WO1998037314A1 - Procede et appareillage relatifs a une turbine a gaz et vapeur et a une utilisation de la chaleur - Google Patents

Procede et appareillage relatifs a une turbine a gaz et vapeur et a une utilisation de la chaleur Download PDF

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Publication number
WO1998037314A1
WO1998037314A1 PCT/BG1998/000004 BG9800004W WO9837314A1 WO 1998037314 A1 WO1998037314 A1 WO 1998037314A1 BG 9800004 W BG9800004 W BG 9800004W WO 9837314 A1 WO9837314 A1 WO 9837314A1
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WO
WIPO (PCT)
Prior art keywords
gas
steam
water
pipe
compressor
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Application number
PCT/BG1998/000004
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English (en)
Inventor
Nikolai Nikolaev Kolev
Dimitar Nikolaev Kolev
Nastia Nikolaeva Filipova
Original Assignee
Nikolai Nikolaev Kolev
Dimitar Nikolaev Kolev
Nastia Nikolaeva Filipova
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.)
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Priority claimed from BG101245A external-priority patent/BG62982B1/bg
Priority claimed from BG102176A external-priority patent/BG63223B1/bg
Application filed by Nikolai Nikolaev Kolev, Dimitar Nikolaev Kolev, Nastia Nikolaeva Filipova filed Critical Nikolai Nikolaev Kolev
Priority to AU57430/98A priority Critical patent/AU5743098A/en
Publication of WO1998037314A1 publication Critical patent/WO1998037314A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/047—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas having at least one combustion gas turbine
    • 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]

Definitions

  • the invention relates to a method for heat utilization at burning of gaseous and liquid fuels for producing heat and mechanical energy and to an installation for its realization and will find an application mainly in energetic, especially in the production of electricity and heat energy for district heating purposes.
  • a method [1] for heat utilization of burning of gaseous and liquid fuels wherein fuels are burnt under high pressures in a combustor, as for the combustor, air and overheated water steam are also injected therein.
  • the gas-steam udixture obtained is passed to the gas-steam turbine and then is cooled indirectly, thus its heat is used for obtaining overheated water steam that after overheating is passed to the combustor of the gas-steam turbine.
  • An installation [1] for realization of the method includes a gas- steam turbine, equipped with combustor, an air compressor and a boiler for obtaining overheated water steam connected to a pipe for injecting overheated water steam into the combustor.
  • a drawback of this method and of the installation of its realization is that the efficiency of converting the heat of fuel burning into mechanical energy and heat is not high enough and a significant portion of the water of the water steam passed to the combustor of the gas-steam turbine is loosed in the atmosphere together with the flue gases at the boiler outlet.
  • the aim of the invention is to develop a method that allows to increase the conversion of the heat transferred to the gas-steam turbine into mechanical energy produced in the installation at simultaneous complete utilization of the whole amount of heat passed with the fuel.
  • the invention is realized by a method for heat utilization of burning of gaseous and liquid fuels for producing mechanical and heat energy in an installation with a gas- steam turbine.
  • fuel burns under pressure in the combustor, as liici, compresscu air anu water steam, mamiy overneateu, are passedu to tne com ⁇ ustor.
  • the heated gas-steam mixture after its passage through the gas-steam turbine, is cooled indirectly according to the countercurrent principle, wherein its heat is utilized for heating products entering the combustor.
  • Characteristic feature of the method is that air and the fuel are passed for burning under pressure in one or more combustors of one or multistage gas-steam turbine.
  • Water steam is passed mainly only to the first combustor working under highest pressure.
  • the gas-steam mixture pre- treated in the previous stage of the gas-steam turbine, is passed for additional heating.
  • the gas-steam mixture is cooled indirectly after the final stage of the turbine, mainly by countercurrent, whereupon products entering to one or more combustors are heated.
  • Tne primarily cooled gas-steam mixture is cooled additionally m irectly using countercurrent, mai y y means ⁇ preneat uist ⁇ ct heating water. Then, it is cooled additionally directly by countercurrent using not less man vjiic »-.l ⁇ u ⁇ u ⁇ g w ⁇ iti iivjw lit ⁇ icu uy ilic g a-si ⁇ cini nii ⁇ iui t, wnd eLip ii nic w ⁇ ici steam transferred to the first combustor as well as a part of the water steam produced during the fuel burning condense from the gas-steam mixture. After its final cooling the gas-steam mixture is thrown out into the atmosphere, whereas water condense is obtained.
  • the coefficient of surplus air in the combustors is from 1.00 to 1.50, mainly from 1.00 to 1.10, as the lowest coefficient of surplus air, equal to 1 is characteristic mainly for the combustors of the gas-steam turbine stages, without the final one, whereas the highest coefficient is peculiar to the combustor of the final stage.
  • the coefficient of surplus air is determined regarding the fuel passed totally to the whole combustors.
  • the ratio of starting to final pressure in the stages of the gas-steam turbine varies from 1.3 to 20.0, mainly from 1.6 to 5.0 At the final stage it varies from 5 to 150, mainly from 10 to 30.
  • the gas-steam mixture leaving the gas-steam turbine, indirectly heats a chemically purified water condensate, which is heated and evaporated
  • the steam obtained is overheated, then entering the first combustor.
  • the chemically purified water condensate is obtained treating the water condense, removed during direct heating of the gas-steam mixture, by countercurrent using water steam which heats it additionally and takes the dissolved oxygen and carbon dioxide away from the condensate.
  • the gas-steam mixture obtained is mixed with the gas-steam udixture coming from the gas-steam turbine, mainly immediately after its last indirect cooling.
  • the water condensate, free of carbon dioxide and oxygen, is cooled in series and indirectly, initially by means of chemically purified water and afterwards using cold water and then it is purified chemically from the traces of ions contained, thus obtaining chemically purified water. Afterwards a portion of this water, obtained from the water condensate during the condensation of water steam, obtained at the fuel burning in the combustor, is removed from the system. The remaining chemically purified water is heated indirectly by water condensate, free of carbon dioxide and oxygen, and is passed for indirect heating, evaporation and overheating of the obtained water steam using me ne t Oi ne gas-steam mixture leaving tne gas-steam tut ine.
  • Air required for fuel burning in the combustors is removed after each of the final N stages of the compressor, whereupon the ratio of the outlet pressure at a given compressor stage, without the stage before air entering the first combustor, to the inlet pressure at the given stage varies from 1.3 to 20.0, mainly from 1.6 to 5.0 as at the final stage, after which air enters the first vjiiiuuanji, iliia ⁇ iAj v ⁇ nca iTuin ⁇ > lO IJU, iii ⁇ iiuy li ii t ⁇ I Ju.
  • compressing of air required for burning is achieved in two compressors, mainly multistage.
  • the number of stages of the second compressor is equal to the number of combustors.
  • the number of stages of the first compressor is lower by one Air enters the first stage under atmospheric pressure, whereas air after each stage of the first compressor is divided into two parts, afterwards the first one is cooled, mainly by means of district heating water, and is passed to the next stage of the first compressor.
  • the other part is passed to the next, according its uiiiuci, ai ⁇ g ui uic ac vjnu vjiiinicaa ⁇ i, as ⁇ m ic, lici Uic Iilai bldgc Oi uic n si compressor to the second stage of the second compressor.
  • Air in the first stage of the second compressor is passed under atmospheric pressure. Air from the all stages of the second compressor enters the corresponding, according to pressure, combustors.
  • the ratio of the outlet pressure at a given stage of the first compressor to the inlet pressure at this stage varies from 1.3 to 20, mainly from 1.6 to 5.0.
  • this ratio is respectively from 5 to 150, mainly from 10 to 30.
  • each of the water streams cooling directly, in series, by countercurrent, previously indirectly cooled gas-steam mixture transfer their heat indirectly to another water stream, mainly district heating water.
  • This is cnicVcvj accoruing to tne count ⁇ rcurr ⁇ nt principle, to a ⁇ i ⁇ tn variant or the method, the water streams, without the last of them, that cool directly in series, by countercurrent, a previously indirectly cooled gas-steam mixture transfer their heat indirectly to another water stream, mainly district heating water according to the countercurrent principle.
  • the last water stream transfers, by direct countercurrent, its heat to air, entering for compressing to a compressor, thus humidifying it.
  • the circulating water stream is passed back again to take away the heat of the gas-steam mixture.
  • the method is applied by an installation with a gas-steam turbine for heat u ⁇ nz, ⁇ vj ⁇ ⁇ i uuinnig ⁇ j ⁇ g ⁇ ac ua ⁇ nt nv-
  • the installation includes a gas-steam turbine and connected to its shaft a mechanical load, mainly an electricgenerator, as the gas-steam turbine is connected by- means of a gas pipe for a gas-steam mixture to a heat exchanger for heat utilization from the gas-steam turbine for producing overheated water steam, as the gas-steam turbine is also connected to a combustor, which is connected to a fuel passing pipe, as it is connected also to a compressor by a compressed air pipe.
  • the installation includes also a system for water steam condensation.
  • a characteristic feature of the installation is that uic g s-sic ⁇ mizi u c la uiviucu iniO I ⁇ subgcS, cci n ui dressingii iilciu iiig One c liIUU i i .
  • the space at the outlet of a given stage, without the last one, is connected by an intermediate gas pipe for a gas-steam mixture to the combustor at the following stage of the gas-steam turbine.
  • it is connected by means of a gas pipe for an additionally heated gas-steam ⁇ uxture to its corresponding stage of the gas-steam turbine.
  • Each combustor is also connected to a pipe for fuel passage and to a compressed air gas pipe.
  • the gas-steam turbine is also connected by the first gas-steam mixture pipe to a heat exchanger for heat utilization from the gas-steam turbine for producing vjvcincaicu w nci aic ⁇ m.
  • each contact economiser is countercurrent and contains packing and a liquid phase distributor and is connected at its bottom part by means of a first pipe for heated circulating water to a pump. This pump is connected by a second pipe for heated circulating water to a heat
  • ni nii ⁇ vjuinci uiiciii. i lna nc i cXcimngci uio is. la evjii eelcu uy I c cooled circulation water pipe to the liquid phase distributor of the contact economiser, and is also connected to a pipe for passing heated liquid, mainly district heating water, as well as to a pipe for passing the heated liquid.
  • This pipe at the first, on the gas-steam mixture path, contact economiser is connected to a countercurrent heat exchanger that is connected also to a pipe for passing heated district heating water, whereas
  • the second pipe for hot circulating water of the same first contact economiser that connects the pump to the h ⁇ at exchanger block is conn ⁇ ct ⁇ d also to a pipe for removing water condensate from the water steam condensing system.
  • contact economiser is also connected to the atmosphere by means of a gas pipe.
  • the heat exchanger for the gas-steam mixture heat utilization after the gas-steam turbine, for obtaining overheated water steam is also connected by the steam pipe for overheated water steam to the first combustor.
  • the condensate removing pipe is divided into two parts, between which a regulating valve is connected in order to regulate the level of water condensate at the first, on the gas-steam mixture path, contact economiser.
  • This pipe is also connected to the liquid phase distributor of a column for desorption of carbon dioxide and oxygen, mainly constructed as a packed column.
  • This column by means of connected in series a first pipe for water condensate, a pump, and a second pipe for water condensate is connected to a heat exchanger for cooling water condensate by purified water condensate.
  • This heat exchanger by means of a third pipe for water condensate is connected to a heat exchanger for cooling water condensate by cooling water that by means of a fourth pipe for water condensate is connected to a block for chemical purification of water condensate. Furthermore, the heat exchanger for cooling water condensate by cooling water is also connected to a pipe for passing cooling water and to a pipe for removing heated cooling water. The block for chemical purification of water condensate is connected also by means of a first pipe for chemically purified water to the heat exchanger for cooling water condensate by chemically purified water.
  • first pipe for chemically purified water there arc in series connected a first pipe for removing chemically purified water from the system, a regulating valve for regulation of the liquid level in the column for desorption of carbon dioxide and oxygen, and a second pipe for removing chemically purified water from the system.
  • the heat exchanger for cooling water condensate by chemically purified water is also connected by means of the second pipe for chemically purified water to not less than one pump for increasing pressure of chemically purified water.
  • This pump is connected also by a third pipe for chemically purified water to the heat exchanger for the gas-steam mixture heat utilization after the gas-steam turbine, for producing overheated water steam.
  • This heat exchanger is connected by an water steam pipe to the column for desorption of carbon dioxide and oxygen.
  • the column is connected by means of a gas-steam mixture pipe to the gas-steam pipe after the countercurrent heat exchanger.
  • dioxide and oxygen is cooled in series and indirectly, initially by means of chemically purified water and afterwards using cold water, then it is purified chemically from the traces of ions contained, thus obtaining chemically purified water, afterwards a portion of this water, obtained from the water condensate during the condensation of water steam, obtained at the fuel burning in the combustor, is removed from the system, whereas the remaining chemically purified water is heated indirectly by water condensate, free of carbon dioxide and oxygen, and is passed for indirect heating, evaporation and overheating of the obtained water steam using the heat of the gas-steam mixture leaving the gas-steam turbine.
  • rtum T amgsa wf ms ew 4 .j.fifta , w si-snpw ms muu ut ms WMUR* pressure at a given compressor stage, without the stage before air entering the first combustor, to the inlet pressure at the given stage varies from 1.3 to 20.0, mainly from 1.6 to 5.0 as at the final stage, after which air enters the first combustor, this ratio varies from 5 to 150, mainly from 10 to 30.
  • the compressor is divided into Nl stages, from the first to Nl, as the number of stages Nl is higher or equal to the number N of stages of the gas-steam turbine.
  • the inlet of the first stage of the compressor is connected by means of a gas pipe for air under atmospheric pressure that is connected mainly to the atmosphere.
  • the inlets of all other stages are connected by pipes for cooled air to heat exchangers for intermediate air cooling, mainly by means of district heating water.
  • Each of these heat exchangers is connected by an air pipe for heated compressed air to the previous stage of the compressor.
  • the last N air pipes for heated compressed air are connected also by means of second air pipes for heated compressed air. These air pipes are connected in a reverse order to the combustors of the gas-steam turbine.
  • the second air pipes for heated compressed air, or a part of them, connecting the stages of the compressor to the corresponding combustors, before their connection to the combustors are divided into two parts.
  • Heaters are included between them that are positioned in the combined heat exchanger for the gas-steam mixture heat utilization after the gas-steam turbine.
  • the compressor consists of two separate compressors, a first and a second, mainly connected on a joint shaft with the gas-steam turbine. Each of them is divided into stages, as the number of the stages of the second compressor is N, which is equal to the number of the stages of gas-steam turbine. This number is by one more than that for the first compressor, where the stages are N-l.
  • the inlets of the first stages of the compressors are connected by means of air pipes under atmospheric pressure.
  • the outlet of each M stage of the first compressor is connected by means of an air pipe for compressed air to a corresponding intermediate heat exchanger that, on the other hand, is connected also by a pipe for cooled compressed air to M+ first stage of the second compressor.
  • the outlet of all intermediate heat exchangers is connected also by means of a second pipe for cooled compressed air to the inlet of M+ first stage of first compressor.
  • the outlets of all stages of the second compressor are connected by pipes for compressed air to the corresponding combustors of the gas-steam turbine in a reverse order. All intermediate heat exchangers are cooled mainly by district heating water.
  • each stage of the compressor is divided into two or more substages Ml, where Ml is mainly two.
  • the outlet of each substage, without the last, is connected in series by means of a pipe for hot air to a second heat exchanger for cooling, whereas it is connected to the next substage of the compressor.
  • the cooling fluid for the heat exchanger is mainly district heating water. 7
  • the installation in case when regarding the heat balance the heat of the gas-steam mixture at the inlet of the heat exchanger for the gas- steam mixture heat utilization after the gas-steam turbine is not sufficient to heat the products heated in it before their entering the combustors, the installation includes also a boiler, wherein additional fuel is burnt.
  • the pipe for transferring steam from the heat exchanger, for the gas-steam mixture heat utilization after the gas-steam turbine, to the first combustor passes through the boiler before its entering the combustor, whereas the pipe for transferring steam to the column for removing carbon dioxide and oxygen from the water condensate is also connected to the boiler.
  • a ventilator is connected to the gas pipe for removing the gas-steam mixture from the contact economiser.
  • the advantage of the invention is that it allows to increase the conversion of heat transferred to the gas-steam turbine into produced by the installation mechanical energy at a simultaneous complete utilization of the whole remaining amount of heat passed with the fuel, mainly for district heating purposes.
  • This advantage is a result of dividing the gas-steam turbine into stages with intermediate heating of the gas-steam mixture, in a manner providing its throttling down at high temperatures.
  • the way of air compressing allows the compressor to spend a relatively low amount of energy produced by the gas-steam turbine, that allows its operating at higher pressures.
  • the heat transferred for obtaining water steam is converted more completely into mechanical energy.
  • the cooling of the heat exchangers by district heating water allows them, in fact, to work as thermo-pumps. This fact together with the condensation of water obtained during the fuel burning allow to increase the amount of heat energy obtained in the installation.
  • An additional advantage of the invention is that it guarantees a reduction of the final nitric oxides concentration in the gas-steam mixture after the gas-steam turbine.
  • This advantage offers a possibility to carry out the process in all combustors, without the last one, with no air surplus, resulting in no production of nitric oxides in these combustors.
  • the amount of carbon oxide obtained in these combustors is burnt in the last combustor of the gas-steam turbine, wherein due to the lower temperature of burning nitric oxides are practically not formed.
  • An additional advantage of the invention is that in the case of its application one can increase the ratio of mechanical energy, obtained at the shaft of the electricgenerator to the heat transferred to the combustors, that is previously passed through a heat exchanger wall. This fact allows to reduce the required heat transfer surface area.
  • This advantage is related to the technological scheme of the compressor and, first of all, to its dividing into two parts, thus providing lower expenditure of mechanical energy for operating the compressor at high air temperatures at its outlet. 8
  • Fig. 1 is a principle technological scheme of the installation with a gas-steam turbine in which the compressor block consists of one compressor;
  • Fig. 2 is a principle technological scheme of the compressor block, with a gas- steam turbine, according to a variant of the invention in which the compressor is divided into two compressors;
  • Fig. 3 is a principle technological scheme of the compressor in which the stages of the first compressor are divided into substages with an intermediate air cooling between them;
  • Fig. 4 is a scheme showing the including an additional boiler to the installation.
  • the installation in accordance with Fig. 1 includes compressor 2 for air required for the burning and gas- steam turbine 6 that is divided into N stages.
  • the internal efficiency of both the gas- steam turbine and the compressors is 85 %.
  • the space at the outlet of a given stage, without the last one, is connected by an intermediate gas pipe for a gas-steam mixture to combustor 4 at the following stage of gas-steam turbine 6.
  • it is connected by means of a gas pipe for an additionally heated gas-steam mixture to its corresponding stage of gas- steam turbine 6.
  • Each combustor 4 is also connected to pipe 5, respectively 5', 5",...,5 , for fuel passage and to compressed air gas pipe 32, respectively 32', 32",.--- .32 .
  • the gas- steam turbine 6 is connected by first gas-steam mixture pipe to heat exchanger 10 for heat utilization from the gas-steam turbine for producing overheated water steam.
  • This gas pipe is connected also by second gas-steam mixture pipe to countercurrent heat exchanger 31, mainly using ribbed pipes.
  • the last one is connected by third gas-steam mixture pipe to first contact economiser at the water steam condensation system.
  • This system includes one or more, connected in series along the path of the gas-steam mixture, contact economisers 15.
  • Each contact economiser 15 is countercurrent and contains packing and a liquid phase distributor and is connected at its bottom part by means of first pipe for heated circulating water to pump 16.
  • the pump is connected by second pipe for heated circulating water to heat exchanger block 13.
  • This heat exchanger block is connected by the cooled circulation water pipe to the liquid phase distributor of contact economiser 15. It is also connected to pipe 14 for passing heated liquid, mainly district heating water, as well as to pipe 17 for passing the heated 9 liquid.
  • the pipe 17 at the first, on the gas-steam mixture path, contact economiser 15 is connected to countercurrent heat exchanger 31 that is connected to pipe 11 for passing heated district heating water.
  • the second pipe for hot circulating water of the same first contact economiser 15 that connects pump 16 to heat exchanger block 13 is connected also to pipe 33 for removing water condensate from the water steam condensing system.
  • the final, on the gas-steam mixture path, contact economiser 15 is also connected to the atmosphere by means of gas pipe 12.
  • this heat exchanger when regarding the heat balance the heat of the gas-steam mixture after the gas-steam turbine is not sufficient to heat the products passed for heating to heat exchanger 10 for gas-steam heat utilization after the gas-steam turbine, this heat exchanger is also connected by means of a pipe to boiler 35 in accordance with Fig. 4. It is also connected by means of overheated steam pipe 9 to first combustor 4'. Condensate removing pipe 33 is divided into two parts, between which regulating valve 18 is mounted to regulate the water condensate level in the first, on the gas-steam mixture path, contact economiser 15. This pipe is also connected to the liquid phase distributor of column 19 for desorption of carbon dioxide and oxygen, mainly constructed as a packed bed column.
  • Column 19 is connected by connecting, in series, first pipe for water condensate, pump 20, and second pipe for water condensate to heat exchanger 22 for cooling water condensate by chemically purified water.
  • the last one by means of a third pipe for water condensate is connected to heat exchanger 25 for cooling water condensate by cooling water.
  • Heat exchanger 25 by means of fourth pipe for water condensate is connected to block 21 for chemical purification of water condensate.
  • This heat exchanger is also connected to pipe 23 for passing cooling water and to pipe 24 for removing heated cooling water.
  • Block 21 for chemical purification of water condensate is connected also by means of first pipe for chemically purified water to heat exchanger 22 for cooling water condensate by chemically purified water.
  • first pipe for chemically purified water in series, there are connected first pipe for removing chemically purified water from the system, regulating valve 26 for regulation of the liquid level in column 19 for desorption of carbon dioxide and oxygen, and second pipe 27 for removing chemically purified water from the system.
  • Heat exchanger 22 for cooling water condensate by chemically purified water is also connected by means of second pipe for chemically purified water to not less than one pump 28 for increasing pressure of chemically purified water.
  • This pump is connected also by third pipe for chemically purified water to heat exchanger 10 for the gas-steam mixture heat utilization after gas- steam turbine 6.
  • Boiler 35 is connected by means of pipe 30 to column 19 for desorption of carbon dioxide and oxygen.
  • This column is also connected by means of gas-steam mixture pipe 29 to the gas-steam mixture pipe after countercurrent heat exchanger 31.
  • Compressor 2 is divided into Nl stages, respectively from first to Nl.
  • the first stage is connected by means of gas pipe 1 to the atmosphere.
  • Each of heat exchangers 3 is connected by means of a pipe for cooled air to the next stage of compressor 2.
  • the last N gas pipes for heated compressed air are connected also by second gas pipes for heated compressed air 32, respectively 32', 32",.--,32 N , as these gas pipes are connected in a reverse order to combustors 4 of gas-steam turbine 6.
  • All second gas pipes for heated compressed air 32 connecting the stages of compressor 2 to corresponding combustors 4, before their connecting to the combustors are divided into two parts, between which heaters are mounted that are located in heat exchanger 10 for the gas-steam mixture heat utilization after the gas-steam turbine.
  • the installation operates in the following manner. Overheated water steam at a temperature tbk is passed from boiler 35 to first combustor 4'. Natural gas is transferred to each of the combustors as its total amount is Gch4 kgmol per one kgmol water steam. The amount of natural gas is dosed in such a way that the gas-steam mixture temperature after the combustor is tt3. Compressed air, in amount corresponding to the coefficient of surplus air equal to Alfa, is passed from compressor 2 to the combustors. Before its passing to combustors 4 of gas-steam turbine 6, air is heated to temperature tbk in heaters, located in heat exchanger 10 for gas-steam mixture heat utilization after gas- steam turbine 6. The pressure in first combustor 4' is equal to P.
  • the values of the parameters according to the above mentioned denotations as well as those given below are presented in Table 1 for 19 separate numerical cases of the example.
  • the fuel transferred to first combustor 4' is burnt in air, thus additionaly overheating the water steam added to the combustor.
  • the ratio of outlet to inlet pressure for each compressor stage is one and the same for all stages and is equal to the ratio of inlet to outlet pressure for all stages of gas-steam turbine, without the last one.
  • the outlet pressure is approximately equal to the atmospheric pressure.
  • the air heated in heat exchanger 10 is distributed between all combustors 4.
  • the gas-steam mixture from heat 11 exchanger 10 enters for additional cooling countercurrent heat exchanger 31 for additional heating of previously heated district heating water.
  • the temperature of the gas-steam mixture after heat exchanger 31 is 100 °C. At this temperature it enters contact economisers 15, where at the outlet of the last, on the gas path, contact economiser it is cooled to a temperature of 50 °C. At this temperature it is thrown out to the atmosphere through gas pipe 12.
  • the cooling of the gas-steam mixture in contact economisers 15 is done during its scrubbing with circulating water transferred from the bottom of the apparatus by means of pump 16.
  • the circulating water cooled in heat exchanger blocks 13 is passed again to the liquid phase distributors of contact economisers 15. Cooling of the heat exchangers is done by district heating water that in all numerical cases of the example is at initial temperature of 45 °C. The operation takes place according to the countercurrent principle. After the last of the heat exchanger blocks 13, the circulating water is heated to 71-85 °C and is overheated to 80-90 °C in heat exchanger 31. At this temperature it is removed from the system through pipe 11 for heated district heating water.
  • the main portion of the water steam carried by the gas-steam mixture condenses in contact economisers 15, as in addition to the water steam transferred to combustor 4', additional water steam condenses in quantity equal to 0.4 kg per each kg natural gas passed to combustors 4 of the gas-steam turbine 6.
  • the condensate obtained is removed through regulating valve 18 and is passed to column 19, where it is treated by water steam, transferred through pipe 30 from boiler 35. Approximately 99.9 % of oxygen as well as approximately 99.9 % of carbon dioxide contained in the water condensate are removed in the column.
  • the remaining chemically purified water enters heat exchanger 22 for cooling water condensate, and is heated to a temperature of 95-100 °C. Then, it enters heat exchanger 10 for gas-steam mixture heat utilization after gas-steam turbine 6, for heating, evaporating, and overheating of the steam obtained. After obtaining additional quantity of heat in boiler 35, it in the form of overheated water steam is passed to first combustor 4'.
  • Air, required for fuel burning is injected from the atmosphere in the first stage of compressor 2.
  • the coefficient of surplus air, Alfa, for this case is equal for all combustors.
  • air is cooled in heat exchangers 3, respectively 3', 3",.-.,3 Nw .
  • the cooled air after all heat exchangers from 3' to 3 N1 N respectively is passed 12 to the next in order stages of the compressor.
  • the air cooled in the other heat exchangers is divided into two parts, one is passed to the next stage of the compressor, and the other, after its heating in heat exchanger 10 enters the corresponding combustor 4. Air from the last compressor stage enters totally to the corresponding combustor after heating it in heat exchanger 10.
  • Dkpd3- energy passed with the fuel to the combustor related to the sum of energy passed with the fuel to the combustors of the gas-steam mixture and the heat transferred for overheating the water steam in boiler 35.
  • compressor 2 consists of two separate compressors 2 and 2' as shown in Fig. 2.
  • the compressors are connected on a joint shaft to gas-steam turbine 6.
  • Each of them is divided into stages, as the number of the stages of the second compressor 2' is N. This number is by one more than those of the first compressor 2, where they are N-l and it is equal to the number of the stages of gas-steam turbine 6.
  • the inlets of the first stages of the compressors are connected by means of air pipes 1 and 1 ' to the atmosphere.
  • the outlet of each M stage of the first compressor 2 is connected by means of an air pipe for compressed air to a corresponding intermediate heat exchanger 3 M .
  • This exchanger is connected also by a pipe for cooled compressed air to the M+ first stage of second compressor 2'.
  • the outlet of all intermediate heat exchangers 3, respectively 3', 3",.-,3 1 is connected also by means of a second pipe for cooled compressed air to the inlet of M+ first stage of first compressor 2 if it exists.
  • the outlets of all stages of second compressor 2' are connected by pipes for compressed air 32, respectively 32', 32",.--,32 , to corresponding combustors 4 of gas-steam turbine 6 in a reverse order, as all intermediate heat exchangers 3 are cooled mainly by district heating water.
  • each stage of compressor 2 is divided into Ml substages.
  • each substage without the last, is connected by means of a pipe for hot air to heat exchanger 34, respectively 34', 34",...,34 MU for cooling.
  • This heat exchanger is connected to the next substage of compressor 2.
  • the cooling fluid for heat exchangers (34) is district heating water.
  • the installation operates in the following manner. Overheated water steam is passed from heat exchanger 10 for gas-steam mixture heat utilization after the gas-steam turbine, or from boiler 35, when the heat of gas-steam mixture is not sufficient to obtain overheated water steam, to first combustor 4'.
  • the temperature of steam is tbk.
  • Natural gas is transferred to each of the combustors as its total amount is Gch4 kgmol per one kgmol water steam. The amount of natural gas is dosed in such a way that the gas-steam mixture temperature after the combustor is tt3.
  • Compressed air in amount corresponding to the coefficient of surplus air equal to Alfa for all combustors, is passed from compressor 2' to the combustors.
  • the pressure in first combustor 4' is equal to P, and in the last one to PI.
  • Air, required for fuel burning is passed through air pipes 1 and V from the atmosphere to the first stages of compressor 2 and compressor 2'. After all stages of compressor 2, without the last, air is divided into two parts. One of them after its cooling in corresponding heat exchanger 3 is passed to the next stage of compressor 2, and the other enters the corresponding stage of compressor 2'. Air from the last stage of compressor 2, after its cooling, enters totally the last stage of compressor 2'. Thus, the air from the first stage of compressor 2 enters the second stage of compressor 2', etc. The air compressed in the separate stages of compressor 2' enters the corresponding combustors,

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  • 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

L'objectif de ce procédé, faisant intervenir l'appareillage correspondant, est d'améliorer le rendement d'une turbine à gaz et vapeur tout en réduisant les teneurs en monoxyde d'azote des gaz de combustion. Cette invention peut trouver des applications dans les domaines relevant de l'énergétique. L'une des particularités de l'invention réside dans le fait que la turbine à gaz et vapeur se divise en deux étages, pourvus, chacun, d'une chambre de combustion, l'eau surchauffée étant transférée vers le premier étage de la turbine. A la sortie de la turbine, le mélange de gaz et de vapeur traverse un échangeur de chaleur aux fins d'une utilisation de la chaleur et de l'obtention de la vapeur d'eau nécessaire. Par la suite, on utilise, de surcroît, l'eau pour chauffer l'eau de chauffage de chauffage urbain dans un échangeur de chaleur à contre-courant et dans un système d'économiseurs à contact où se condense la vapeur d'eau. Le condensat est purifié par voie chimique et, après évaporation et surchauffe de la vapeur, il est envoyé vers une première chambre de combustion. On alimente les chambres de combustion en air et ce, sous des volumes stoechiométriques, à l'exception de la dernière qui reçoit un petit volume excédentaire d'air. La température de combustion de la dernière chambre est plus basse que celle des autres. Cette procédure, qui se solde par une diminution importante de la teneur en monoxyde d'azote dans les gaz de combustion, permet d'obtenir un rendement énergétique élevé. L'appareillage est constitué d'une turbine à gaz et vapeur à plusieurs étages (6) équipée de chambres de combustions (4), d'un compresseur à air (2), d'un échangeur de chaleur combiné (10) servant au chauffage des substances pénétrant dans les chambres de combustion, d'un échangeur de chaleur (31) destiné au chauffage de l'eau de chauffage de chauffage urbain, d'économiseurs à contact (15) reliés à une pompe (16) et d'un bloc échangeur de chaleur (13) ainsi que d'une colonne servant à épurer le condensat aqueux du dioxyde de carbone et de l'oxygène, d'échangeurs de chaleur (22 et 25), d'un bloc (21) aux fins d'une purification par voie chimique du condensat aqueux et de pompes (20 et 28).
PCT/BG1998/000004 1997-02-18 1998-02-10 Procede et appareillage relatifs a une turbine a gaz et vapeur et a une utilisation de la chaleur WO1998037314A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU57430/98A AU5743098A (en) 1997-02-18 1998-02-10 Method and installation with a gas-steam turbine and heat utilization

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
BG101245 1997-02-18
BG101245A BG62982B1 (bg) 1997-02-18 1997-02-18 метод и инсталация с парогазова турбина за оползотворяване на топлината от изгарянето на газообразни и течни горива
BG102176A BG63223B1 (bg) 1998-01-12 1998-01-12 Метод и инсталация с парогазова турбина за оползотворяване на топлината на изгаряне на газообразни и течни горива
BG102176 1998-01-12

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WO1998037314A1 true WO1998037314A1 (fr) 1998-08-27

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6194788B1 (en) 1999-03-10 2001-02-27 Alpha Metals, Inc. Flip chip with integrated flux and underfill
US6727316B1 (en) 1999-06-30 2004-04-27 Basf Coatings Ag Coating material and its use for producing filler coats and stone impact protection primers
DE102013208002A1 (de) * 2013-05-02 2014-11-06 Siemens Aktiengesellschaft Thermische Wasseraufbereitung bei STIG Kraftwerkskonzepten

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2678531A (en) * 1951-02-21 1954-05-18 Chemical Foundation Inc Gas turbine process with addition of steam
GB1212511A (en) * 1967-01-23 1970-11-18 Atomic Energy Authority Uk Improvements in power generating plant
GB1284335A (en) * 1970-04-15 1972-08-09 Rolls Royce Improvements in or relating to gas turbine engines
GB2074659A (en) * 1979-09-28 1981-11-04 Vseso G Pi Steam-and-gas turbine plant
US4509324A (en) * 1983-05-09 1985-04-09 Urbach Herman B Direct open loop Rankine engine system and method of operating same

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2678531A (en) * 1951-02-21 1954-05-18 Chemical Foundation Inc Gas turbine process with addition of steam
GB1212511A (en) * 1967-01-23 1970-11-18 Atomic Energy Authority Uk Improvements in power generating plant
GB1284335A (en) * 1970-04-15 1972-08-09 Rolls Royce Improvements in or relating to gas turbine engines
GB2074659A (en) * 1979-09-28 1981-11-04 Vseso G Pi Steam-and-gas turbine plant
US4509324A (en) * 1983-05-09 1985-04-09 Urbach Herman B Direct open loop Rankine engine system and method of operating same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"ADDING A CONDENSING HEAT EXCHANGER", POWER, vol. 136, no. 3, 1 March 1992 (1992-03-01), NEW YORK US, pages 82 - 83, XP000260670 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6194788B1 (en) 1999-03-10 2001-02-27 Alpha Metals, Inc. Flip chip with integrated flux and underfill
US6727316B1 (en) 1999-06-30 2004-04-27 Basf Coatings Ag Coating material and its use for producing filler coats and stone impact protection primers
DE102013208002A1 (de) * 2013-05-02 2014-11-06 Siemens Aktiengesellschaft Thermische Wasseraufbereitung bei STIG Kraftwerkskonzepten

Also Published As

Publication number Publication date
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