siemens Aktiengesellschaft Method for flexible operation of a power plant
US20180371956A1 (en) * 2015-12-22 2018-12-27 Siemens Energy, Inc. Stack energy control in combined cycle power plant

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US20230358396A1 (en) 2023-11-09
EP4214405A1 (de) 2023-07-26
JP2023541492A (ja) 2023-10-02
KR20230069191A (ko) 2023-05-18
WO2022058091A1 (en) 2022-03-24

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