JP5983213B2 - Supercritical steam combined cycle - Google Patents

Description

  The present invention relates to a supercritical steam combined cycle using a supercritical exhaust heat recovery boiler as an exhaust heat recovery boiler of a combined cycle power plant.

  A combined cycle power plant is a power plant that guides exhaust gas from a gas turbine to an exhaust heat recovery boiler, guides steam obtained by the exhaust heat recovery boiler to a steam turbine, and drives a generator to generate electric power. As a result, a highly efficient power plant is realized.

  Furthermore, what used the supercritical waste heat recovery boiler as the waste heat recovery boiler of a combined cycle power plant is proposed (for example, refer patent document 1). The use of a supercritical waste heat recovery boiler improves the efficiency of the steam cycle and the overall thermal efficiency of the combined cycle power plant.

JP 2009-092372 A

  However, when a supercritical exhaust heat recovery boiler is used, it is necessary to increase the exhaust gas temperature of the gas turbine. In the case of Patent Document 1, optimization in a high temperature part (superheater, reheater) is not necessarily performed. Not. For example, when the turbine inlet is above the supercritical pressure, the gas turbine exhaust gas temperature needs to be about 700 ° C. in order to achieve good steam conditions that do not get wet even at the turbine outlet. The exhaust gas temperature must be higher.

  FIG. 22 is a relationship diagram between temperature and enthalpy. Tg is the temperature of the exhaust gas supplied to the supercritical exhaust heat recovery boiler, Tc is the critical temperature, A is the gas phase liquid phase boundary of water, S1 is the fluid temperature of the superheater when the pressure is, for example, 30 MPa, and P1 is the pinch It is a point.

  When a superheater is installed in a supercritical exhaust heat recovery boiler, an exhaust gas temperature exceeding the pinch point P1 is necessary. Further, in order to achieve a steam condition that is higher than the supercritical pressure at the high-pressure turbine inlet and does not get wet at the high-pressure turbine outlet, the enthalpy of the steam at the superheater outlet needs to be Ha or higher. For this purpose, the exhaust gas temperature Ta must be about 700 ° C. (point P2).

  On the other hand, the case where a reheater is installed in addition to a superheater will be described. S2 is the steam temperature of the reheater. Since the steam pressure of the reheater is reduced because it passes through the turbine, it is about 7 MPa, for example. That is, S2 indicates the steam temperature of the reheater when the pressure is 7 MPa. Tz is the initial value of the steam temperature of the reheater. In addition, the initial value Hz of the enthalpy of steam of the reheater is lower than the enthalpy Ha of the outlet of the superheater. In this case, the heat exchange diagrams with the exhaust gas overlap, so to avoid it, Was the same value as the enthalpy Ha at the outlet of the superheater.

  In order to satisfy the steam condition that the steam led out from the reheater and led to the medium pressure turbine does not get wet at the medium pressure turbine outlet, the enthalpy of the steam at the reheater outlet needs to be Hb or more. is there. For this purpose, the exhaust gas temperature Tb must be 800 ° C. or higher (point P3).

  Thus, in the supercritical exhaust heat recovery boiler, reheating cannot be performed unless the exhaust gas temperature of the gas turbine is increased. At present, since the exhaust gas temperature of the gas turbine is about 700 ° C., it is difficult to reheat with the supercritical exhaust heat recovery boiler. On the other hand, reheating is desirable to improve the efficiency of the steam cycle.

  An object of the present invention is to provide a supercritical steam combined cycle that enables reheating to the steam cycle without increasing the temperature of the exhaust gas of the gas turbine supplied to the supercritical exhaust heat recovery boiler.

A supercritical steam combined cycle according to the invention of claim 1 includes a combustor that inputs compressed air and fuel from an air compressor and burns the fuel, a gas turbine that is driven by the combustion gas of the combustor, and A supercritical exhaust heat recovery boiler that generates steam that is supercritical fluid in the exhaust gas of the gas turbine, a high pressure turbine that is driven by steam that is supercritical fluid generated in the supercritical exhaust heat recovery boiler, and the high pressure turbine An intermediate pressure turbine driven by reheated steam that has finished work and is reheated in at least one of the gas turbine and the combustor, and a low pressure turbine driven by steam that has finished work in the intermediate pressure turbine, Bei example, said reheat steam, characterized in that said in a steam satisfies vapor not wetted even pressure turbine outlet.

  A supercritical steam combined cycle according to a second aspect of the present invention is the supercritical steam combined cycle according to the first aspect of the present invention, wherein the steam that has finished work in the intermediate pressure turbine is converted into at least one of the air compressor, the gas turbine, and the combustor. Then, the low-pressure turbine is driven by the reheated steam.

The supercritical steam combined cycle according to the invention of claim 3 is driven by a first stage combustor that inputs compressed air and fuel from an air compressor and burns the fuel, and combustion gas of the first stage combustor. A first stage gas turbine, a second stage combustor that inputs exhaust gas and fuel of the first stage gas turbine and burns the fuel, and a second stage gas driven by the combustion gas of the second stage combustor A turbine, a supercritical exhaust heat recovery boiler that generates steam as supercritical fluid from the exhaust gas of the second stage gas turbine, and a high pressure driven by the steam that is supercritical fluid generated in the supercritical exhaust heat recovery boiler The turbine and the high-pressure turbine finish work, and the reheat is reheated by at least one of the first stage gas turbine, the second stage gas turbine, the first stage combustor, and the second stage combustor. Medium pressure turbine driven by thermal steam Emissions and, e Bei a low pressure turbine driven by the steam after finishing of work in the intermediate-pressure turbine, the reheat steam is characterized in that said in a steam satisfies vapor not wetted even pressure turbine outlet .

  A supercritical steam combined cycle according to a fourth aspect of the present invention is the supercritical steam combined cycle according to the third aspect of the present invention, wherein the steam that has finished work in the intermediate pressure turbine is converted into the air compressor, the first stage gas turbine, and the second stage gas. Reheating is performed by at least one of a turbine, the first stage combustor, and the second stage combustor, and the low pressure turbine is driven by the reheated reheated steam.

According to the first aspect of the present invention, the high-pressure turbine is driven by the steam that is the supercritical fluid generated in the supercritical exhaust heat recovery boiler, and the steam that has finished work in the high-pressure turbine is reheated by the gas turbine or the combustor. Since the pressure turbine is driven, the reheat pipe can be a short distance between the high-pressure turbine and the gas turbine or combustor, or between the gas turbine or combustor and the intermediate-pressure turbine. Loss can be reduced. In addition, since the reheat steam satisfies the steam condition that does not get wet even at the outlet of the intermediate pressure turbine, reheat to the steam turbine can be realized without increasing the temperature of the exhaust gas supplied to the supercritical exhaust heat recovery boiler. .

  According to the invention of claim 2, in addition to the effect of the invention of claim 1, the steam that has finished work in the intermediate pressure turbine is reheated by at least one of an air compressor, a gas turbine, and a combustor. In addition, since the low-pressure turbine is driven, a highly efficient combined cycle power plant can be obtained, and energy saving can be achieved.

According to the invention of claim 3, the high-pressure turbine is driven by the steam that is the supercritical fluid generated in the supercritical exhaust heat recovery boiler, and the steam that has finished work in the high-pressure turbine is converted into the first stage gas turbine, the second stage Since the intermediate pressure turbine is driven by reheating at least one of the gas turbine, the first stage combustor, and the second stage combustor, the reheat pipe includes the high pressure turbine, the first stage gas turbine, and the second stage Short between gas turbine, first stage combustor, second stage combustor, first stage gas turbine, second stage gas turbine, first stage combustor, second stage combustor and medium pressure turbine The reheat steam is a steam that satisfies the steam condition that does not get wet even at the outlet of the intermediate pressure turbine , and the reheat steam can be recirculated to the steam turbine without increasing the temperature of the exhaust gas supplied to the supercritical exhaust heat recovery boiler. Heat can be realized.

  According to the invention of claim 4, in addition to the effect of the invention of claim 3, the steam that has finished work in the intermediate pressure turbine is converted into an air compressor, the first stage gas turbine, the second stage gas turbine, Since at least one of the first-stage combustor and the second-stage combustor drives the low-pressure turbine, a highly efficient combined cycle power plant can be obtained, and energy saving can be achieved.

The block diagram of the supercritical steam combined cycle which concerns on Example 1a of Embodiment 1 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 2a of Embodiment 1 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 3a of Embodiment 1 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 1b of Embodiment 2 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 2b of Embodiment 2 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 3b of Embodiment 2 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 4b of Embodiment 2 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 5b of Embodiment 2 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 1c of Embodiment 3 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 2c of Embodiment 3 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 3c of Embodiment 3 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 4c of Embodiment 3 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 5c of Embodiment 3 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 1d of Embodiment 4 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 2d of Embodiment 4 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 3d of Embodiment 4 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 4d of Embodiment 4 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 5d of Embodiment 4 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 1e of Embodiment 5 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 2e of Embodiment 5 of this invention. The block diagram of the supercritical steam combined cycle which concerns on Example 3e of Embodiment 5 of this invention. It is a relationship diagram between various temperatures and enthalpy in a supercritical exhaust heat recovery boiler.

  Embodiments of the present invention will be described below. FIGS. 1 to 3 are configuration diagrams of the supercritical steam combined cycle according to Embodiment 1 of the present invention, and show examples of the supercritical steam combined cycle of Examples 1a to 3a, respectively.

  In FIG. 1, the supercritical steam combined cycle has a gas turbine facility and a steam turbine facility, and guides the exhaust gas of the gas turbine 11 of the gas turbine facility to a supercritical exhaust heat recovery boiler 12, thereby supercritical exhaust heat recovery boiler 12. In this power generation plant, the steam obtained in step 1 is guided to the high-pressure turbine 13 of the steam turbine facility to drive the generator 14 to generate power.

  The gas turbine equipment includes a gas turbine 11, a combustor 15, and an air compressor 16. The combustor 15 inputs the compressed air and fuel from the air compressor 16 and burns the fuel. The combustion gas in the combustor 15 is supplied to the gas turbine 11 to drive the gas turbine 11.

  The exhaust gas that has finished its work in the gas turbine 11 is supplied to the supercritical exhaust heat recovery boiler 12, and the exhaust gas of the gas turbine 11 generates steam that is a supercritical fluid. Steam, which is a supercritical fluid generated in the supercritical exhaust heat recovery boiler 12, is guided as steam to the high-pressure turbine 13 to drive the high-pressure turbine 13. The steam that has finished work in the high-pressure turbine 13 is guided to the gas turbine 11 and reheated in the gas turbine 11. For example, steam that has finished work in the high-pressure turbine 13 is guided to the gas turbine 11 as steam for cooling the gas turbine blades.

  The reheated steam reheated in the gas turbine 11 is guided to the intermediate pressure turbine 17, and the steam that has finished work in the intermediate pressure turbine 17 is guided to the low pressure turbine 18 to drive the low pressure turbine 18. The steam that has finished its work in the low-pressure turbine 18 is returned to water by the condenser 19 and supplied to the supercritical exhaust heat recovery boiler 12 by the feed water pump 20. In the supercritical exhaust heat recovery boiler 12, water is converted into steam that is a supercritical fluid by the exhaust gas that has finished work in the gas turbine 11.

  Thus, since the high pressure turbine 13 is driven by the steam that is the supercritical fluid generated in the supercritical exhaust heat recovery boiler 12, the efficiency of the high pressure turbine 13 is improved. Moreover, since the steam which finished the work in the high-pressure turbine 13 is reheated by the gas turbine 11 and the intermediate-pressure turbine 13 is driven by the reheated steam, the efficiency of the entire steam turbine is improved.

  The steam that has finished its work in the high-pressure turbine 13 is reheated not in the supercritical exhaust heat recovery boiler 12 but in the gas turbine 11, so that the reheat pipe can be short. That is, the distance between the high-pressure turbine 13 and the gas turbine 11 and the distance between the gas turbine 11 and the intermediate-pressure turbine 17 are the distance between the high-pressure turbine 13 and the supercritical exhaust heat recovery boiler 12, the supercritical exhaust gas. Since the distance is shorter than the distance between the heat recovery boiler 12 and the intermediate pressure turbine 17, the reheat pipe can be shorter than the supercritical exhaust heat recovery boiler 12 for reheating.

  And since it reheats with the gas turbine 11 without reheating with the supercritical exhaust heat recovery boiler 12, it is not necessary to raise the temperature of the exhaust gas supplied to the supercritical exhaust heat recovery boiler 12 for reheating, Reheating to the steam turbine can be realized. Further, by using the supercritical exhaust heat recovery boiler 12, the temperature difference between the exhaust gas temperature in the high temperature portion of the supercritical exhaust heat recovery boiler 12 and the steam temperature supplied to the high pressure turbine 13 can be suppressed, so that efficient operation is possible. is there. As shown in FIG. 2, the same effect can be obtained even when the steam is reheated by the combustor 15 instead of the gas turbine 11 of FIG. 1.

  In the above description, the case where the steam that has finished work in the high-pressure turbine 13 is guided to the gas turbine 11 or the combustor 15 and reheated in the gas turbine 11 or the combustor 15 has been described. However, as shown in FIG. It may be guided to both the turbine 11 and the combustor 15 and reheated. The steam that has finished work in the high-pressure turbine 13 is guided to the gas turbine 11 and the combustor 15, and is reheated in both the gas turbine 11 and the combustor 15. Since the combustor 15 is also reheated, it is effective when the amount of heat due to steam cooling of the gas turbine 11 is insufficient.

  4 to 8 are configuration diagrams of the supercritical steam combined cycle according to Embodiment 2 of the present invention, and show examples of the supercritical steam combined cycle of Examples 1b to 5b, respectively.

  The second embodiment is different from the first embodiment shown in FIGS. 1 to 3 in that the steam that has finished work in the intermediate pressure turbine 17 is converted into at least one of the air compressor 16, the gas turbine 11, and the combustor 15. Then, the low-pressure turbine 18 is driven by the reheated steam that is reheated by at least one of the air compressor 16, the gas turbine 11, and the combustor 15. The same elements as those in FIGS. 1 to 3 are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 4 is different from FIG. 1 in that the steam that has finished work in the intermediate pressure turbine 17 is guided to the air compressor 16 and reheated by the air compressor 16. Further, FIG. 5 is a diagram in which the steam that has finished work in the intermediate pressure turbine 17 is guided to the gas turbine 11 and reheated in the gas turbine 11 with respect to FIG. 2. Further, FIG. 6 is a diagram in which the steam that has finished work in the intermediate pressure turbine 17 is guided to the combustor 15 and reheated in the combustor 15 with respect to FIG.

  The reheated steam reheated by at least one of the air compressor 16, the gas turbine 11, and the combustor 15 is guided to the low pressure turbine 18 to drive the low pressure turbine 18. Thereby, the efficiency of the steam turbine can be further increased and energy saving can be achieved.

  Further, as shown in FIG. 7, the reheated steam reheated by the air compressor 16 may be guided to the combustor 15 to perform further reheating, or as shown in FIG. The reheated reheated steam may be guided to the gas turbine 11 for further reheating. Since the temperature of the air compressor 16 is lower than that of the gas turbine 11 and the combustor 15, the air compressor 16 is further led to the gas turbine 11 and the combustor 15 to have a high steam temperature. This improves the efficiency of the steam cycle.

  FIG. 9 thru | or FIG. 13 is a block diagram of the supercritical steam combined cycle which concerns on Embodiment 3 of this invention, and has each shown an example of the supercritical steam combined cycle of Example 1c thru | or Example 5c.

  The third embodiment is applied to a reheat cycle gas turbine facility having a multi-stage gas turbine and a combustor as compared with the first embodiment shown in FIGS. The same elements as those in FIGS. 1 to 3 are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 9 is applied to a gas turbine equipment of a reheat cycle having a two-stage gas turbine and a combustor as compared with FIG. As shown in FIG. 9, the first stage combustor 15a receives the compressed air and fuel from the air compressor 16 and burns the fuel. And the combustion gas of the 1st stage combustor 15a is supplied to the 1st stage gas turbine 11a, and drives the 1st stage gas turbine 11a. The exhaust gas from the first stage gas turbine 11a is input to the second stage combustor 15b, and the fuel is also input to the second stage combustor 15b. Since the exhaust gas from the first stage gas turbine 11a is rich in air compared to the amount of fuel (for example, about three times the amount necessary for complete combustion), the fuel can be burned in the second stage combustor 15b. The combustion gas of the second stage combustor 15b is supplied to the second stage gas turbine 11b and drives the second stage gas turbine 11b. The exhaust gas that has finished work in the second stage gas turbine 11b is supplied to the supercritical exhaust heat recovery boiler 12, and the exhaust gas from the second stage gas turbine 11b generates steam that is a supercritical fluid.

  Then, the steam that is the supercritical fluid generated in the supercritical exhaust heat recovery boiler 12 is guided to the high-pressure turbine 13, and the steam that has finished work in the high-pressure turbine 13 is guided to the first stage gas turbine 11 a, and the first It is reheated by the stage gas turbine 11 a and guided to the intermediate pressure turbine 17.

  In this way, the two-stage gas turbines 11a and 11b and the two-stage combustors 15a and 15b are provided, and the exhaust gas from the first-stage first-stage gas turbine 11a is supplied to the second-stage second-stage combustor 15b. Therefore, since the restriction of NOX is eased, the combustion temperature of the second stage combustor 15b can be made higher. Therefore, the heat drop of the gas turbine can be increased and the power generation output can be increased.

  In the above description, the steam that has finished work in the high-pressure turbine 13 is guided to the first stage gas turbine 11a, but may be guided to the second stage gas turbine 11b. Furthermore, as shown in FIG. 10, it may be guided to both the first stage gas turbine 11a and the second stage gas turbine 11b.

  Further, as shown in FIG. 11, instead of the first stage gas turbine 11a, the steam may be reheated by the first stage combustor 15a or may be led to the second stage combustor 15b. . Furthermore, as shown in FIG. 12, it may be guided to both the first stage combustor 15a and the second stage combustor 15b.

  Moreover, as shown in FIG. 13, the steam which finished the work in the high-pressure turbine 13 is led to the first stage gas turbine 11a and the second stage gas turbine 11b, the first stage combustor 15a and the second stage combustor 15b, You may make it reheat in the 1st stage gas turbine 11a and the 2nd stage gas turbine 11b, the 1st stage combustor 15a, and the 2nd stage combustor 15b.

  As shown in FIG. 13, the steam that has finished work in the high-pressure turbine 13 is also led to the first stage gas turbine 11a and the second stage gas turbine 11b, the first stage combustor 15a, and the second stage combustor 15b, Reheating is performed in both the two-stage gas turbines 11a and 11b and the two-stage combustors 15a and 15b. Since reheating is performed in both the two-stage gas turbines 11a and 11b and the two-stage combustors 15a and 15b, the amount of heat of the reheated steam is further increased, and the efficiency of the steam cycle is improved. Thus, by applying to the gas turbine equipment of the reheat cycle which has a multistage gas turbine and a combustor, the shortage of heating heat amount of reheat steam can be solved.

  14 to 18 are configuration diagrams of the supercritical steam combined cycle according to Embodiment 4 of the present invention, and show examples of the supercritical steam combined cycle of Examples 1d to 5d, respectively. The fourth embodiment is different from the third embodiment shown in FIGS. 9 to 13 in that the steam that has finished work in the intermediate pressure turbine 17 is converted into the air compressor 16, the first stage gas turbine 11a, and the second stage gas turbine 11b. The low-pressure turbine is driven by the reheated steam that is reheated by at least one of the first stage combustor 15a and the second stage combustor 15b. The same elements as those in FIGS. 9 to 13 are denoted by the same reference numerals and redundant description is omitted.

  FIG. 14 shows the embodiment 2c of FIG. 10 in which the steam that has finished work in the intermediate pressure turbine 17 is guided to the air compressor 16 and the low pressure turbine 18 is driven by the reheated steam reheated by the air compressor 16. It is what I did.

  FIG. 15 shows the low pressure turbine with the reheated steam re-heated by the first-stage gas turbine 11a, with the steam that has finished work in the intermediate-pressure turbine 17 guided to the first-stage gas turbine 11a with respect to the embodiment 4c of FIG. 18 is driven.

  FIG. 16 shows the low pressure turbine with the reheated steam re-heated by the first-stage combustor 15a, with the steam that has finished work in the intermediate-pressure turbine 17 being guided to the first-stage combustor 15a with respect to the embodiment 2c of FIG. 18 is driven.

  FIG. 17 shows that the steam that has finished work in the intermediate pressure turbine 17 is led to the air compressor 16, the first stage combustor 15 a, and the second stage combustor 15 b with respect to the embodiment 2 c of FIG. The low-pressure turbine 18 is driven by reheated steam reheated by the first stage combustor 15a and the second stage combustor 15b.

  FIG. 18 shows, with respect to the embodiment 4c of FIG. 12, the steam that has finished work in the intermediate pressure turbine 17 is guided to the air compressor 16, the first stage gas turbine 11a, and the second stage gas turbine 11b. The low-pressure turbine 18 is driven by reheated steam reheated by the first stage gas turbine 11a and the second stage gas turbine 11b.

  In this way, the steam that has finished work in the intermediate pressure turbine 17 is supplied to at least one of the air compressor 16, the first stage gas turbine 11a and the second stage gas turbine 11b, the first stage combustor 15a, and the second stage combustor 15b. Since either one is reheated and the low-pressure turbine is driven by the reheated reheated steam, the efficiency of the steam cycle can be increased and energy saving can be achieved.

  Further, with respect to the embodiment 2c of FIG. 10, the steam that has finished work in the intermediate pressure turbine 17 is led to at least one of the two-stage gas turbines 11a and 11b and the two-stage combustors 15a and 15b to be reheated. May be performed. Thermal efficiency is further improved by performing two-stage reheating in the steam cycle.

  FIGS. 19 to 21 are configuration diagrams of the supercritical steam combined cycle according to Embodiment 5 of the present invention, and show examples of supercritical steam combined cycles of Examples 1e to 3e, respectively.

  The fifth embodiment is different from the third embodiment shown in FIGS. 9 to 13 and the fourth embodiment shown in FIGS. 14 to 18 in that the steam that has finished work in the high-pressure turbine 13 is converted into a two-stage gas turbine 11a. , 11b and the two-stage combustors 15a, 15b are supplied in series. The same elements as those in FIGS. 9 to 13 and FIGS. 14 to 18 are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 19 shows an example of supplying steam that has finished work in the high-pressure turbine 13 to the two-stage gas turbines 11a and 11b and the two-stage combustors 15a and 15b, as compared with Example 5c of Embodiment 3 shown in FIG. The first stage gas turbine 11a and the second stage gas turbine 11b are supplied in series instead of being supplied in parallel, and similarly to the first stage combustor 15a and the second stage combustor 15b. However, instead of parallel, it is supplied in series.

Figure 20 is to Example 1d of the fourth embodiment shown in FIG. 14, Ri per the supplying steam after finishing of work in the high pressure turbine 13 the two-stage gas turbine 11a, the 11b, first stage gas turbine 11a and the second stage gas turbine 11b are supplied in series instead of being supplied in parallel.

  FIG. 21 shows that the first stage combustor 15a and the second stage combustor 15a and 15b are supplied with the steam that has finished work in the high pressure turbine 13 to the example 5d of the fourth embodiment shown in FIG. Instead of being supplied in parallel, the two-stage combustor 15b is supplied in series. In the case of the fifth embodiment, the same effect as in the third and fourth embodiments can be obtained.

  Here, in the fifth embodiment, in contrast to the fifth embodiment of the third embodiment, the first embodiment of the fourth embodiment, and the fifth embodiment of the fourth embodiment, the steam that has finished work in the high-pressure turbine 13 is replaced in parallel and serially. Although the case where it supplies and reheats was demonstrated, it replaces with the steam which finished work with the high pressure turbine 13, and supplies it in series similarly and reheats also about the other Examples of Embodiment 3, 4. You may do it.

  In the fifth embodiment, the steam that has finished work in the intermediate pressure turbine 17 may be reheated by the gas turbine 11, the combustor 15, and the air compressor 16 connected in series or in parallel and supplied to the low pressure turbine 18. .

  As mentioned above, although some embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 11 ... Gas turbine, 12 ... Supercritical waste heat recovery boiler, 13 ... High pressure turbine, 14 ... Generator, 15 ... Combustor, 16 ... Air compressor, 17 ... Medium pressure turbine, 18 ... Low pressure turbine, 19 ... Condensate 20, water supply pump

Claims (4)

A combustor that inputs compressed air and fuel from an air compressor and burns the fuel;
A gas turbine driven by the combustion gas of the combustor;
A supercritical exhaust heat recovery boiler that generates steam that is a supercritical fluid in the exhaust gas of the gas turbine;
A high-pressure turbine driven by steam, which is a supercritical fluid generated in the supercritical exhaust heat recovery boiler;
An intermediate pressure turbine driven by reheated steam that has finished work in the high pressure turbine and is reheated in at least one of the gas turbine and the combustor;
E Bei a low pressure turbine driven by the steam after finishing of work in the intermediate-pressure turbine,
The superheated steam combined cycle , wherein the reheated steam is a steam that satisfies a steam condition that does not get wet even at the outlet of the intermediate pressure turbine .   The steam that has finished work in the intermediate pressure turbine is reheated by at least one of the air compressor, the gas turbine, and the combustor, and the low pressure turbine is driven by the reheated steam. The supercritical steam combined cycle according to claim 1. A first stage combustor for receiving compressed air and fuel from an air compressor and burning the fuel;
A first stage gas turbine driven by the combustion gas of the first stage combustor;
A second stage combustor for inputting the exhaust gas and fuel of the first stage gas turbine and burning the fuel;
A second stage gas turbine driven by the combustion gas of the second stage combustor;
A supercritical exhaust heat recovery boiler that generates steam that is a supercritical fluid in the exhaust gas of the second stage gas turbine;
A high-pressure turbine driven by steam, which is a supercritical fluid generated in the supercritical exhaust heat recovery boiler;
Reheated steam that has finished work in the high-pressure turbine and has been reheated by at least one of the first-stage gas turbine, the second-stage gas turbine, the first-stage combustor, and the second-stage combustor. A driven medium pressure turbine;
E Bei a low pressure turbine driven by the steam after finishing of work in the intermediate-pressure turbine,
The superheated steam combined cycle , wherein the reheated steam is a steam that satisfies a steam condition that does not get wet even at the outlet of the intermediate pressure turbine .   Steam that has finished work in the intermediate pressure turbine is converted into at least one of the air compressor, the first stage gas turbine, the second stage gas turbine, the first stage combustor, and the second stage combustor. The supercritical steam combined cycle according to claim 3, wherein the low pressure turbine is driven by the reheated reheated steam.

Images