JP2012225228A - Supercritical pressure co2 gas turbine composite power generation system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power generation system whose power generation efficiency is higher than that of a conventional power generation system or a simple supercritical pressure COgas turbine cycle in the power generation region of 25,000 kWe class, and to further provide a thermoelectric variable power generation system in addition thereto.SOLUTION: In a composite power generation system of the supercritical pressure COgas turbine and a gas turbine, a flue COheating unit 21 for recovering the heat of exhaust gas and a steam generator 3 are arranged within an exhaust gas duct 17 of a conventional gas turbine 1, the flue COheating unit 21 is used as a COheater of a supercritical pressure COgas turbine cycle 2 (in some case, together with a cooling wall pipe 19 provided in a combustor), and steam generated in the steam generator 3 is introduced within the conventional gas turbine, and supplies the heat as demanded.

Description

The present invention relates to a turbine using supercritical carbon dioxide (CO ₂ ) as a working medium (hereinafter referred to as “supercritical CO ₂ gas turbine”) and a conventional gas turbine using LNG or the like as fuel (hereinafter referred to as “ This is related to a combined power generation system with a conventional gas turbine.

As described in Non-Patent Document 1 and Non-Patent Document 2, development of a supercritical pressure CO ₂ gas turbine cycle is underway. The conceptual diagram of the supercritical pressure CO ₂ gas turbine cycle is shown in FIG.

As shown in FIG. 8, the supercritical pressure CO ₂ gas turbine cycle is a conventional gas engine, a conventional gas turbine, or a conventional power generation region of 1,000 kWe to 100,000 kWe, particularly a power generation region of 25,000 kWe or less. High power generation efficiency can be obtained compared to the steam turbine cycle. Also, unlike the conventional gas turbine and gas engine, the supercritical pressure CO ₂ gas turbine is a completely closed cycle, and the heat is supplied to the cycle through the heat exchanger wall. Since there is an advantage that so-called dirty gas including particulate matter such as biomass combustion gas and blast furnace gas can be used as a heat source, it is expected to spread in the power generation area in the future.

Applicant has such attention than before to the future has been developing, the supercritical CO ₂ gas turbines and described in Non-Patent Document 3 supercritical CO ₂ gas turbine cycle, JP The CO ₂ heater described in 1 is one end of its development.

As described above, the supercritical pressure CO ₂ gas turbine cycle is more efficient than the conventional power generation system, but further higher efficiency is desired.

  On the other hand, for power generation systems in the power generation region of 25,000 kWe class or less, steam is supplied to the outside of the power generation system at the same time as the power, and the ratio of power to heat output according to the demand, that is, the thermoelectric ratio is changed. There is a demand for a thermoelectric variable type facility that can be used.

  In a conventional gas turbine plant, there is a steam injection cycle that recovers exhaust heat of the gas turbine to generate steam, injects the steam into the gas turbine, increases power generation output, and improves thermal efficiency. . Among them, what uses superheated steam as injection steam in order to avoid entrainment of drain in the injection steam into the gas turbine is called a Cheng cycle and is put into practical use.

  In this steam injection cycle, a variable thermoelectric type in which part or all of the generated steam is supplied to the outside of the power generation system as necessary has been put into practical use. A conceptual diagram of the steam injection cycle is shown in Case 4 of FIG.

  However, the conventional combined power generation system of the conventional gas turbine and the steam turbine (case 1 in FIG. 9) has improved the power generation efficiency due to the high inlet temperature of the gas turbine and the improvement of the steam conditions on the steam turbine side. For this reason, the efficiency and thus the economic advantage of the steam injection cycle is waning. In the steam injection cycle, power generation is performed only by the gas turbine because of the essence of the system, and therefore the power generation efficiency depends only on the gas turbine efficiency. Since it is discharged, white smoke is conspicuous, and these economic and landscape problems prevent the spread of power generation.

  There is a demand for a power generation facility that has higher power generation efficiency than that of such a conventional technique and can be used as a thermoelectric variable type facility as necessary.

Japanese Patent Application No. 2009-279495.

"Research and development of gas turbine using supercritical pressure CO2 as working medium" Motoaki Utamura et al., Edited by Energy Research Institute of Energy, "Kiho Energy Engineering" Vol. 32, No. 1, April 20, 2009 Issued daily. "Supercritical pressure CO2 gas turbine power generation system efficiency characteristics evaluation" presented by Hiroshi Hasuike et al., October 20-21, 2010, at the 38th Annual Gas Turbine Society Annual Meeting held in Tokushima City. “Development of Supercritical Pressure CO2 Closed Cycle Gas Turbine” by Motoaki Utamura et al., October 21 and 22, 2009, presented at the 37th Japan Gas Turbine Society Regular Lecture Meeting held in Yamaguchi City.

The problem to be solved by the present invention is to provide a power generation system having a power generation efficiency higher than that of a conventional power generation system or a simple supercritical pressure CO ₂ gas turbine cycle in a power generation region of 25,000 kWe class or less, In addition, it is to provide a thermoelectric variable power generation system.

In the present invention, a flue CO ₂ heating unit and a steam generator for recovering heat of exhaust gas are arranged in order from the upstream side in an exhaust gas duct of a gas turbine using LNG or the like as fuel, and the flue CO ₂ heating is performed. A combination of a CO ₂ gas turbine and a conventional gas turbine in which the section is used as a CO ₂ heater for a supercritical CO ₂ gas turbine cycle and the steam generated by the steam generator is injected into the conventional gas turbine It is a power generation system.

  A conceptual diagram of the combined power generation system of the present invention is shown in case 3 of FIG. Conventional gas turbines that use LNG as a fuel rotate the turbine with high-temperature and high-pressure gas generated by burning fuel with a combustor, rotate the generator to send power to the outside, and rotate their compressors. Pressurize the combustion air.

A flue CO ₂ heating section and a steam generator are provided in an exhaust gas duct that guides the exhaust gas of the turbine of this conventional gas turbine to a chimney. Both of them improve the efficiency of the system by recovering the heat of the exhaust gas from the turbine and lowering the temperature of the exhaust gas discharged from the chimney.

The flue CO ₂ heating portion corresponds to CO ₂ heater supercritical CO ₂ gas turbine cycle shown in FIG. 7, the CO ₂ exiting the regenerative heat exchanger predetermined supercritical pressure CO ₂ gas turbine Heat to inlet temperature. On the other hand, the steam generated by the steam generator is injected into the gas turbine and contributes to power generation.

With this configuration, the exhaust heat of the conventional gas turbine is effectively recovered, and a part of the exhaust heat is effectively used as a heating source for the supercritical pressure CO ₂ gas turbine cycle. It is injected into a gas turbine to increase power generation output and improve thermal efficiency.

Based on a 10,000 kWe class existing gas turbine, the output and power generation efficiency were compared with other power generation systems. Compared to each other, as shown in the conceptual diagram of FIG. 9, in addition to the combined power generation system of the present invention (case 3), the combined power generation system of the conventional gas turbine and the steam turbine (case 1), supercritical pressure CO A combined power generation system of _two gas turbines and a conventional gas turbine (without a steam generator) (case 2), and a steam injection cycle (case 4).

  Table 1 summarizes the results of the trial calculation.

  As a result, the output of each power generation system is as shown in FIG. 10, and the power generation efficiency is as shown in FIG. When a gas turbine of the same scale is used, the combined power generation system (Case 3) of the present invention is slightly smaller in output than the combined power generation system of the conventional gas turbine and the steam turbine (Case 1) under trial calculation conditions. However, in the efficiency (low heating value / power generation end standard), Case 1 was 40.4%, significantly exceeding 47.3%, and the efficiency improvement effect was remarkable.

FIG. 12 shows the result of a similar trial calculation with the power generation scale changed. Here, in addition to the combined power generation system of the present invention (Case 3) and the combined power generation system of the conventional gas turbine and the steam turbine (Case 1), the superheater that heats CO ₂ in the combustion furnace without combining with the conventional gas turbine. Comparison was made with a critical pressure CO ₂ gas turbine power generation system and a conventional thermal power generation system consisting of a boiler and a steam turbine.

  As is apparent from the figure, the combined power generation system of the present invention has higher efficiency (low heating value / power generation end reference) than other power generation systems in a wide range of power generation scale. In particular, the effect is outstanding in the power generation area below 25,000 kWe class.

  Further, the present invention is the combined power generation system according to claim 1, wherein a part of or all of the steam generated by the steam generator is used as a heat source to send out the combined power generation system. It is a power generation system. The conceptual diagram is shown in FIG.

  The steam injection cycle, which recovers exhaust heat from the gas turbine and generates steam, and injects the steam into the gas turbine to increase the power generation output and improve the thermal efficiency, is an aeroderivative gas turbine or variable stator blade In many cases, an industrial gas turbine having a power generation output of 6,000 kWe to 27,000 kWe has already been put into practical use. As described above, the amount of power generated when using the same size gas turbine is not large compared to other power generation methods, but considerably higher power generation efficiency is obtained, and furthermore, the equipment unit price is cheaper because there are few attached equipment. It is also characterized by space saving.

  A gas turbine combustor has a double structure of an outer cylinder and an inner cylinder, and fuel is burned in the inner cylinder, and the temperature of the inner cylinder which becomes high due to the combustion can be lowered between the outer cylinder and the inner cylinder. A cooling fluid (usually combustion air) is passed through an annular channel.

  In the steam injection cycle, the steam generated by the heat recovery of the exhaust heat of the gas turbine is injected into the gas turbine in a form of being mixed into the air flowing through the annular flow path. The amount of steam that can be injected is about 0 to 0.3 in terms of the thermoelectric ratio shown in Equation 1 below, that is, the steam corresponding to 30% of the generated electric energy from the operating state in which all the steam generated by heat recovery is injected into the gas turbine. It is possible to cope with the operating state in which air is supplied to the outside of the cycle.

Formula 1
Thermoelectric ratio = calorie of steam sent out of cycle / generated energy

  Based on a 10,000 kWe class existing gas turbine, we compared the power generation efficiency with other cogeneration systems. The comparison is as shown in FIG. 14 in which each conceptual diagram is a combined power generation system of the present invention, in which there is one steam generator placed in the flue, and the pressure of the generated steam is one pressure. That is, when the steam generator has a single pressure (case 6), there are a plurality of steam generators (two in this case) placed in the flue, and the generated steam has a plurality of pressures, that is, the steam generator. Is a double pressure (case 7), a conventional combined power generation system of a gas turbine and a steam turbine (case 5), and a steam injection cycle (case 8).

  Table 2 summarizes the results of the trial calculation.

  As a result, when the power generation amount of each power generation system is maximized (hereinafter referred to as “power generation MAX”), the efficiency (low heating value / power generation end standard) is shown in FIG. The efficiency (referred to as “heat MAX”) (low heating value) is as shown in FIG.

  When a gas turbine of the same scale is used, the combined power generation system of the present invention, particularly when the steam generator has multiple pressures, the efficiency of power generation MAX (low heating value / power generation end standard) is 47.4%, which is another system. It is extremely efficient compared to

  Although the efficiency (low heating value) of the thermal power generation system of the combined power generation system of the present invention is lower than those of Case 5 and Case 8, as seen in many cases, the power generation is the main component, and the heat supply is the subordinate position. In a certain plant, it is very beneficial nowadays that there is a concern about power shortage that an extremely high efficiency can be obtained in an operation state with a large amount of power generation, that is, power generation MAX or a state close thereto.

Furthermore, the present invention provides a combined cycle power generation system of claim 1, the CO ₂ that is heated by the flue CO ₂ heater, led to the cooling wall tube of the combustor of the conventional gas turbine, therein In the combined power generation system, after being reheated at, the mixture is sent to the supercritical CO ₂ gas turbine.

FIG. 17 shows a conceptual diagram of the combined power generation system of the present invention. By heating the CO ₂ sent to the supercritical CO ₂ gas turbine in two stages, the flue CO ₂ heater and the cooling wall pipe in the combustor, the heat transfer area of the flue CO ₂ heater is reduced. As a result, the installation space can be saved, and the pressure loss of CO _{2 in} the heating stage is reduced, so that the power generation efficiency of the supercritical pressure CO ₂ gas turbine cycle and thus the power generation efficiency of the combined power generation cycle are further improved.

  Further, the present invention is the combined power generation system according to claim 3, wherein a part or all of the steam generated by the steam generator is sent out of the combined power generation system as a heat source. It is a power generation system.

The CO ₂ that is heated by the flue CO ₂ heater, lead to combustor of a conventional gas turbine, after heating at a cooling wall tube therein, high power generation efficiency than was obtained with a complex system to be sent to the CO ₂ gas turbine The above-described thermoelectric variable effect can be utilized while maintaining the above.

By adopting the composite power system of the present invention, a power generation system having a power generation efficiency higher than that of a conventional power generation system or a simple supercritical CO ₂ gas turbine cycle in a power generation region of 25,000 kWe or less, In addition, a thermoelectric variable type power generation system can be provided.

It is explanatory drawing of Example 1 and Example 2 of the combined power generation system of this invention. 3 is a temperature diagram of Example 1. FIG. 6 is a temperature diagram of Example 2. FIG. 10 is an explanatory diagram of Example 3. FIG. It is sectional drawing of the combustor of the gas turbine of Example 3. FIG. 6 is a temperature diagram of Example 3. FIG. It is an illustration of supercritical CO ₂ gas turbine cycle. It is a comparison diagram of the power generation efficiency of the supercritical CO ₂ gas turbine cycles and other power generation systems. It is the conceptual diagram of the electric power generation system which compared the output and efficiency (low heating value and electric power generation end standard). It is an output comparison diagram. It is a comparison figure of efficiency (low heating value, power generation end standard). It is a comparison figure of the efficiency (low heating value and power generation end standard) when the power generation scale is changed. It is a conceptual diagram of the thermoelectric variable type combined power generation system of this invention. It is a conceptual diagram of the cogeneration type power generation system which compared the power generation efficiency. It is a comparison figure of efficiency of power generation MAX (low heating value / power generation end standard). It is a comparison figure of efficiency (low calorific value) of heat MAX. The CO ₂ of the present invention is an explanatory diagram of a combined cycle power generation system for heating in combustor flue CO ₂ heater and conventional gas turbines.

  Embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to such an embodiment, and it goes without saying that various modifications may be made to the specific structure within the scope of the present invention.

FIG. 1 is an explanatory diagram showing a configuration of a supercritical pressure CO ₂ gas turbine combined power generation system according to a first embodiment of the present invention. The line and valve indicated by the alternate long and short dash line in the figure are added in the second embodiment and do not exist in the first embodiment. FIG. 2 shows a temperature diagram calculated for Example 1.

  The conventional gas turbine 1 includes a compressor 12 that compresses combustion air 11, a combustor 14 that combusts LNG or the like 13 that is fuel using the compressed combustion air, and the energy of the high-temperature and high-pressure gas generated therein is rotated. A turbine 15 to be changed and a generator 16 that rotates by the turbine to generate electric power, and the exhaust gas exiting the turbine 15 is guided to a chimney 18 through a flue 17.

A flue CO ₂ heater 21 that heats CO ₂ used in the supercritical pressure CO ₂ gas turbine cycle 2 is provided in a portion close to the turbine 15 in the flue 17, that is, a portion where the temperature of the gas turbine exhaust gas is highest. Provided. A steam generator 3 for generating steam to be injected into the gas turbine 1 is provided on the downstream side thereof, that is, in a portion where the temperature of the gas turbine exhaust gas is lowered.

  In the first embodiment, a two-stage multi-pressure type is adopted, and the steam generator 3 includes a high-pressure steam generator 31, a low-pressure steam generator 32, a economizer 33 for preheating the feed water to be sent to them, and its feed water. It consists of a water supply pump 34 that feeds in water. As shown in FIG. 2, the high-pressure steam generator 31 having the highest saturation temperature is arranged in a higher exhaust gas temperature region, the low-pressure steam generator 32 having a lower saturation temperature on the downstream side, and finally the lower temperature below the saturation temperature. By providing the economizer 33, the exhaust gas temperature reaching the chimney 18 can be lowered to an appropriate value of 165 ° C. while avoiding pinch points. Further, since a sufficient temperature difference necessary for heat exchange can be taken, a compact configuration can be taken as a heat exchanger.

  In this embodiment, feed water is fed from one feed pump 34 to two steam generators 31 and 32 having different pressures, branches after passing through one economizer 33, and feeds feed water to the respective steam generators. The distribution regulating valves 35 and 36 are provided, but it is natural that the steam generator and the water supply pump are individually provided in each steam generator, the line is separated, and the regulating valve is not provided. Conceivable.

  The steams 36 and 37 generated by the two steam generators 31 and 32 are all in the first embodiment because there is no heat supply line 41 or 42 indicated by an alternate long and short dash line and regulating valves 38, 39, 43 and 44 therefor. Is injected into the gas turbine 1 and used to increase the generated power and improve the power generation efficiency.

On the other hand, details of the supercritical pressure CO ₂ gas turbine cycle 2 are not shown in FIG. 1, but have the configuration shown in FIG. 7, and the role of the CO ₂ heater in FIG. 7 is the flue CO _{2 in} FIG. The heater is responsible. As described above, the supercritical pressure CO ₂ gas turbine cycle is a conventional gas engine, a conventional gas turbine, or a conventional steam turbine in a power generation region of 1,000 kWe to 100,000 kWe, particularly in a power generation region of 25,000 kWe or less. High power generation efficiency can be obtained compared to the cycle.

In the trial calculation shown in FIG. 2, the combustion gas generated in the combustor 14 is sent to the turbine 15 at 1,250 ° C. and generates 12,547 kWe. The exhaust gas temperature at the outlet of the turbine 15 is 544 ° C., and heat is exchanged with the flue CO ₂ heater 21, the two steam generators 31 and 32, and the economizer 33, and the exhaust gas is discharged from the chimney at 165 ° C.

  3,170 kg / h of steam is sent from the high-pressure steam generator 31, and 11,300 kg / h of steam is sent from the low-pressure steam generator 32 to the gas turbine 1.

  In FIG. 1, a second embodiment is obtained by adding lines 41 and 42 indicated by a one-dot chain line and regulating valves 38, 39, 43, and 44 to the first embodiment. FIG. 3 shows one temperature diagram calculated for Example 2. FIG.

  In order to supply heat, heat supply lines 41 and 42 for supplying a part or all of the steam 36 and 37 generated by the steam generator 3 in a branched manner are provided. In order to deliver steam to meet the demand for heat supply and to meet the demand for power, the steam 36, 37 is appropriately distributed for heat supply and for injection into the gas turbine. For this purpose, regulating valves 38, 39, 43, 44 are provided.

FIG. 3 is a trial calculation in the case where the whole amount of the generated steams 36 and 37 is supplied with heat in the second embodiment. The combustion gas generated in the combustor 14 is sent to the turbine 15 at 1,250 ° C., and generates 12,415 kWe. The exhaust gas temperature at the outlet of the turbine 15 is 539 ° C., and heat is exchanged with the flue CO ₂ heater 21, the two steam generators 31 and 32, and the economizer 33, and the exhaust gas is discharged from the chimney at 165 ° C.

  Steam supplied from the high-pressure steam generator 31 to the gas turbine 1 is supplied with 3,270 kg / h of steam and from the low-pressure steam generator 32 is supplied with 11,500 kg / h of steam to the outside of the power generation system for heat supply. The amount is 0 kg / h.

FIG. 4 is an explanatory diagram showing the configuration of a third embodiment of the supercritical pressure CO ₂ gas turbine combined power generation system of the present invention. FIG. 5 is a cross-sectional view of an example of a gas turbine combustor according to the third embodiment. Further, FIG. 6 shows one temperature diagram calculated for Example 3. FIG.

  In order to facilitate understanding, elements having the same functions as those in the first embodiment or the second embodiment and having similar configurations are assigned the same numbers.

The exhaust gas exiting the turbine 15 of the gas turbine 1 is guided to the chimney 18 through the flue 17 and is supercritical in a portion near the turbine 15 in the flue 17, that is, a portion where the temperature of the gas turbine exhaust gas is highest. A flue CO ₂ heater 21 is provided to heat the CO ₂ used in the pressure CO ₂ gas turbine cycle 2. The place where the steam generator 3 for generating the steam injected into the gas turbine 1 is provided on the downstream side, that is, the portion where the temperature of the gas turbine exhaust gas is lowered is the same as in the first embodiment.

  In this embodiment, the case where the steam generator 3 is a single pressure type is shown. That is, the feed water fed by the feed water pump 34 is preheated by the economizer 33 and then led to one steam generator 30 to generate single pressure steam. Depending on the results of technical examination and economic comparison, it is possible to use a double pressure type as in the first embodiment.

  Steam generated by the steam generator 30 is injected into the gas turbine 1. When the thermoelectric variable type is required, the heat supply line 41 indicated by the one-dot chain line in the drawing of FIG. 4 and the regulating valves 38 and 43 are provided as in the second embodiment.

Flue CO CO ₂ heated by the _second heating unit 21 is sent to the combustor 19 of the gas turbine 1, further heated in cold wall pipe 19 installed in the combustor, after reaching a predetermined temperature, a supercritical pressure To the CO ₂ gas turbine cycle 2. That is, in this embodiment, the role of the CO ₂ heater of FIG. 7 is played by the flue CO ₂ heater 21 and the cooling wall pipe 19 provided in the combustor 14.

  FIG.5 (b) is sectional drawing of the silo type combustor of the conventional gas turbine. The gas turbine combustor includes a can type and an annular type in addition to the silo type. The silo type is considered to be optimal for applying the third embodiment because of its structure. Normally, one silo type combustor is provided for each gas turbine. The combustor 14 includes a double cylinder of an outer cylinder 51 and an inner cylinder 52, and fuel such as LNG burns in the inner cylinder 52. Because the heat causes the inner cylinder to become hot, combustion air is caused to flow through the annular part of the double cylinder, and the pores 53 are opened in the inner cylinder 52 so that the combustion air flows along the inner wall of the inner cylinder. Thus, cooling is performed.

FIG. 5A shows an example of the cooling wall pipe 19 in the combustor according to this embodiment installed in the silo type combustor. The cooling wall pipe 19 is installed in the combustor inner cylinder 52 in a form in which the tubes are wound in a close coil shape. The cooling wall pipe 19 functions as a heat exchanger for heating CO ₂ in the combustor and also functions as a cooling device for the inner cylinder 52. The CO ₂ 22 heated by the flue CO ₂ heater 21 is introduced into the in-combustor cooling wall pipe 19 and reheated. The CO ₂ 23 heated to a specified temperature is sent to the supercritical pressure CO ₂ gas turbine cycle 2.

Heating of CO ₂ sent to the supercritical pressure CO ₂ gas turbine is performed in two stages of the flue CO ₂ heater 21 and the cooling wall pipe 19 in the combustor, so that the heat transfer area of the flue CO ₂ heater 21 is increased. As a result, the installation space can be saved, and the pressure loss of CO _{2 in} the heating stage is reduced, and the power generation efficiency of the supercritical pressure CO ₂ gas turbine cycle, and thus the power generation efficiency of the combined power generation cycle is further improved.

FIG. 6 shows one temperature diagram calculated in this example.
The combustion gas generated in the combustor 14 is sent to the turbine 15 at 1,250 ° C. to generate power. The exhaust gas temperature at the outlet of the turbine 15 is 544 ° C., and is exchanged with the flue CO ₂ heater 21, the steam generator 30, and the economizer 33, and is discharged from the chimney at 183 ° C.
In this trial calculation, since heat is not supplied, the steam generated by the steam generator 30 is sent to the gas turbine 1 in its entirety.

CO ₂ flowing into the flue CO ₂ heater 21 at 385 ° C. is where it is heated to 450 ° C., is fed in to the cooling wall tube 19 combustor is further heated up to 490 ° C. with supercritical CO ₂ gas turbine cycle Sent to 2.

  There is a growing need for power generation systems with high power generation efficiency in the power generation range of 25,000 kWe class and below, and in addition to these, thermoelectric variable power generation systems. The combined power generation system of the present invention is very likely to be used in this field.

DESCRIPTION OF SYMBOLS 1 Gas turbine 2 Supercritical pressure CO ₂ Gas turbine cycle 3 Steam generator 11 Combustion air 12 Compressor 13 Fuel such as LNG 14 Combustor 15 Turbine 16 Generator 17 Chimney 18 Chimney 19 Cooling tube 21 in combustor 21 Flue CO ₂ Heater 22, 23 CO ₂
30 steam generator 31 high pressure steam generator 32 low pressure steam generator 33 economizer 34 feed water pump 35a, 35b regulating valve 36, 37 steam 38, 39 regulating valve 41, 42 heat supply line 51 combustor outer cylinder 52 in combustor Tube 53 pore

Claims (4)

A flue CO ₂ heating section and a steam generator for heat recovery of exhaust gas are arranged in the exhaust gas duct of a gas turbine (hereinafter referred to as “conventional gas turbine”) using LNG or the like as fuel from the upstream side. And the flue CO ₂ heating section is used as a CO ₂ heater in a supercritical pressure CO ₂ gas turbine cycle, and the steam generated by the steam generator is injected into the conventional gas turbine. Combined power generation system of CO ₂ gas turbine and conventional gas turbine   The combined power generation system according to claim 1, wherein a part or all of the steam generated by the steam generator is sent out of the combined power generation system as a heat source. A combined cycle power generation system according to claim 1, after the CO ₂ that is heated by the flue CO ₂ heater, the guided cooling wall tube combustor of a conventional gas turbine, reheated therein, A combined power generation system for sending to the supercritical pressure CO ₂ gas turbine.   4. The combined power generation system according to claim 3, wherein a part or all of the steam generated by the steam generator is sent out of the combined power generation system as a heat source.

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