NO760980L - - Google Patents
Info
- Publication number
- NO760980L NO760980L NO760980A NO760980A NO760980L NO 760980 L NO760980 L NO 760980L NO 760980 A NO760980 A NO 760980A NO 760980 A NO760980 A NO 760980A NO 760980 L NO760980 L NO 760980L
- Authority
- NO
- Norway
- Prior art keywords
- steam
- hot water
- turbine
- heating
- heated
- Prior art date
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 69
- 238000010438 heat treatment Methods 0.000 claims description 32
- 239000007789 gas Substances 0.000 claims description 25
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims description 4
- 239000003546 flue gas Substances 0.000 claims description 4
- 238000002485 combustion reaction Methods 0.000 description 5
- 238000005485 electric heating Methods 0.000 description 4
- 239000000446 fuel Substances 0.000 description 4
- 238000007872 degassing Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000002562 thickening agent Substances 0.000 description 2
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
- F01K17/025—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic in combination with at least one gas turbine, e.g. a combustion gas turbine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- 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
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- 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
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
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)
Description
Oppfinnelsen angår et gassturbinvarmekraftverk, omfattende en gassturbinenhet med etterfølgende varmekjele for oppvarming av varmtvann. Slike varmekraftverk er kjent. I den forbindelse er det også kjent for temperaturregulering å anordne en shuntledning mellom varmtvannstilbakeløpet og varmtvannsfrem-løpet. Videre er det kjent å anordne et ekstra hjelpebrennkammer for å dekke toppvarmebehov og reserve. The invention relates to a gas turbine thermal power plant, comprising a gas turbine unit with a subsequent boiler for heating hot water. Such thermal power plants are known. In this connection, it is also known for temperature regulation to arrange a shunt line between the hot water return and the hot water forward. Furthermore, it is known to arrange an additional auxiliary combustion chamber to cover peak heating needs and reserve.
Ved fjernvarmeforsyning, f.eks. ved hjelp av anlegg av den inneldningsvis nevnte art, må det imidlertid tas hensyn til at til varmeoverføringsrørledningene kan det. bare til-sluttes avtagergrupper hvor a) det foreligger en bestemt minste varmestrømtetthet fordi ellers ville varmefordelingsbehovet bli ukonomisk stort. b) Det ved romoppvarming allerede forekommer et varmtvanns-sirkulasjonssytem elier kan installeres et slikt efterpå. In case of district heating supply, e.g. with the help of facilities of the kind mentioned at the outset, it must be taken into account that for the heat transfer pipelines it can customer groups are only connected where a) there is a specific minimum heat flow density because otherwise the need for heat distribution would be uneconomically large. b) A hot water circulation system already exists for space heating, or such a system can be installed afterwards.
I mange tilfeller foreligger imidlertid slike forhold eller slike betingelser at en med hensyn til vamrebehov vesentlig avtagergruppe ikke kan nås via en varmeoverførings-rørledning, særlig når det gjelder økonomiske betraktninger som avgjørende kriterier. Kravene til miljøvern og sparsom anvendelse av fosile brennstoffer kan disse avtagergrupper ikke nås via rørledninger, men nås f.eks. ved direkte elektrisk oppvarming eller ved en kombinasjon av direkte elektrisk oppvarming og lagringsoppvarming eller ved en kombinasjon av direkte elektrisk oppvarming og elektrisk drevende varmepumper. In many cases, however, there are such conditions or such conditions that, with regard to heating needs, a significant customer group cannot be reached via a heat transfer pipeline, especially when it comes to economic considerations as decisive criteria. The requirements for environmental protection and sparing use of fossil fuels cannot be met by these consumer groups via pipelines, but can be reached e.g. by direct electric heating or by a combination of direct electric heating and storage heating or by a combination of direct electric heating and electrically driven heat pumps.
Det er derfor allerede foreslått et fjernvarme-system (^rown Boveri Mitteilungen 6-73,, side 253 til 263) hvor avtagergruppene skal forsynes med tilstrekkelig varmetetthet med varmtvann via rørledninger kan fjernforsyne avtagergrupper som ellers ikke kan nås ved direkte elektrisk oppvarming. Den elektriske energi for fjernvarmeforsyning av forbrukere som ikke kan nås via varmeoverføringsrørledninger, skal der frembringes ved hjelp av mottrykksdrift av varmekraftverket. For store anlegg foreslås i denne artikkel anvendelse av høyttrykksdamp-kjeler med mottrykksturbogrupper eller gassturbinanlegg med utnyttelse av tapsvarme. A district heating system has therefore already been proposed (^rown Boveri Mitteilungen 6-73,, page 253 to 263) where the consumer groups must be supplied with sufficient heat density with hot water via pipelines, can remotely supply consumer groups that cannot otherwise be reached by direct electric heating. The electrical energy for district heating supply of consumers who cannot be reached via heat transfer pipelines must be produced there by means of back pressure operation of the thermal power plant. For large plants, this article proposes the use of high-pressure steam boilers with counter-pressure turbo groups or gas turbine plants using waste heat.
Hensikten med foreliggende oppfinnelse er å tilveiebringe et varmefosyningsanlegg nemlig et gassturbinvarmekraftverk som er særlig godt egnet for oppnåelse av de ovenfor antydede ønskemål, særlig størst mulig brennstoffutnyttelse ved stor strømfrembringelse i mottrykksdrift. The purpose of the present invention is to provide a heat fueling plant, namely a gas turbine heat power plant which is particularly well suited for achieving the above-mentioned objectives, in particular the greatest possible fuel utilization with large power generation in back pressure operation.
Dette oppnås ifølge oppfinnelsen _ved at varmtvannsoppvarmingen skjer i to parallellkoplede grener av hvilke den ene oppvarmes med mottrykksdamp fra dampturbinen som driver en elektrisk generator, og varmekjelen er innrettet for frembringelse av damp for drift av turbinen, og at den andre gren er ført gjennom kjelens lavtemperaturområde resp. gjennom en der anordnet varmt-vannbereder for oppvarming med røkgass. Denne oppdeling av varmtvannsoppvarmingen i en dampoppvarmet del og en røkgass-oppvarmet del i lavtrykkstemperaturområde av kjelen muliggjør en vidtgående utnyttelse av brennstoffvarmen for strøm- og varme-frembringelse. Her blir en bemerkelsesverdig andel av brenn-stof fvarmen omsatt i elektrisk energi. Dermed kan en tilsvarende større del av varmeavtagende som ikke på økonomisk måte kan forsynes via rørledning forsynes med strøm fra sammen anlegg. This is achieved according to the invention _by the fact that the hot water is heated in two parallel-connected branches, one of which is heated with back-pressure steam from the steam turbine that drives an electric generator, and the boiler is designed to produce steam for operating the turbine, and that the other branch is led through the boiler's low-temperature area respectively through a hot water heater arranged there for heating with flue gas. This division of the hot water heating into a steam-heated part and a flue gas-heated part in the low-pressure temperature range of the boiler enables extensive utilization of the fuel heat for power and heat generation. Here, a remarkable proportion of the fuel heat is converted into electrical energy. In this way, a correspondingly larger part of heat sinks that cannot be economically supplied via pipelines can be supplied with electricity from the combined plant.
Fortrinnsvis er det for den gren som oppvarmesPreferably, it is for the branch that is heated
med mottrykksdamp anordnet minst to på vannsiden etter hverandre kopléde varmtvannsvarmere og mottrykket på uttaksstedet av turbinen har forskjellig verdi og tilsvarer forskjellen i trykkbehovet av damp for cfe enkelte varmtvannsvarmere. På denne måte kan turbinene være utformet som tostrøms mottrykksturbiner med midtinnstrømning og uttaksstedene for forsyning av varmtvanns-berederne med vanndamp er anordnet ved de ytre ender av turbin-strømmene. Ved denne totrinnsoppvarming av varmtvannet "oppnås et særlig stort strømutbytte for mottrykksdampen. with back-pressure steam arranged on the water side at least two successively connected hot water heaters and the back pressure at the outlet point of the turbine has a different value and corresponds to the difference in the pressure demand of steam for cfe individual hot water heaters. In this way, the turbines can be designed as two-flow counter-pressure turbines with central inflow and the outlet points for supplying the hot water heaters with steam are arranged at the outer ends of the turbine flows. With this two-stage heating of the hot water, a particularly high current yield is achieved for the back pressure steam.
For ved toppvarmebehov å kunne oppnå en over-temperatur på varmtvannet som er høyere enn den vanlige tempe-ratur, kan de med mottrykksdamp oppvarmede varmtvannsvarmere på vannsiden minst ha en ytterligere varmtvannsvarmer koplet efter seg som ved toppvarmebehov oppvarmes med damp fra friskdampnettet In order to be able to achieve an over-temperature of the hot water that is higher than the normal temperature in case of peak heating demand, the hot water heaters heated with counter-pressure steam on the water side can at least have an additional hot water heater connected after them which, in case of peak heating demand, is heated with steam from the fresh steam network
via en reduksjonsinnretiiing.via a reduction arrangement.
En annen måte å øke forhåndstemperaturen av varmtvannet på som kan anvendes i tillegg til eller i stedet for den nevnte måte hvor varmtvannsvarmeren oppvarmes fra firskdampnettet, er mulig ved at det i delgrenen for den med røkgass oppvarmede vannvarmer efter den røkgassoppvarmede varmtvannsvarmer er anordnet et forgreningssted fra hvilken det avgrenes en med reguleringsventil forsynt ledning som munner ut i delgrenen for det kalde tilbakeløpsvann, på et sted foran den første dampoppvarmede varmtvannsvarmer. Another way to increase the pre-temperature of the hot water, which can be used in addition to or instead of the aforementioned method where the hot water heater is heated from the fresh steam network, is possible by arranging a branch point in the sub-branch for the flue gas-heated water heater after the flue gas-heated hot water heater from from which a line fitted with a control valve is branched off, which opens into the partial branch for the cold return water, at a place in front of the first steam-heated hot water heater.
Strømmen som frembringes i den av dampturbinen drevne elektriske generator og/eller i gassturbogeneratoren tjener til forsyning av de varmeavtagere som ikke på økonomisk måte kan nås via rørledninger. The current produced in the electric generator driven by the steam turbine and/or in the gas turbogenerator serves to supply the heat exchangers that cannot be economically reached via pipelines.
Ved hjelp av et ekstra tilbakekjølingsanlegg som ikke er i drift under oppvarmingsperioden, dvs. når anlegget arbeider i sin helhet som varmekraftverk og som utenfor oppvarmingsperioden eller ved små varmebehov, dvs. ved fullstendig eller delvis utkoplet varmtvannsoppvarming, og ved drift av anlegget for toppstrømfrembringelse eller ved anvendelse som reserveanlegg kan den tapte varme fra dampturbinen helt eller delvis avgis til omgivelsene.... Denne anvendelsesmulighet av gassturbinvarmekraftverket kan lett istandbringes med et for-holdsvis lite tilbakekjølingsanlegg. Det kan på den måte frembringes toppytelser med god termisk virkningsgrad. By means of an additional cooling system which is not in operation during the heating period, i.e. when the plant works in its entirety as a thermal power plant and as outside the heating period or in case of small heating needs, i.e. when hot water heating is completely or partially switched off, and when operating the plant for peak flow generation or when used as a reserve plant, the lost heat from the steam turbine can be fully or partially emitted to the surroundings.... This application possibility of the gas turbine thermal power plant can easily be restored with a relatively small recooling plant. In this way, top performances with good thermal efficiency can be produced.
Oppfinnelsen skal nedenfor forklares nærmere under henvisning til tegningen som skjematisk viser et ut-førelseseksempel på oppfinnelsen. The invention will be explained in more detail below with reference to the drawing which schematically shows an embodiment of the invention.
Utførelseseksempelet omfatter en gassturboenhet med en gassturbin 23 som driver en fortøtter 22 og en elektrisk generator 24. Foruten det for normal drift beregnede brennkammer 25 er det i avgasstrømmen fra gassturbinen anordnet et hjelpebrennkammer 4 med tilhørende hjelpefortøtter 5- The design example comprises a gas turbo unit with a gas turbine 23 that drives a thickener 22 and an electric generator 24. In addition to the combustion chamber 25 designed for normal operation, an auxiliary combustion chamber 4 with associated auxiliary thickener 5 is arranged in the exhaust gas flow from the gas turbine
Efter gassturbinenheten 1 er koplet en kjele 2 i hvilken det frembringes overhetet damp som enten helt eller After the gas turbine unit 1 is connected a boiler 2 in which superheated steam is produced which is either completely or
delvis via et trykk- og temperaturreguleringssted 12 direkte via Mningen 50 avgir industridamp eller helt eller delvis damp til en dampturbin 3- Kjelen 2 inneholder en økonomiseringsdel 26, en fordamper 27 og en overheter 28 og drives av avgassen fra gassturbinen 23- Som dampturbin 3 er i utførelseseksempelet partly via a pressure and temperature regulation point 12 directly via Mningen 50 emits industrial steam or all or part of steam to a steam turbine 3- The boiler 2 contains an economizer part 26, an evaporator 27 and a superheater 28 and is powered by the exhaust gas from the gas turbine 23- As steam turbine 3 is in the execution example
valgt en totrinns turbin med midtinnstrømning som driver en elektrisk generator 14. selected a two-stage mid-inflow turbine driving an electric generator 14.
En vannvarmer 21 i kjelen 2 ervforbundétA water heater 21 in the boiler 2 inherited
med en fremløpsledhing 19 til forbrukerne for varmt vann, og med en tilbakeløpsledning 20 som inneholder en pumpe 49 for det kalde tilbakeløpsvann. For delgrenen 31 som oppvarmes med motttrykkdamp er det valgt to på vannsiden efter hverandre koplede varmtvannsvarmere 6a og 6b som tilføres mottrykksdamp via ledninger 29 og 30. Efter de to varmtvannsvarmere 6a og 6b er det på vannsiden koplet en varmtvannsvamrer 6c som kan utnyttes ved toppvarmebehov med drift fra friskdampnettet 32 via en reduseringsinnretning 11. Kondensatét fra varmtvannsvarmerne 6a,6b og 6c blir via ledninger 34, 33335resp. ved hjelp av kondensatpumper 36 og 37 tilført en avgassblandefor-varmer 7 som på en annen side tilføres damp for ytterligere oppvarming og for avgassing av vannet fra dampturbinen 3 via ledning-ene 38. Avgassings- blandeforvarmeren 7 kan via en ledning 39 resp. ved hjelp av pumpen 40 tlføres tilsetningsvann som er erstatning for vann som er godt tapt i kretsløpet resp. som erstatning ved levering av industridamp. For kjemisk oppberedr..' ning av tilsetningsvannet er det anordnet en innretning 51- Fra avgassningsblandeforvåSneren :7 føres vannet så via ledningen 4l resp. matepumpen 42 til kjelen 2 hvorved kretsløpet er sluttet. with a flow line 19 to the consumers for hot water, and with a return line 20 containing a pump 49 for the cold return water. For branch 31, which is heated with back-pressure steam, two hot water heaters 6a and 6b connected one after the other on the water side have been selected, which are supplied with back-pressure steam via lines 29 and 30. After the two hot water heaters 6a and 6b, a hot water heater 6c is connected on the water side, which can be used in case of peak heating demand with operation from the fresh steam network 32 via a reduction device 11. The condensate from the hot water heaters 6a, 6b and 6c is via lines 34, 33335resp. by means of condensate pumps 36 and 37 supplied to an exhaust gas mixing preheater 7 which, on the other hand, is supplied with steam for further heating and for degassing the water from the steam turbine 3 via the lines 38. The degassing mixing preheater 7 can via a line 39 resp. with the aid of the pump 40, make-up water is supplied as a replacement for water that is well lost in the circuit or as compensation for the supply of industrial steam. For the chemical treatment of the additive water, a device 51 has been arranged - From the degassing mixer :7, the water is then fed via the line 4l resp. feed pump 42 to boiler 2, whereby the circuit is closed.
En annen delgren for varmtvannet som oppvarmes med røkgass i lavtrykkstemperaturområdet av kjelen 2 resp. føres gjennom den der anordnende varmtvannsoppvarmer 21. Et forgreningssted for de to delgrener er betegnet med 43 og et annet sted hvor de to delgrener efter oppvarming av varmtvannet igjen flyter sammen er betegnet med 44. Efter forgreningsstedet 43 er det i grenen for kaldttilbakeløpsvann anordnet en regulerings-innretning resp. en reguleringsventil 10 ved hjelp av hvilke en del av tilbakeløpsvannet som tilføres de dampoppvarmede varmtvannsvarmere 6a og 6b er innstillbare. En tilbakeslags-ventil 45 er anordnet efter reguleringsventilen 10. Another branch for the hot water that is heated with flue gas in the low-pressure temperature range of the boiler 2 or is led through it where the hot water heater 21 is arranged. A branching point for the two sub-branches is denoted by 43 and another place where the two sub-branches, after heating the hot water, flow together again is denoted by 44. After the branching point 43, a regulating valve is arranged in the branch for cold return water - device or a control valve 10 by means of which part of the return water supplied to the steam-heated hot water heaters 6a and 6b is adjustable. A non-return valve 45 is arranged after the control valve 10.
Den røkgassoppvarmede varmtvannsvarmer 21 er helt eller delvis shuntbar ved hjelp av en blandeventil 8 i ledningen 15. Videre er det i delgrenen for den med røkgass oppvarmede vannvarmer 21 og efter denne anordnet et oforgrenings-sted l6 som via en pumpe 48 og enreguleringsventil 9 og en ledning 17 munner ut i delgrenen for det kalde tilbakeløpsvann foran det første dampoppvarmede varmtvannsvarmer 6a, nemlig på stedet 18. Et målested 47 er anordnet i fremløpsledningen 19, hvor øyeblikksverdien av fremløpstemperaturen t vmåles og tilføres en regulator 16 som ved ikke viste hjelpemidler styrer reguleringsventilen 10. The flue gas-heated hot water heater 21 can be completely or partially shunted by means of a mixing valve 8 in the line 15. Furthermore, in the sub-branch for the flue gas-heated water heater 21 and after this, a branching point l6 is arranged which via a pump 48 and a control valve 9 and a line 17 opens into the partial branch for the cold return water in front of the first steam-heated hot water heater 6a, namely at location 18. A measuring point 47 is arranged in the supply line 19, where the instantaneous value of the supply temperature tv is measured and supplied to a regulator 16 which controls the control valve 10 by auxiliary means not shown .
Gassturbinvarmekraftverket ifølge utførelses-eksemplet virker på følgende måte: Under normal drift blir en del (største delen) av det kalde tilbakeløpsvann via reguleringsventilen 10 tilført de to efter-hverandre koplede dampoppvarmede overflatevarmtvannsvarmere 6a og 6b og her oppvarmet til den ønskede fremløpstemperatur t , The gas turbine heating power plant according to the design example works in the following way: During normal operation, part (the largest part) of the cold return water is supplied via the control valve 10 to the two sequentially connected steam-heated surface hot water heaters 6a and 6b and here heated to the desired flow temperature t,
mens den andre del av det kalde tilbakeløpsvann i kjelens 2 avgasstrøm oppvarmes til den ønskede fremløpstemperatur. while the other part of the cold return water in the boiler 2 exhaust gas flow is heated to the desired flow temperature.
Normalt er ingen andre reguleringsinngrep'nød-vendige. Oppdelingen av varmtvannsoppvarmingen ved totrinns damp-oppvarming -,og ved røkgassoppvarming skjer slik at på den ene side den damp som frembringes av avgassen (minus den direkte avgitte industridamp) efter å ha passert dampturbinen 3 utnyttes fullstendig for varmtvannsoppvarming og på den annen side at restavgassvarmen som i kjelen 2 ikke benyttes for dampfremstilling, utnyttes for varmtvannsoppvarming inntil tillatt kjeleavgass-temperatur. Normally, no other regulatory intervention is necessary. The division of the hot water heating in two-stage steam heating - and in flue gas heating occurs so that on the one hand the steam produced by the exhaust gas (minus the directly released industrial steam) after passing the steam turbine 3 is fully utilized for hot water heating and on the other hand that the residual gas heat which in boiler 2 is not used for steam production, is used for hot water heating up to the permitted boiler exhaust gas temperature.
Hvis det er ønskelig med lavere fremløpstemperatur dvs. med mindre varmebehov hos .'forbrukerne som er tilsluttet varmtvannsnettet, så åpnes blandeventilen 8. Ved full åpning av denne ventil shuntes den røkgassoppvarmede varmtvannsvarmer 21 fullstendig-.. Er derimot en høyere fremløpstemperatur ønskelig'altså når utetemperaturen synker til en meget lav verdi, kan en del av det allerede i den røkgassoppvarmede varmtvannsvarmer 21 oppvarmede varmtvann via ventilen 9 bringes inn foran den dampoppvarmede varmtvannsoppvarmer 6a slik at fremløpstemperaturen øker og energifrembringelsen i dampturboenheten resp. i damp^ turbinen 3 minskes tilsvarende. Som ytterligere forholdsregel for å øke fremløpstemperaturen tjener den allerede nevnte re-duksjonsventil 11. Ved åpning av denen ventil blir det en del av friskdampem tilført den tredje varmtvannsvarmer 6c hvilket er forbundet med en minskning av strømfrembringelsen i gene-ratoren 14 ved hjelp av dampturboenheten resp. dampturbinen 3- If it is desirable to have a lower flow temperature, i.e. with less heating demand from the consumers who are connected to the hot water network, then the mixing valve 8 is opened. When this valve is fully opened, the flue gas-heated hot water heater 21 is completely shunted... If, on the other hand, a higher flow temperature is desired, that is when outside temperature drops to a very low value, part of the hot water already heated in the flue gas-heated hot water heater 21 can be brought in via the valve 9 in front of the steam-heated hot water heater 6a so that the supply temperature increases and the energy production in the steam turbo unit resp. in steam^ the turbine 3 is reduced accordingly. As a further precaution to increase the supply temperature, the already mentioned reduction valve 11 serves. When this valve is opened, part of the fresh steam is supplied to the third hot water heater 6c, which is associated with a reduction in the power generation in the generator 14 by means of the steam turbo unit resp. . steam turbine 3-
Ved ekstremt høye varmtvannsbehov tas hjelpe-brennkammerét 4 i bruk. Ved denne ekstra anvendles av brenn-stoffvarme øker aveasstemneraturan før innløpet i kjelen 2 tilsvarende. Dermed øker også dampproduksjonen i kjelen og damptrykket øker med helt åpne dampturbininnløpsvehtil. Hjelpebrennkammeret 4 tjener samtidig som reserve ved svikt av gassturbinen 23- In case of extremely high hot water needs, the auxiliary combustion chamber 4 is used. With this extra use of fuel heat, the ash temperature before entering boiler 2 increases accordingly. This also increases the steam production in the boiler and the steam pressure increases with fully open steam turbine inlet valves. The auxiliary combustion chamber 4 also serves as a reserve in case of failure of the gas turbine 23-
De ovenfor nevnte ekstra innretninger for påvirkning av fremløpstemperaturen Tv kan styres for hånd. The above-mentioned additional devices for influencing the supply temperature Tv can be controlled by hand.
Der er naturligvis også mulig å styre disse ved en regulerings-innretning som er innrettet slik at den nominelle verdi for fremløpstemperaturen endres autoamtisk i avhengighet av utetemperaturen. Of course, it is also possible to control these by means of a control device which is arranged so that the nominal value for the supply temperature changes automatically depending on the outside temperature.
Oppfinnelsen er ikke begrenset til det beskrevne utførelseseksempel. Forskjellige modifikasjoner av konstruksjons-og koplingsteknisk art er tenkbar. Således vehøver ikke dampturbinen 3 være en tostrømsturbin den kan også være utformet som en enstrømsmottrykksturbin. Oppvarmingen av varmtvannet ved hjelp av mottrykksdamp kan også være utført i et trinn. Slutte-lig er det også mulig for gassturboenheten og anvende et lukket gassturbinanlégg i stedet for det viste åpne gassturbinanlegg. The invention is not limited to the described embodiment. Various modifications of construction and connection technology are conceivable. Thus, the steam turbine 3 does not have to be a two-flow turbine, it can also be designed as a single-flow back pressure turbine. The heating of the hot water using counter-pressure steam can also be carried out in one step. Finally, it is also possible for the gas turbo unit to use a closed gas turbine system instead of the open gas turbine system shown.
Claims (3)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2512774A DE2512774C2 (en) | 1975-03-22 | 1975-03-22 | Combined gas-steam turbine system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| NO760980L true NO760980L (en) | 1976-09-23 |
Family
ID=5942189
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| NO760980A NO760980L (en) | 1975-03-22 | 1976-03-19 |
Country Status (6)
| Country | Link |
|---|---|
| AT (1) | AT352350B (en) |
| DE (1) | DE2512774C2 (en) |
| DK (1) | DK121876A (en) |
| FI (1) | FI58002C (en) |
| NL (1) | NL7602877A (en) |
| NO (1) | NO760980L (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH636674A5 (en) * | 1978-07-28 | 1983-06-15 | Bbc Brown Boveri & Cie | CLOSED HEATING WATER CIRCUIT, IN PARTICULAR TO USE THE WASTE HEAT OF A HEATER BOILER, WITH A PRESSURE CONTROL DEVICE. |
| EP0020821A1 (en) * | 1979-07-02 | 1981-01-07 | BBC Aktiengesellschaft Brown, Boveri & Cie. | Method for the utilisation of waste heat from exhaust gases |
| HU202958B (en) * | 1984-01-11 | 1991-04-29 | Energiagazdalkodasi Intezet | Method for combined electric power and heat producing at power plants operating with boilers of heat utilization |
| DE3928771A1 (en) * | 1989-08-31 | 1991-03-07 | Asea Brown Boveri | GENERATION OF STEAM AND ELECTRICITY FOR THE START-UP AND / OR AUXILIARY OPERATION OF A STEAM POWER PLANT |
| DE4117191C2 (en) * | 1991-05-25 | 1994-11-24 | Saarbergwerke Ag | Combined gas-steam power plant to generate energy |
| GB9225949D0 (en) * | 1992-12-11 | 1993-02-03 | British Gas Plc | Combined heat and power apparatus |
| DE19545668A1 (en) * | 1995-12-07 | 1997-06-12 | Asea Brown Boveri | Method for operating a gas turbine group combined with a waste heat steam generator and a steam consumer |
| DE19720881A1 (en) * | 1997-05-17 | 1998-11-19 | Asea Brown Boveri | Combined heat and power station with conversion turbines |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB660090A (en) * | 1949-01-11 | 1951-10-31 | Svenska Turbinfab Ab | Method of operating a steam-power plant comprising a gas turbine or other heat engine producing exhaust gases, a steam producer and a steam turbine with associated condenser |
| CH303789A (en) * | 1952-07-12 | 1954-12-15 | Sulzer Ag | Device for damping pressure pulsations in a liquid-carrying line. |
| CH547435A (en) * | 1972-01-22 | 1974-03-29 | Sulzer Ag | COMBINED GAS TURBINE-STEAM POWER PLANT. |
-
1975
- 1975-03-22 DE DE2512774A patent/DE2512774C2/en not_active Expired
-
1976
- 1976-03-15 FI FI760673A patent/FI58002C/en not_active IP Right Cessation
- 1976-03-17 AT AT197476A patent/AT352350B/en not_active IP Right Cessation
- 1976-03-19 NL NL7602877A patent/NL7602877A/en not_active Application Discontinuation
- 1976-03-19 NO NO760980A patent/NO760980L/no unknown
- 1976-03-19 DK DK121876A patent/DK121876A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| DE2512774C2 (en) | 1982-09-02 |
| FI58002C (en) | 1980-11-10 |
| FI58002B (en) | 1980-07-31 |
| AT352350B (en) | 1979-09-10 |
| DK121876A (en) | 1976-09-23 |
| ATA197476A (en) | 1979-02-15 |
| DE2512774A1 (en) | 1976-09-30 |
| NL7602877A (en) | 1976-09-24 |
| FI760673A (en) | 1976-09-23 |
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