BG63223B1 - Method and installation with steam-and-gas turbine for the recuperation of the heat from the combustion of gaseous and liquid fuels - Google Patents

Abstract

The invention is used in the power industry for increasing the energy efficiency of steam-gas turbines with simultaneous reduction of the concentration of nitrogen oxides in the flue gases. The turbine is divided in stages each having its combustion chamber, the water steam being fed overheated into the first stage of the turbine. After the turbine the steam-and-gas mixture enters a heat-exchanger for the heat recuperation and for producing the necessary water steam. There follows additional heat recuperation for heating the water for heating in an indirect heat-exchanger and in a system with contact economizers where the steam is condensed. The condensate is chemically cleaned and after evaporation and overheating of the steam it is fed to the first combustion chamber. In the combustion chambers, save the last one, the air is fed in stoichiometric quantity, and with a small excess in the last one. The combustion temperature in the last combustion chamber is reduced. The installation includes multistage steam-and-gas turbine (6) with combustion chambers (4) and air compressor (2), as well as a combined heat-exchanger (10) for heating the products entering the combustion chambers. Heat-exchanger (31) serves for heating the water for heating. The installation also includes contact economizers (15) with a pump (16) connected to them and a heat-exchange unit (13), as well as a column for cleaning the water condensate from CO2 and O2, heat-exchangers (22 & 25), unit for chemical cleaning of the water condensate (21) and pumps (20 & 28). 15 claims, 4 figures

Description

(54) METHOD AND INSTALLATION WITH A GAS TURBINE FOR THE RECOVERY OF THE HEAT FROM THE COMBUSTION OF GASES AND LIQUID FUELS

Technical field

The invention relates to a method for recovering heat from the combustion of gaseous and liquid fuels for the production of heat and mechanical energy and an installation for its implementation, and will find application mainly in energy, especially in the production of electricity and heat for district heating purposes.

BACKGROUND OF THE INVENTION

There is a method [1] for utilizing the heat obtained from the combustion of gaseous and liquid fuels, whereby the fuels are combusted under high pressure in the combustion chamber, with the addition of air and superheated steam. The resulting steam-gas mixture is throttled into a steam-gas turbine, then cooled indirectly, whereby its heat is used to produce superheated water vapor, which, after overheating, is fed into the combustion chamber of the turbine.

An installation [1] is known for carrying out the method, which includes a steam turbine, with an air compressor and a steam boiler for producing superheated steam, for utilizing the heat of the exhaust gas from 35 turbines. The steam boiler is connected to the combustion chamber of the gas-steam turbine for supplying to it the boiler steam produced in the boiler.

The disadvantage of this method and the installation for its realization is that a considerable part of the water of the steam vapor supplied to the combustion chamber of the gas-gas turbine is lost in the atmosphere with the flue gases at the boiler outlet, as a conversion efficiency of 45 fuel in thermal and mechanical energy are not high enough.

A second method [2] is known for using the heat obtained from the combustion of gaseous and liquid fuels using a 50 gas steam turbine. The fuel is burned under high pressure in the combustion chambers of a multi-stage gas turbine, where more pressurized air is supplied. The first combustion chamber also supplies water, mostly overheated. Both the combustion air and the water vapor are indirectly heated by the steam-gas mixture leaving the turbine. In all combustion chambers, with the exception of the first one, the steam-gas mixture throttled in the previous stage of the gas-turbine is fed for additional heating. The steam-gas mixture obtained in each of the combustion chambers is throttled into the next stages of the gas-turbine. After its last stage, the gas-gas mixture is indirectly cooled, whereby its heat is used to heat the water vapor and air entering the combustion chambers of the turbine. The flue gases are subsequently indirectly cooled by compressed air and water vapor, and then indirectly cooled by district heating water. The flue gases are then cooled directly, countercurrently, with at least one consecutive circulating water stream, whereby the water vapor condenses therein and is discharged in the form of water condensate. According to one embodiment of this method, each of the circulating water streams, heated directly, indirectly heats a water stream, preferably district heating water, in compliance with the principle of counterflow. According to another variant of the method, each of the circulating water streams heated directly, in addition to the last one during the steam-gas mixture, indirectly heats a water stream, preferably district heating water. The latter, heated directly by the circulating water stream, flushes the air entering the compressor, moistening it.

An installation [2] is known for carrying out the second method, which includes a multi-stage gas turbine connected to its shaft by a mechanical operation consumer, in particular an electric generator. It also includes air compressors and a heat exchanger to recycle the heat of the steam-gas mixture after the turbine, to heat the air and heat the steam entering the combustion chambers, as well as a heat exchanger to indirectly heat the hot water and sequentially included in the course of the steam-gas mixture. contact economizers. According to one embodiment of this installation, each of the contact economizers is connected via pipelines to a pump and a heat exchanger to heat district heating water, in accordance with the principle of counterflow. According to another embodiment of this installation, each of the contact economizers, with the exception of the latter in the course of the steam-gas mixture, is connected to pipelines to a pump and a heat exchanger for heating of district heating water, in accordance with the principle of counterflow. The last contact gas economizer in the course of the steam-gas mixture is connected by pipelines and pump to a filling column for direct humidification of the air entering the inlet of the compressor.

The disadvantage of the second method and the installation for its implementation is that it does not provide a sufficiently high degree of conversion of the heat supplied by the fuel into mechanical work.

Another disadvantage of the method is that the combustion of the fuel at high temperature is carried out at excess oxygen, which leads to an increase in the concentration of nitrogen oxides.

SUMMARY OF THE INVENTION

It is an object of the invention to provide a method which allows to increase the conversion of heat supplied to the gas-gas turbine into mechanical operation, while fully utilizing the entire amount of heat supplied by the fuel and reducing the final concentration of nitrogen oxides in the gas-gas mixture after the steam turbine.

The invention is carried out by a method of utilizing the heat of combustion of gaseous and liquid fuels in a steam turbine installation, wherein the fuel is pressurized in two or more combustion chambers of two or more stage gas turbines. In addition to air and fuel, steam is also supplied to the combustion chamber, which operates under high pressure. In the other combustion chambers, the gas-gas mixture treated in the previous stage of the gas-gas turbine is supplied for reheating. The additional gas mixture heated in a combustion chamber is fed to the next stage of the gas turbine. After the last stage of the turbine, the gas-gas mixture is indirectly cooled, preferably counter-flow, to heat the products entering one or more of the combustion chambers. The steam-gas mixture is then indirectly cooled counter-flow, preferably with preheated district heating water. The partially cooled gas-vapor mixture is then cooled sequentially, directly, as opposed to at least one circulating water stream heated by it. The vapor mixture condenses the supplied steam and after its final cooling the vapor mixture is discharged into the atmosphere. The resulting aqueous condensate was separated. A characteristic feature of the method is that the coefficient of excess air in the combustion chambers is from 1.00 to 1.5, preferably from 1.00 to 1.1. The combustion chambers of the stages of the gas turbine, with the last but not the highest, and the highest combustion chamber of the last stage, have the advantage of having the lowest coefficient of excess air equal to 1. The ratio between the initial and final pressure in the stages of the turbine, excluding the latter, ranges from 1.3 to 20, preferably from 1.6 to 5. In the latter stage of the turbine, this ratio varies from 5 to 150, preferably from 10 to 30.

According to one embodiment of the method, the gas-vapor leaving the turbine heats a chemically purified water condensate which is heated and evaporated and the resulting steam is overheated and then fed into the first combustion chamber. Chemically purified water condensate is obtained by treating the water condensate separated by direct cooling of the gas-vapor mixture as a counter-current with water vapor, which reheats it and removes oxygen and carbon dioxide dissolved therein. The resulting gas mixture is mixed with the gas mixture from the gas turbine immediately after its last indirect cooling. The carbon dioxide and oxygen liberated aqueous condensate is sequentially cooled indirectly, first with purified chemical aqueous condensate and then with cold water and chemically purified from traces of ions contained therein. Subsequently, part of the chemically purified water condensate obtained by condensation of water vapor obtained during combustion of the combustion chambers is removed from the system. The remaining purified water condensate is indirectly heated with crude chemical water condensate released from carbon dioxide and oxygen and fed for indirect heating, evaporation and overheating of the resulting water vapor, using the heat of the gas-leaving steam turbine.

According to a second embodiment of the method, the vapor leaving the turbine heats a chemically purified water condensate which is evaporated and the resulting water vapor is heated. It heats up even more compressed air. The heating products are fed into the respective combustion chambers of the gas-steam turbine.

According to a third variant of the method, when the heat balance of the gas-gas mixture is not sufficient on the heat balance, the additional heat obtained by combustion of a steam boiler is added to the steam.

According to a fourth embodiment of the method, air compression for each N-stage steam turbine is carried out in an N1-stage compressor, where N1 is greater than or equal to N. The air heated in the first N1-N-1 stages of the compressor is indirectly cooled in heat exchangers, mainly with district heating water and then returned to the next stage of the compressor. The air heated in the other stages of the compressor, without the latter, is divided into two streams. One stream is cooled, preferably by district heating water, and then fed for further compression to the next stage of the compressor. The other flow is fed into its corresponding gas chamber of the steam turbine. The air, which is compressed to the last stage of the compressor, is fed into the first combustion chamber of the steam turbine. The ratio between the outlet pressure of a given stage of the compressor, without the last one, to the inlet pressure of the given stage, ranges from 1.3 to 20, preferably from 1.6 to 5. At the last stage, after which the air enters the first fuel camera, this ratio ranges from 5 to 150, preferably from 10 to 30.

According to a fifth embodiment of the method, the compression of the air required for combustion is carried out in two multistage compressors. The number of stages of the second compressor is equal to the number of combustion chambers. The number of degrees of the first is one less. The air after each stage of the first compressor is divided into two parts, one of which is cooled with district heating water and then fed to the next stage of the first compressor. The other part is fed into the next second stage of the second compressor. The air of 10 in the first stage of the second compressor enters the atmosphere and the air from each of the stages of the second compressor enters the corresponding combustion chamber. In this case, the ratio between the outlet pressure 15 from a given stage of the first compressor to the inlet pressure therein varies from 1.3 to 20, preferably from 1.6 to 5. In the second compressor, this ratio is from 2 to 150, preferably from 10 to 30.

According to a sixth embodiment of the method, in each stage of the first compressor, the air is compressed into more than one sub-stage, with each sub-stage having a pressure ratio of inlet and outlet is substantially the same for all sub-stages. After each step, the air is cooled with district heating water.

According to a seventh embodiment of the method, each of the water streams that cools directly, sequentially, in counter-current, the indirectly cooled gas-vapor mixture, transfers its heat indirectly to another water stream, in particular district heating water. In doing so, the principle of counterclaim is respected.

According to an eighth variant of the method, the water streams, without the latter, which cool directly, sequentially, in turn, the indirectly cooled steam-gas mixture, transfer their heat indirectly to another water stream, mainly district heating water, observing the principle of counterflow. The latter water flow directly supplies the heat carried by the air supplied to the compressor by compressing it, thus moistening it. Thereafter, the circulating water stream returns to remove the heat of the gas mixture.

The method is implemented by an installation comprising a gas-steam turbine for utilizing the heat of combustion of gaseous and liquid fuels, which is divided into N stages, each with a single combustion chamber. The first combustion chamber is connected to a steam line, mostly overheated. The space of exit of a stage, with the exception of the last stage, is connected by an intermediate gas duct for a steam-gas mixture with the combustion chamber of the next stage of the gas-gas turbine, which in turn is connected with a gas-pipe for the pre-heated gas-gas mixture, with the next stage of the turbine. Each combustion chamber is also connected to a fuel supply line. It is also connected to a second pipeline for supplying compressed air, which in turn is connected to a compressor for the air required for combustion. The steam turbine is connected by a first gas pipeline for a gas mixture with the combined heat exchanger. It is connected via a second gas-gas pipeline to a counter-flow heat exchanger, preferably ribbed pipes. The latter is connected via a third gas-gas pipeline to the first contact economizer of a water vapor condensation system. This system includes one or more contact economizers, connected in series by the gas / gas mixture. Each contact economizer is countercurrent and has a filling and irrigation device and is connected at its bottom by a first pipeline for heated circulating water to the pump. It, in turn, is connected via a second pipeline for heated circulation water, with a counter-flow heat exchanger. This block is connected via the cooled circulation water pipeline to the sprinkler of the respective contact economizer. It is also connected to a pipeline for supplying heated fluid, in particular district heating water, and a pipeline for draining the heated fluid therein. The same pipeline of the first in-line steam-gas mixture contact economizer is connected to a counter-flow heat exchanger to heat district heating water. The second hot water conduit of the same first contact economizer connecting the pump and the heat exchanger unit is also connected to a conduit for water condensation from the steam condensation system. The last contact economizer on the path of the gas-gas mixture is connected to the atmosphere through a gas pipeline. A characteristic feature of the installation is that the condensate discharge line is divided into two parts, between which is included a control valve for regulating the water condensate level in the first contact steam economizer. The other part of the pipeline is connected to the irrigation device of a carbon dioxide and oxygen desorption column, preferably designed as a filling column. The latter is connected in series with a first water condensate conduit, a pump and a second water condensate conduit to a heat exchanger for cooling water condensate with chemically treated water. The latter is connected via a third water condensate pipeline to a heat exchanger for cooling the water condensate with cooling water, which through a fourth water condensate pipeline is connected to a chemical condensation unit for the water condensate. The heat exchanger for cooling the water condensate with cooling water is also connected to a pipeline for supplying cooling water and to a pipeline for draining the heated cooling water. The water condensate chemical treatment unit is connected via a first chemically treated water pipeline to the heat exchanger for cooling the water condensate with chemically treated water.

The first chemically treated water pipeline is sequentially connected to the first chemically treated water pipeline by a system, a regulating valve for regulating the level of carbon dioxide and oxygen desorption column, and a second pipeline for removing chemically treated water from the system.

The heat exchanger for cooling the water condensate with chemically treated water is connected by a second pipeline for chemically treated water with at least one pump to increase the pressure of the chemically treated water. It is also connected to a third pipeline for chemically treated water to the combined heat exchanger. The combined heat exchanger is also connected via a pipeline to the carbon dioxide and oxygen desorption column. It is connected to a gas-gas pipeline after a counter-flow heat exchanger by means of a gas-gas mixture pipeline.

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According to one variant of the installation, the compressor is divided into N1 stages (from first to N1). The entrance of the first stage is connected by an air duct to the atmosphere. Exit compressed air outlet ducts are available at each stage. To each of them without the latter are connected heat exchangers for intermediate air cooling, preferably with district heating water. Each of the heat exchangers is connected via a second cooled air duct to the next stage of the compressor. The outlet pipelines for compressed air, for the stages of the compressor with numbers from N1 minus N to N1, are connected with a third air duct. These air ducts are connected in reverse order to the combustion chambers of the steam-gas turbine, namely: the first one with the last combustion chamber, the second with the penultimate, etc., with the last pipeline connected to the first combustion chamber. The way of connecting these ducts to the ducts connected to the stages of the compressor is as follows: the first pipeline is connected to the pipeline of the Nl-N stage of the compressor, the second pipeline is to the pipeline of N1-N + 1 stage, .. .and the last N-line, with the степен stage of the compressor.

According to a second variant of the installation, the three air ducts or part of them connecting the compressor stages with the respective combustion chambers are split into two parts before connecting them to the combustion chambers. These include heaters located in the combined heat exchanger.

According to a third variant of the installation, the compressor is formed by two separate compressors, the first and the second, mainly connected to a common shaft by a gas-gas turbine. Each is divided into stages, the number of stages of the second compressor being N and equal to the number of stages of the turbine. It has one more than the first compressor with при-l. The inputs of the first stages of the compressors are connected by air ducts to the atmosphere. The output of each M-stage of the first compressor is connected by a compressed air duct to a corresponding intermediate heat exchanger, which is further connected by a cooled-compressed air pipeline to M + of the first stage of the second compressor. The output of all intermediate heat exchangers, except that of the last stage of the first compressor, is further connected, via a second pipeline for cooled air for 5 days, to the inlet of M + the first stage of the first compressor. The outputs of all stages of the second compressor are connected by conduits to the respective combustion chambers of the steam turbine 10 in reverse order. All intermediate heat exchangers are cooled primarily by district heating water.

According to a fourth installation, each stage of the compressor, respectively 15 all stages of the first compressor, for the two-compressor variant, is divided into two or more sub-stages P, preferably P 2. The output of each sub-stage, with the exception of the latter, is connected successively through a hot air duct with one second heat exchanger for cooling. In this case, the heat exchanger cooling fluid is preferably district heating water.

According to a fifth installation25, it also includes a steam boiler. In this case, the steam supply line from the combined heat exchanger to the first combustion chamber passes through the boiler before entering the chamber. The steam supply line 30 to the carbon and oxygen desorption column is also connected to the boiler.

The advantage of the invention is that it allows to increase the fraction of the heat supplied to the installation by the combustion of the fuel in mechanical work transmitted to the shaft of the generator. This advantage is related to the technological scheme of the compressor and above all to its division into two 40 parts. This reduces the energy supplied to the compressor shaft while keeping the flue gas inlet at the combustion chambers high. It is also due to the possibility for this technological scheme to operate at higher pressure at the inlet of the gas-gas turbine.

An additional advantage of the invention is that its use leads to a decrease in the concentration of nitrogen oxides. 50 The latter is due to the lack of excess air in the combustion chambers (excluding the latter) and to the operation of the last combustion chamber where the air is supplied to the excess at reduced temperature.

A second additional advantage of the invention is that, when used, the ratio between the mechanical energy of the power generator shaft and the heat supplied to the combustion chambers previously passed through a heat exchanger wall is increased. The latter leads to a decrease in the required heat exchange surface. This advantage is related to the technological scheme of the compressor, and above all, to its separation into two parts, which ensures a low mechanical energy consumption to drive the compressor with high air temperature at the outlet of the compressor.

Description of the attached figures

The invention is illustrated by the accompanying figures, of which:

Figure 1 is a schematic flow diagram of a gas turbine installation in which the compressor unit consists of a single compressor;

FIG. 2 is a schematic flow diagram of a gas turbine compressor unit according to one embodiment of the invention, wherein the compressor is divided into two compressors; FIG.

Figure 3 is a schematic diagram in which the compressor stages are divided into sub-stages, with intermediate air cooling between them;

Figure 4 is a diagram of the connection to the installation of an additional steam boiler.

Examples of carrying out the invention

Example 1. The installation presented in Figures 1 to 4 includes a compressor 2 for the combustion air required and a steam turbine 6, which is divided into N stages. The internal efficiency of both the turbine and the compressors is 85%. To each stage of the turbine 6 there is one combustion chamber 4, respectively 4'4 ".... 4 ^N .np0CTpaHCTB0T0 at the outlet of a given stage, with the exception of the last one, is connected via an intermediate gas duct for a gas mixture with the combustion chamber 4. the next stage of the steam turbine 6. It, in turn, is connected to a gas duct for the pre-heated steam-gas mixture, with the next stage of the turbine 6. Each combustion chamber 4 is also connected to a pipeline 5, respectively 5'5 "... 5 ^N for supply fuel and with 32 ', 32', ..., 32 ^K ducts to supply compressed air.

The steam turbine 6 is connected via a first gas pipeline for a gas mixture with a combined heat exchanger 10. It, in turn, is connected by a second gas pipeline for a gas mixture with a counterflow heat exchanger 31, preferably ribbed pipes. The latter is connected via a third gas-gas pipeline to the first contact economiser 15 of the water vapor condensation system. This system includes one (as shown in FIG. 1) or more connected in series by the gas-gas mixture of contact economizers 15. Each contact economiser 15 is counter-flow and has a filling and irrigation device and is connected at its bottom by means of a first heated circulation water pipeline to pump 16. The pump is in turn connected via a second heated circulating water pipeline to a counter-flow heat exchanger unit 13. The heat exchanger unit 13 is connected by means of a cooled circulation pipeline a water spray to the contact economizer 15. The heat exchange unit 13 is further connected with a duct 14 for feeding heating water and a pipe 17 for discharging the heated therein district heating water. The pipeline 17 of the first contact gas economizer 15 is connected to the counterflow heat exchanger 31. The second hot water conduit of the same first contact economizer 15, which connects the pump 16 and the heat exchanger unit 13, is also connected to a pipeline 33 for discharge. water condensate from the water vapor condensation system. The latter, via the gas-mixture mixture, the contact economizer 15 is further connected to the atmosphere via the gas pipeline 12.

According to a variant embodiment of the installation, as shown in FIG. the combined heat exchanger 10 is further connected via a pipeline to the boiler 35. It, in turn, is connected to the steam line 9 for superheated water vapor to the first combustion chamber 4 '.

The condensate discharge line 33 is divided into two parts, between which there is a regulating valve 18 for regulating the water condensate level in the first contact gas economizer 5 during the steam and gas mixture.

15. This pipeline is also connected to the irrigation device of a carbon dioxide and oxygen desorption column 19, preferably designed as a filler column. Column 19 is connected by means of successively connected first 10 condensate water pipes, a pump 20 and a second water condensate pipeline with a heat exchanger to cool water condensate with chemically treated water 22. The latter, in turn, through a third water condensate pipeline 20 connected to a heat exchanger for cooling the water condensate with cooling water 23. Through a fourth water condensate pipeline, the heat exchanger 25 is connected to a unit 21 for the chemical treatment of the water condensate 20 g. This heat exchanger is also connected to a conduit 23 for supplying cooling water and to a conduit 24 for discharging the heated cooling water. The water condensate chemical cleaning unit 21 is connected 25 more by a first chemical purified water condensate pipeline to the heat exchanger 22 for cooling the water condensate with chemically purified water condensate. The first pipeline for chemically treated water condensate 30 is sequentially connected to the first pipeline for removal of chemically purified water from the system, control valve 26 for regulating the liquid level in the column 19 for desorption of carbon dioxide and oxygen 35 and a second pipeline 27 to remove chemically purified water from the system.

The heat exchanger 22 for cooling the water condensate with chemically treated water is further connected via a second pipeline 40 for the chemically treated water with at least one pump 28 to increase the pressure of the chemically treated water. It is in turn connected to a third pipeline for chemically treated water to the combined heat exchanger 10.

The boiler 35 is connected via conduit 30 to the column 19 for desorption of carbon dioxide and oxygen. It, in turn, is connected 50 via the steam-gas pipeline 29 to the gas-gas mixture after the counter-current heat exchanger 31.

As shown in FIG. 2 according to one embodiment of the installation, the compressor 2 is formed by two separate compressors 2 and 2 'connected to a common shaft by the gas turbine 6. Each of them is divided into stages by the number of stages of the second compressor 2 'is N. It is one more than those of the first 2, with Ν-l, and is equal to the number of stages of the steam turbine 6. The inputs of the first stages of the compressors are connected by air ducts 1 and 1'. to the atmosphere. The output of each M-stage from the first compressor 2 is connected by means of a compressed air duct to a corresponding intermediate heat exchanger 3 ^m . It, in turn, is also connected by means of a cooled compressed air line to M + the first stage of the second compressor 2 '. The output of all intermediate heat exchangers 3, respectively 3 ', 3 "..... 3 ^Ν ·', without that of the last stage of the first compressor is further connected by a second pipeline for cooled compressed air with the inlet of M + the first stage of the first compressor 2.

The outputs of all stages of the second compressor 2 'are connected via conduits 32 respectively 32', 32 ', ...., 32 ^Ν to the respective combustion chambers 4 of the steam turbine 6, in reverse order. All intermediate heat exchangers 3 are cooled primarily by district heating water. Each stage of compressor 2 is divided into two or more sub-stages Ml. The output of each sub-stage, with the exception of the latter, is connected in series by a hot air duct with a heat exchanger 34, respectively 34 ', 34' ... 34 ^{M |} · 'For cooling. This pipeline, in turn, is connected to the next sub-stage of the compressor 2. The cooling fluid for the heat exchanger 34 is district heating water.

The installation works as follows. In the first combustion chamber 4 'of the steam turbine. delivers superheated steam from boiler 35, temperature tbk. More natural gas is supplied to each of the combustion chambers, totaling Gch4 kgmol per kgmol of water vapor. The quantity of natural gas is dosed so that the temperature of the gas-vapor mixture after the combustion chamber is tt3. Compressor 2 'also supplies compressed air to the combustion chambers in an amount corresponding to an excess air factor equal to Alfa. The pressure in the first combustion chamber 4 'is equal to P. Both the values of the values used above and those given below are listed in Table 1 for 23 separate variants of the example.

The fuel supplied to the first combustion chamber 4 'burns in the air supplied to it, overheating the additional steam supplied to the combustion chamber 4'. After lowering the pressure in the first stage of the turbine 6 so that the relations between the inlet and outlet pressures for each stage of the turbine 6 without the last one are equal, with the inlet pressure at the last stage being Pl and at the outlet of it of the atmospheric vapor-gas mixture enters the combustion chamber 4 of the next stage of the turbine 6. Here the fuel supplied is burned into the air by heating the supplied vapor-gas mixture. The same is repeated for each subsequent stage of turbine 6. The outlet temperature of the last stage of turbine 6 is tt41. At this temperature, the vapor mixture enters the combined heat exchanger 10 for heat recovery of the flue gases. In the heat exchanger 10 more chemically purified water enters, which is heated to reflux temperature, evaporated and heated to tbk. If the heat carried by the gas-vapor mixture is not sufficient to heat the steam to tbk, the steam is further heated in the boiler 35 from which it enters the combustion chamber 4 '. From the combined heat exchanger 10, the gas-gas mixture is supplied for additional cooling in the counter-flow heat exchanger 31 to preheat the pre-heated district heating water. After the heat exchanger 31, the temperature of the gas-vapor mixture is 100 ° C. At this temperature, the vapor mixture enters the contact economiser 15, where, at the outlet of the latter, the contact economizer 15 is cooled to 50 ° C. At this temperature it is discharged into the atmosphere through the duct 12. Cooling of the gas-vapor mixture and the contact economizers 15 is carried out by flushing it with circulating water sucked from the bottom of the apparatus by means of the pumps 16. Cooled in the heat exchange units 13, the circulating water is supplied again in the irrigation devices of the contact economizers 15. The cooling of the heat exchangers is carried out with district heating water, which in all examples has an initial temperature of 45 ° C. In doing so, the principle of counterclaim is respected. After passing through the heat exchangers, the circulating water is heated to a temperature of 71-85 ° C, with which it is brought to a temperature of 80-90 ° C in the counter-flow heat exchanger 31.

In the contact economizers 15, the main part of the steam vapor carried by the gas-gas mixture condenses and, in addition to the water vapor supplied to the combustion chamber 4 ', condenses also water vapor in an amount of 0.4 kg per kg of natural gas supplied to the combustion chambers 4. turbine 6. The resulting condensate is discharged through the control valve 18 and fed into the column 19, where it is treated with water vapor supplied through pipeline 30 from the boiler 35. About 99.9% of the oxygen contained in the water condensate is released into the column and about 99.9% of its content carbon dioxide. The latter, together with excess water vapor, which is about 1 kg per tonne of water condensate, is fed to the gas-gas mixture before entering and into the first contact economizer 15.

The carbon dioxide and oxygen liberated aqueous condensate is cooled in the heat exchangers 22 and 25 to a temperature of 30 ° C and then fed into the ion exchange unit 21. Here it is finally purified from ions and left the unit as chemically purified water. Part of it, in the amount of 0.4 kg of each kg of natural gas burned in the combustion chambers 4 of the turbine 6 is discharged from the installation through the control valve 27 and the pipeline 26,

The remaining chemically purified water enters the heat exchanger 22 for cooling the water condensate, is heated from it to a temperature of 95-100C and enters the combined heat exchanger 10 to recycle the heat of the gas-vapor mixture after the turbine 6, to heat, evaporate and heat it. the resulting steam. After receiving an additional amount of heat in the boiler 35, it, in the form of superheated steam, is fed to the first combustion chamber 4 '.

The air required to burn the fuel is sucked out of the atmosphere in the first stage of the compressor 2 and the compressor 2 '.

Of all the compressor 2 steps, except the last ones, the air is extracted and cooled in the heat exchangers 34, respectively 34 ', 34' - 34 ^{M |} . After the last step of each stage, the air is cooled in the heat exchangers 3, respectively 3 ', 3' .... 3 ^N. The cooled air after all stages of the compressor 2, without the latter is divided into two parts. One returns to the next stage of the compressor 2 and the other returns to the corresponding stage of the compressor 2 '. The last stage air flows fully into the final stage of the compressor 2 '. Thus, the air from the first stage of the compressor 2 enters the second stage of the compressor 2 ', etc. The air compressed by the individual stages of the compressor 2 'enters the respective combustion chambers, namely, from the first stage of the compressor 2' to the Nth combustion chamber, from the second stage of the compressor 2 'to the N - 1 th, ------ and from the Nth to the first combustion chamber.

The operation of the installation is characterized by the following important values, different for the different variants of the example given in Table 1:

-D pkO - mechanical efficiency of the installation, determined on the basis of the lower working heat of combustion of natural gas and all the amount of heat received by the steam in the boiler 35;

-D pkl - the ratio of energy given to compressors 2 and 2 ';

-D pk2 - the ratio of the energy delivered to the shaft of the power generator related to the energy passed through the heat exchanger surface of the combined heat exchanger 10 and the boiler 35.

It is accepted that the water from which the water vapor is produced is pre-heated to 120 ° C in the system of contact economizers 15 and in part of the combined heat exchanger 10, made of finned pipes. At the point where the condensate is heated to 120 ° C, the gas-vapor mixture in the combined heat exchanger 10 is cooled to 180 ° C.

-D pk3 - the energy supplied by the fuel in the combustion chamber, related to the sum of the energy supplied by the fuel into the combustion chambers of the turbine, and the heat supplied to heat the steam in the boiler 35.

Table 1

Example N M1 Gch4 Alfa P P1 NZ tbk tt41 Dpko Dpk1 Dpk2 Dpk3 N bar bar C ° C ° C ° % % % %

1 1 1 0.0644 1.1 15 - 1200 550 645 41.5 20.07 179 69.37 2 1 1 0.0459 1.1 15 - 1100 550 584 38,1 18,44 212 57.36 3 1 1 0.0364 1.1 15 - 1000 550 521 34.9 16.4 226 45.73 4 1 1 0.0620 1.1 20 - 1200 550 574 42.6 21.07 171 65.67 5 1 1 0.0644 1.1 50 - 1200 550 476 44,8 24.55 157 56.35 6 1 1 0.0515 1.1 80 - 1200 550 421 45,2 26.63 153 52.79 7 1 1 0.1713 1.1 150 - 1200 550 355 45,6 30.12 151 49.36 8 2 1 0.1418 1.1 150 15 1200 550 627 55,6 26,23 78 93.32 9 2 2 0.1389 1.1 150 15 1200 550 628 56.5 25.63 78,1 92,81 10 3 2 0.1571 1.1 150 15 1200 550 625 58,8 26.03 68,4 95.66 11 4 2 0.1570 1.1 150 15 1200 550 624 59,7 26,65 64,6 96.86 12 5 2 0.1713 1.1 150 15 1200 550 623 60 9 26,87 62.5 92,81 13 4 1 0,1873 1.1 200 15 1200 550 622 60 1 27.76 57.5 100,0 _ 14 3 2 0.1873 1.1 200 15 1200 550 622 60 7 27.31 58.05 99.68 15 2 1 0.1691 1.1 300 15 1200 550 618 56,0 29,22 60.45 99.48 16 4 1 0.2171 1.1 300 15 1200 550 619 58.7 28,90 48.75 100,0 17 4 2 0.2130 1.1 300 15 1200 550 619 59,9 28.36 49.10 100,0 18 6 1 0.2045 1.1 300 20 1200 550 574 60.5 30.03 49.48 98.54 19 6 2 0,2008 1.1 300 20 1200 550 574 60.5 30.03 49.85 98.51 20 6 1 0,1828 1.0 300 20 1200 550 580 61,1 27.63 53.67 96,50 21 6 1 0.2583 1,2 300 20 1200 550 577 58.08 29.42 41,00 99.05 22 6 1 0.1754 1.1 300 20 1100 550 523 57.14 28.46 57.40 92.78 23 6 2 0.2107 1.1 300 20 1200 600 579 60.12 28.15 50,50 97.09

Example 2.

The installation shown in FIG. 1 and 4, includes a compressor 2 for the combustion air and a steam turbine 6 which is divided into N stages. The internal efficiency of both the turbine and the compressors is 85%. For each stage there is one combustion chamber 4, respectively 4 ', 4 ”______ 4 ^N. The space of exit of a stage, with the exception of the last stage, is connected by an intermediate gas duct for a steam-gas mixture with the combustion chamber 4 of the next stage of the gas-gas turbine 6. It is connected with a gas-pipe for the pre-heated steam-gas mixture, with the next stage of the turbine 6. Each combustion chamber 4 is also connected to conduit 5, respectively 5 ', 5 "..... 5 ^N for supply of fuel and to conduit 32, respectively 32', 32" _______ 32 ^N for supply of compressed air.

The steam turbine 6 is connected by a first gas pipeline for a gas mixture with a combined heat exchanger 10. It, in turn, is connected by a second gas pipeline for a gas mixture with a counter-flow heat exchanger 31, preferably ribbed pipes. The latter is connected via a third gas-gas pipeline to the first contact economizer of the steam condensation system. This system includes one or more contact-economized contact gas economists 15. The contact economiser 15 is counter-flow and has a filling and irrigation device, and is connected at its bottom by a first pipeline for heated circulating water to the pump 16. The pump, in turn, is connected via a second conduit for heated circulation water, to a heat exchanger unit 13. This unit is connected via a conduit for cooled circulation water to the contact dehumidifier of the contact economizer 15. It is also connected to a pipeline 14 for supplying district heating water and a pipeline 17 to discharge the heated district heating water therein. The pipeline 17 of the first contact gas economizer 15 is connected to the counterflow heat exchanger 31. condensate from the water vapor condensation system. The latter, via the gas-mixture mixture, the contact economizer 15 is further connected to the atmosphere via the gas pipeline 12.

The combined heat exchanger 10 is also connected via a pipeline to the boiler 35. It in turn is connected to the steam line 9 for superheated water vapor to the first combustion chamber 4 '.

The condensate drainage line 33 is divided into two parts, between which there is a regulating valve 18 for regulating the water condensate level in the first contact gas economizer 15. This pipeline is also connected to the irrigation device of the column 19 for desorption. of carbon dioxide and oxygen, in particular as a filling column. The column 19 is connected in series by first connected condensate water conduit, pump 20 and a second condensate water conduit with heat exchanger 22, to cool water condensate, with chemically purified water. The latter, in turn, is connected to a heat exchanger 25 through a third water condensate pipeline for cooling the water condensate with cooling water. Through a fourth water condensate pipeline, the heat exchanger 25 is connected to a unit 21 for the chemical treatment of the water condensate. This heat exchanger is also connected to a conduit 23 for supplying cooling water and to a conduit 24 for draining the heated cooling water.

The water condensate chemical treatment unit 21 is connected by a first chemically treated water pipeline to the heat exchanger 22 for cooling the chemical condensate water condensate. The first pipeline for chemically purified water is sequentially connected to the first pipeline for removal of chemically purified water from the system, a regulating valve 26 for regulating the level of the liquid in the column 19 for desorption of carbon dioxide and oxygen, and a second pipeline 27 for removing the chemically purified water from the system.

The heat exchanger 22 for cooling the water condensate with chemically treated water is further connected via a second pipeline for chemically treated water with at least one pump 28 to increase the pressure of the chemically treated water. It is also connected to a third pipeline for chemically treated water to the combined heat exchanger 10.

The boiler 35 is connected via a conduit 30 to the column 19 for desorption of carbon dioxide and oxygen, it is connected via a conduit for gas-gas mixture 29 to the gas-gas mixture for the gas-gas mixture after the counter-flow heat exchanger 31.

Compressor 2 is divided into N1 stages, respectively, from first to N1. The first stage is connected by air duct 1 to the atmosphere, and outlet of each stage outlet ducts for compressed air are installed, with each of them without the last one being connected by heat exchangers 3, respectively 3 ', 3' .. - 3 ^{N |} · 'For intermediate air cooling, mainly with district heating water. Each of the heat exchangers 3 is connected by a second cooled air duct to the next stage of the compressor 2. In addition to the outlet lines for the compressed air, third air ducts 32 and 32 'respectively are connected to the outlet lines of the compressor 2 numbered N1 minus N to N1. 32 ".._ .. 32 ^N , with the air ducts in reverse order to the combustion chambers 4 of the steam turbine 6, namely 32 'with 4 ^N , 32" with 4 ^N ·· ______ and 32 ^N with 4 *. The way of connecting these ducts to the ducts connected to the compressor stages is such that the conduit 32 is connected to the conduit of the N1- N grade of the compressor, the conduit 32 "with the conduit of N1- N +

Grade 1, _______ and the 32 ^N pipeline with Grade Nl.

The installation works as follows. In the first combustion chamber 4 'of the steam turbine 6, superheated steam from the boiler 35 is supplied, at a temperature of tbk. Natural gas was also supplied to each of the combustion chambers 4 in a total amount of Gch4 kgmol per kgmol of water vapor. The quantity of natural gas is dosed so that the temperature of the gas-vapor mixture after the combustion chamber is «3. Compressor 2 'also supplies compressed air to the combustion chambers in an amount equal to the Alfa excess air ratio. The pressure in the first combustion chamber 4 'is equal to P.

Both the values of the values used above and the values given below are given in Table 2 for 19 separate variants of the example.

The fuel supplied to the first combustion chamber 4 'burns in the air supplied to it by overheating the additional steam supplied to the combustion chamber 4'. The pressures in the turbine 6 are varied so that the relationship between the inlet and outlet pressures for each stage of the turbine 6, without the latter, is the same. The ratio of the inlet pressure to the outlet pressure for the last stage N1-N + 1 times that of each of the other stages. The outlet pressure is about atmospheric.

After reducing the pressure in the first stage of the turbine 6, the gas mixture enters the combustion chamber 4 of the next stage. The fuel supplied here burns in the air, heating the supplied gas-gas mixture. The same is repeated for each subsequent stage of the turbine 6.

The outlet temperature of the last stage of the turbine is tt41. At this temperature, the vapor mixture enters the combined heat exchanger 10 for heat recovery of the flue gases. In the heat exchanger. 10 enters more chemically purified water koya- _d it is heated to the boiling point heretofore _d vaporized and preheated to a temperature tbk. In the same heat exchanger, up to the same temperature tbk, the air entering the combustion chambers 4 is also heated.

If the heat carried by the gas-vapor mixture is not sufficient to produce and overheat the water vapor and the heating of the heating air, the heat supplied to the boiler 35 is used. From the combined heat exchanger 10 and the boiler 35, the superheated water vapor enters the combustion chamber 4 ' , and the heated air to all combustion chambers 4. From the combined heat exchanger 10, the gas-vapor mixture is supplied for additional cooling in the counter-flow heat exchanger 31 to preheat the pre-heated district heating water. After the heat exchanger 31, the temperature of the gas-vapor mixture is 100 ° C. At this temperature, it enters the contact economiser 15, where, at the outlet of the latter, the contact economizer is cooled to a temperature of 50 ° C. At this temperature, it is discharged into the atmosphere through the duct 12.

Cooling of the gas-vapor mixture in the contact economizers 15 is performed by flushing and with the circulating water sucked from the bottom of the apparatus by means of the pumps 16. The circulating water cooled in the heat exchangers 13 is again fed into the irrigation devices of the contact economizers 15.

Cooling of the heat exchangers is carried out with district heating water, which in all examples has an initial temperature of 45 ° C. In doing so, the principle of counterclaim is respected. After passing through the heat exchanger units 13, the circulating water is heated to a temperature of 71-85 ° C, with which it is brought to a temperature of 80 90 ° C in the counter-heat exchanger 31.

In the contact economizers 15, the main part of the water vapor carried by the gas-gas mixture condenses, and in addition to the water vapor supplied to the combustion chamber 4 ', condenses a further steam equal to 0.4 kg per kg delivered to the combustion chambers 4 of the turbine 6 natural gas. The resulting condensate is discharged through the control valve 18 and fed into the column 19, where it is treated with water vapor supplied through the conduit 30 from the boiler 35. About 99.9% of the oxygen contained in the water condensate and about 99 are separated in the column. 9% of the carbon dioxide contained therein. The latter together with the excess of water vapor, which is about 1 kg per tonne of water condensate, are fed to the gas-gas mixture before entering the first contact economizer 15 during the gas-gas mixture.

The carbon dioxide and oxygen liberated aqueous condensate is cooled in the top 20 exchangers 22 and 25 to a temperature of 30 ° C, then enters the ion exchange unit 21. Here it is finally purified from ions and leaves the unit as chemically purified water.

Part of it, in the amount of 0.4 kg of each kg of natural gas burned in the combustion chambers 4 of the turbine 6 is discharged from the installation through the control valve 26 and the pipeline 27.

The remaining chemically purified water pos10 is plunged into the heat exchanger 22 to cool the water condensate, heated from it to a temperature of 95-100 ° C and fed into the combined heat exchanger 10, to recycle the heat of the gas mixture after the turbine 6, to heat 15, evaporate and overheating of the resulting steam. After receiving an additional amount of heat in the boiler 35, it, in the form of superheated steam, is fed to the first combustion chamber 4 '.

The air required to burn the fuel is sucked out of the atmosphere in the first stage of the compressor 2. After each stage, without the latter, it is cooled in the heat exchangers 3, respectively 3 ', 3' .... 3 ^N1 . The cooled air after all heat exchangers 3 'to 3 ^{NI N1} , including returns to the next stages of the compressor 2. The cooled air from the other heat exchangers is divided into two parts, one returns to the next stage of the compressor 2 and the other after its heating in the combined heat exchanger 10 enters the respective combustion chamber 4. The air from the last stage of the compressor 2 enters fully into the respective combustion chamber 4 after its heating in the combined heat exchanger 10.

Table 2

Take | pN N1 Gch4 Alpha P «3 tbk «41 Dpko Dpk1 Dpk2 Dpk3 Nr bar c ° C ' K % % % % 1 1 4 0,0708 1.1 15 1200 550 648 31,23 34.79 42.08 66.26 2 1 4 0,0710 1.1 20 1200 550 603 31.76 36,23 44.45 64.21 3 2 4 0,0974 1.1 20 1200 550 719 47.15 14,79 70.78 78.38. 4 4 4 0,1627 1.1 20 1200 550 1014 47.52 10.55 83,93 100 5 1 4 0,0710 1.1 50 1200 550 475 32.05 41.09 49.43 58.94 6 2 4 0,1048 1.1 50 1200 550 604 50.91 16.80 87,21 74.04 7 4 4 0,1929 1.1 50 1200 550 961 53.79 11,36 110,1 100 8 3 5 0,1396 1.1 60 1200 550 656 55.33 17.30 107,5 82.5 9 3 6 0,1288 1.1 60 1200 550 601 51,8 20,92 98.45 77.97 10 4 6 0,1632 1.1 60 1200 550 719 57.01 16.93 114.0 89,26

11 2 5 0,1019 1.1 80 1200 550 520 47.90 22,96 85.32 69,00 12 3 5 0,1379 1.1 80 1200 550 657 55.26 17.23 106,1 81,86 13 4 6 0,1613 1.1 80 1200 550 769 56.95 16,84 112.6 88.65 14 4 6 0,1522 1.1 80 1200 600 721 56.70 16.40 106,2 85,50 15 4 5 0,1832 1.1 80 1200 550 800 60.19 16.40 122,0 97,60 16 4 4 0,2166 1.1 150 1200 550 974 ' 55.5 12,62 129.0 100,0 17 5 5 0,2379 1.1 150 1200 550 982 52,9 13,12 128,0 100,0 18 5 7 0,1875 1.1 150 1200 550 975 58.13 16.59 121,2 95.85 19 5 6 0,2081 1.1 150 1200 550 856 58.24 14,73 126,4 100,0

Claims

Claims (15)

Claims 1. A method for utilizing the combustion heat of gaseous and liquid fuels in a steam turbine installation, wherein the fuel is pressurized in two or more combustion chambers of a two or more stage gas turbine, such as air and fuel in the combustion chamber, which operates at the highest pressure, more steam is supplied, preferably overheated, and in the other combustion chambers the gas-gas mixture treated in the preceding stage of the gas-gas turbine is supplied for further heating, further heated in a given the combustion chamber the steam-gas mixture is fed to the next stage of the gas-gas turbine, and after the last stage of the turbine, the gas-gas mixture is first cooled indirectly, preferably in the counter-flow, during which the products entering one or more of the combustion chambers are heated, then the gas-gas mixture is further cooled indirectly counter-flow, preferably with pre-heated district heating water, and then the partially cooled steam-gas mixture is cooled sequentially, directly, in counterflow with at least one compass ions, which are heated by it, condensing the supplied water vapor as well as a part of the water vapor obtained during combustion of the fuel, and after its final cooling the vapor mixture is discharged into the atmosphere and the resulting water condensate separates, characterized in that the coefficient of excess air in the combustion chambers is from 1.00 to 1.5, preferably from 1.00 to 1.1, having preferably the lowest coefficient of excess air, pa20 vein per 1 having the combustion chambers of the steam-gas stages the turbine without the latter, and the highest - the combustion chamber of the last stage, and the ratio between the initial and final pressure in the stages of the turbine, without the latter, varies from 1.3 to 20, preferably from 1.6 to 5, and at the last degree the turbine ranges from 5 to 150, preferably from 10 to 30. 2. The method according to claim 1, characterized in that the steam-gas mixture leaving the turbine heats chemically purified water condensate, which is heated and evaporated, and the resulting steam is heated, and then enters the first combustion chamber, such as the chemically purified water condensate is obtained by treating the water condensate, separated by direct cooling of the gas-vapor mixture, as a counter-current with water vapor, which reheats it and removes oxygen and carbon dioxide dissolved therein, and the resulting vapor-gas cm. is mixed with the gas-gas mixture of the gas-gas turbine, preferably immediately after its last indirect cooling, and the carbon dioxide and oxygen-liberated water condensate is subsequently cooled indirectly, first by means of chemically purified water and then by cold water, chemically purified from those present. it is monitored by ions to produce chemically purified water, after which part of this water obtained from water condensate by condensation of water vapor obtained by combustion of fuel it in the combustion chambers is withdrawn from the system, and the remaining chemically purified water is indirectly heated with crude chemical aqueous condensate, released from carbon dioxide and oxygen and fed to indirectly heat, evaporate and overheat the resulting water vapor, using the heat of outlet gas turbine vapor mixture. Method according to claim 1, characterized in that the steam-gas mixture leaving the turbine heats chemically purified water condensate, which is evaporated and the resulting water vapor is heated, as well as heated compressed air, the heating products being fed into the respective combustion chambers of the gas-steam turbine. Method according to claims 2 and 3, characterized in that when the heat of the steam mixture is insufficient on the heat balance, the additional steam obtained by combustion of the steam boiler is added to the steam. A method according to claim 1-4, characterized in that the compression of the air for each N-stage steam turbine is carried out in an N1-stage compressor, where N1 is greater than or equal to N, such as that heated in the first N1-N- 1 stages of the compressor the air is cooled in the heat exchangers indirectly, preferably with district heating water, after which it returns to the next stage of the compressor, and the air heated to the other stages of the compressor, without the latter being divided into two streams, one stream being cooled, preferably with district heating and the water is then fed for further compression to the next stage of the compressor, and the other stream is fed to its corresponding pressure chamber of the steam turbine, the air being compressed at the last stage of the compressor is supplied to the first combustion chamber of the gas turbine, and the ratio between the pressure at the outlet of a given stage of the compressor, without the latter, to the inlet pressure of the given stage, ranges from 1.3 to 20, preferably from 1.6 to 5, and at the last stage, after which the air enters the first combustion chamber, this ratio varies from 5 to 150, preferably from 10 to 30. Method according to claim 1-4, characterized in that the compression of the combustion air is carried out in two compressors, preferably multistage, with the number of stages of the second compressor being equal to the number of combustion chambers and the number of combustion chambers. the degrees of the first is one less, the air after each stage of the first compressor is divided into two parts, one of which is cooled, mainly by district heating water, and then fed to the next stage of the first compressor, and the other is fed to the next by number of the second compressor, whereby the air in the first stage of the second compressor enters the atmosphere and the air of all stages of the second compressor enters the corresponding combustion chamber, the ratio between the pressure of an outlet from a given stage of the first compressor and the inlet pressure it varies from 1.3 to 20, preferably from 1.6 to 5, and for the second compressor this ratio is from 5 to 150, preferably from 10 to 30. 7. A method according to claim 6, characterized in that at each stage of the compressors, in which the air is supplied wholly or partially to the next stage of the same compressor, the air is compressed into more than one sub-stage, and at each sub-stage the pressure ratio the inlet and outlet is preferably the same, and after each step the air is cooled, preferably by district heating water. A method according to claims 1 to 7, characterized in that each of the water streams, which directly, consecutively, counter-cooled, the pre-cooled steam-gas mixture, indirectly cools their heat indirectly to another water stream, preferably district heating water, at which respects the principle of counterflow. A method according to claims 1 to 7, characterized in that the water streams, excluding the latter, which cool directly, sequentially, in turn, the indirectly cooled steam-gas mixture, indirectly transfer their heat to another water stream, preferably district heating water. , which respects the principle of countercurrent, with the last water flow giving in direct counterflow the heat carried by the air entering the compressor into the compressor, while moistening it, and then the circulating water flowing through the compressor. October returns for withdrawing heat of the gas mixture. 10. Installation with a steam-gas turbine for recovering the heat of combustion of gaseous and liquid fuels, including a compressor (2) for the combustion air and a steam-gas turbine (6) divided into N stages, each with one fuel chamber (4), respectively (4 * 4 ”..... 4 ^N ), and the space of the exit of a stage with the exception of the last one is connected via an intermediate gas duct for a steam-gas mixture with the combustion chamber (4) of the next stage of the steam turbine (6), which in turn is connected to a gas duct for the upstream threshold mixture, with the next stage of the turbine (6), and each combustion chamber (4) is also connected to a pipeline (5), respectively (5 ', 5 ”..... 5 ^N ) for fuel supply and a pipeline (32), respectively (32 ', 32 ”.._. 32 ^N ) for supplying compressed air, and the steam turbine (6) is connected by a first gas pipeline for a gas mixture with a combined heat exchanger (10), which in turn is connected via a second gas-gas pipeline to a counter-flow heat exchanger (31), preferably ribbed tubes, and the latter connected by a third gas-gas mixture to the first a contact economizer (15) of a water vapor condensation system comprising one or more gas-contact mixture contact series (15) connected in series by the path, wherein each contact economizer (15) is counter-current and has a filling and irrigation device and is connected at the bottom, through a first conduit for heated circulating water, to a pump (16) which in turn is connected by a second conduit for heated circulating water to a heat exchanger block (13), preferably a counter-flow, in that case the heat exchanger block (13) is connected by means of a pipeline for cooled circulation water to the contact economizer of the contact economizer (15), and is further connected to a pipeline (14) for supplying heated fluid, preferably district heating water, and to a pipeline (17) for draining the heated into it fluid, such pipeline (17) of the first contact gas economizer (15) being connected to the counterflow heat exchanger (31) and the second hot water pipeline of the same first economizer (15) connecting the pump (16) and the heat exchanger block (13 ) is also connected to a conduit (33) for removal of water condensate from the condensation system of the water vapor, and the latter, via the steam-gas mixture, the contact economizer (15) is also connected to the atmosphere by means of a gas pipeline (12), such as the combined heat exchanger ( 10) is further connected via a steam line (9) for the superheated water vapor to the first combustion chamber (4 '), characterized in that the condensate discharge line (33) is divided into two parts, between which is a regulating valve ( 18) for regulating the level of water condensate in the first contact gas economizer (15) and further connected to the irrigation device of a carbon dioxide and oxygen desorption column (19), preferably configured as a filler column, which is pumped via a series of first connected condensate water pipelines (20). ) and a second water condensate pipeline is connected to a heat exchanger (22) for cooling water condensate with purified water condensate, and the latter, through a third water condensate pipeline, is connected to a heat exchanger for cooling the water horse an enzyme with cooling water (25) which is connected to a chemical condensation unit of the aqueous condensate (21) by means of a fourth water condensate pipeline, wherein the heat exchanger for cooling the water condensate with cooling water (25) is further connected to a supply pipeline of cooling water (23) and a pipeline to drain the heated cooling water (24), and the water condensate chemical treatment unit (21) is further connected by means of a first chemically purified water pipeline to the heat exchanger to cool the water condensate with chemically purified water (22), with the first pipeline for chemically treated water being sequentially connected to the first pipeline for the removal of chemically treated water from the control valve system (26) for regulating the level of liquid in the desorption column for carbon dioxide and oxygen (19) and a second a pipeline for the removal of chemically treated water from the system (27), and the heat exchanger for cooling the water condensate with the chemically treated water (22) is connected by a second pipeline for chemically treated water with at least one booster pump. not the pressure of the chemically treated water (28), but in turn it is connected via a third pipeline for chemically treated water to the combined heat exchanger (10), whereby the combined heat exchanger (10) is connected by a conduit (30) to the column for desorption of carbon dioxide and oxygen (19), which in turn is connected to the gas-gas pipeline after the counter-flow heat exchanger (31) via a gas-gas mixture pipeline (29). Installation according to claim 10, characterized in that the compressor (2) is divided into N1 stages, the inlet of the first stage is connected by means of an air duct (1) to the atmosphere, and at the outlet of each stage there are outlet ducts for compressed air with heat exchangers (3), respectively (3 ', 3 ”.._ .. 3 ^N11 ) being connected to each of them without the latter for intermediate cooling of the air, mainly by district heating water, and each of the heat exchangers (3) is connected through a second cooled air duct with the next stage of com press (2), with third air ducts (32), respectively (32 ', 32 ”..... 32 for the stages of the compressor (2) with the numbers N1 minus N to N1. 32 ^N ), with these air ducts connected in reverse order to the combustion chambers (4) of the steam-gas turbine (6), namely (32 ') with (4 ^N ), (32 ”) with (4 ^N1 ) ..... and (32 ^N) to (4 '), and the way of connecting these air ducts to the air ducts associated with the levels of the compressor, is as follows: the pipe 32' is connected to the outlet pipe for compressed air of Nl-N-th power of the com spring, the duct 32 "with the corresponding conduit of N1-N + 1-th degree, ....... a conduit 32 ^N with a corresponding conduit of the Nl-th degree. Installation according to claim 11, characterized in that the third air ducts (32) respectively (32 ', ______ 32 ^N ) or a part thereof, connecting the stages of the compressor (2) to the respective combustion chambers (4), before connecting them to the combustion chambers (4) are divided into two parts, including heaters located in the combined heat exchanger (10). Installation according to claim 10, characterized in that the compressor (2) is formed by two separate compressors (2) and (2 '), preferably connected to a common shaft by the gas turbine (6), each of which is separated in degrees and the number of degrees of the second compressor (2 ') is N, with one more than those of the first (2), where are Ν-l and equal to the number of stages of the gas turbine (6), such as the inputs of the first stages of the compressors are connected by means of air ducts (1) and (D) to the atmosphere, and the output of each Mth stage of the first compressor (2) is connected by means of a compressed air duct to a corresponding intermediate heat exchanger (3 ^m ), which in turn is connected by a cooled compressed air conduit to M + the first stage of the second compressor (2 '), leaving the output of all intermediate heat exchangers (3 ), respectively (3 ', 3 ”_______ 3 ^N ·'), without that of the last stage of the first compressor (2) is connected further by a second pipeline for cooled compressed air to the inlet of M + the first stage of the first compressor (2) , and the outputs of all stages of the second compressor (2 ') are connected via pipelines (32) respectively (32 ', 32 "_______ 32 ^N ) to the respective combustion chambers (4) of the steam-gas turbine (6), in the reverse order, and all the intermediate heat exchangers (3) are cooled primarily by district heating water. Installation according to claims 11 and 13, characterized in that each stage of the compressor (2) is divided into two or more sub-stages P, preferably two, and the output of each sub-stage, with the exception of the latter, is connected in series by an air duct for hot air with one heat exchanger for cooling (34), which in turn is connected to the next sub-stage of the compressor (2), whereby the cooling fluid for all heat exchangers (34) is preferably district heating water. Installation according to claim 10, characterized in that it further comprises a steam boiler (35), the duct (9) for supplying steam from the heat exchanger (10) to the combustion chamber (4 ') passes through the boiler (35) before entering the combustion chamber (4 ') and the steam supply line (30) to the column (19) is also connected to the boiler (35).