JP2014185613A - Preheater device of fuel for gas turbine, gas turbine plant including the same, and preheating method of fuel for gas turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a preheater device of a fuel for a gas turbine which improves heat efficiency of an entire gas turbine plant while cooling a high temperature component in a gas turbine.SOLUTION: A preheater device of a fuel for a gas turbine includes: a first preheater 51 which conducts heat exchange between steam and a fuel F to preheat the fuel F and flows out the steam cooled by preheating the fuel F as cooling steam CS; a cooling steam line 62 which supplies the cooling steam CS to a high temperature component of a gas turbine 10 contacting with a combustion gas; a superheated steam line 63 in which superheated steam SS, the cooling steam CS that has passed through the high temperature component, passes; a second preheater 52 which conducts heat exchange between the superheated steam SS supplied from the superheated steam line 63 and a fuel F to preheat the fuel F; and a preheat fuel line 71 which supplies the fuel F preheated by the first preheater 51 and the second preheater 52 to a combustor 21.

Description

  The present invention relates to a preheating device for a gas turbine fuel in a gas turbine including a combustor that burns fuel to generate combustion gas and a turbine that is driven by the combustion gas, a gas turbine plant including the same, and a gas The present invention relates to a method for preheating turbine fuel.

  The gas turbine includes a compressor that compresses air, a combustor that generates combustion gas by burning fuel in the air compressed by the compressor, and a turbine that is driven by the combustion gas. The fuel supplied to the combustor is often preheated before being supplied to the combustor in order to save fuel and increase the efficiency of the gas turbine.

  Patent Document 1 below discloses a gas turbine plant that preheats fuel supplied to a combustor with steam. This gas turbine plant supplies a gas turbine, an exhaust heat recovery boiler that generates steam by the heat of exhaust gas from the gas turbine, a steam turbine that is driven by the steam generated by the exhaust heat recovery boiler, and a combustor. And a preheater for heating the fuel to be produced. The preheater is connected to a first steam line that supplies steam generated in the exhaust heat recovery boiler to the preheater. Furthermore, the preheater is connected to a second steam line that guides the steam that has heated the fuel to high-temperature components such as a combustor. In addition, a third steam line is connected to the high-temperature parts to guide the steam that has cooled the high-temperature parts to a steam turbine or the like. The gas turbine plant further includes a temperature reducing spray that injects water into the second steam line in order to cool the steam flowing through the second steam line, that is, the steam that has heated the fuel.

JP-A-10-325338

  In the technique described in Patent Document 1, since the steam that has heated the fuel is cooled with water and then this steam is supplied to the high-temperature components, the heat of the steam that has heated the fuel cannot be effectively used. There is a problem that the thermal efficiency of the whole plant is not so good.

  Accordingly, the present invention provides a gas turbine fuel preheating device capable of increasing the thermal efficiency of the entire gas turbine plant while cooling high-temperature components in the gas turbine, a gas turbine plant including the same, and a gas turbine fuel An object of the present invention is to provide a preheating method.

An apparatus for preheating a gas turbine fuel as one aspect according to the invention for solving the above-described problems,
A first preheater in which steam and fuel are heat-exchanged to preheat the fuel, and the steam cooled by preheating the fuel flows out as cooling steam, and a combustor that burns the fuel to generate combustion gas And a cooling steam line for supplying the cooling steam to any one of the turbines driven by the combustion gas and in contact with the combustion gas, and the cooling steam passing through the high temperature parts A superheated steam line through which a certain superheated steam passes, a second preheater for preheating the fuel by exchanging heat between the superheated steam supplied from the superheated steam line and the fuel, the first preheater, and the second preheater And a preheating fuel line for supplying the fuel preheated by the preheater to the combustor.

  In the preheating device, steam is supplied to the high-temperature parts and the high-temperature parts are cooled, so the air extracted from the compressor of the gas turbine is supplied along the surface where the high-temperature parts come into contact with the combustion gas, Rather than cooling the parts, the cooling efficiency of the high-temperature parts and the efficiency of the gas turbine plant can be increased.

  Specifically, since steam has a higher thermal conductivity and a larger heat capacity than air, high-temperature components can be efficiently cooled. Moreover, when the compressed air is extracted from the compressor of the gas turbine and this air is used for cooling the high-temperature parts, the output of the gas turbine and the output of the exhaust heat recovery device are also reduced. The efficiency of the turbine plant is reduced. On the other hand, in the preheating device, when the steam from the exhaust heat recovery device is used for cooling the high-temperature components, the output of the exhaust heat recovery device is reduced, but the output of the gas turbine is not reduced. Therefore, the use of the steam from the exhaust heat recovery device for cooling the high-temperature components can suppress a decrease in the efficiency of the gas turbine plant, in other words, the efficiency of the gas turbine plant can be increased.

  Further, in the preheating device, the steam and the fuel are heat-exchanged by the first preheater, and after cooling the steam, the cooled steam is supplied to the high-temperature component as the cooling steam. Parts can be efficiently cooled.

  Further, in the preheating device, the superheated steam that is superheated by the cooling of the high-temperature parts and the fuel are heat-exchanged by the second preheater and the fuel is heated, so that the heat of the steam, in other words, combustion The heat of the vessel can be used effectively, and the efficiency of the gas turbine plant can be increased also from this viewpoint.

  By the way, in the technique described in Patent Document 1, the heat of the combustor is returned to the steam of the exhaust heat recovery device to increase the efficiency of the exhaust heat recovery device, but the efficiency of the gas turbine cannot be increased. On the other hand, in the preheating device, the heat of the combustor is used for preheating the fuel, so that the efficiency of both the gas turbine and the exhaust heat recovery device can be increased. Can be increased.

  Moreover, in the said preheating apparatus, since the fuel is preheated with the 1st preheater and the 2nd preheater, the temperature of fuel can be made higher.

  Here, in the gas turbine fuel preheating apparatus as the one aspect, the preheating fuel line includes a first preheating fuel line that supplies the fuel preheated by the first preheater to the second preheater; And a second preheating fuel line for supplying the fuel preheated by the second preheater to the combustor.

  In the preheating device, since the first preheater and the second preheater are arranged in series with the fuel, high temperature fuel can be supplied to the combustor. In particular, when the temperature of the superheated steam supplied to the second preheater is higher than the temperature of the steam supplied to the first preheater, the temperature of the fuel can be increased efficiently.

  In the gas turbine fuel preheating apparatus according to the aspect, the preheating fuel line receives the fuel preheated by the first preheater and the fuel preheated by the second preheater. And an integrated preheat fuel line for supplying to the combustor.

  In the preheating device, the first preheater and the second preheater are arranged in parallel with the fuel. For this reason, the flow rate of the fuel supplied to one preheater decreases, for example, the temperature of the steam supplied to the first preheater and the temperature of the superheated steam supplied to the second preheater are substantially the same. In some cases, the fuel can be heated efficiently.

  The gas turbine fuel preheating apparatus may further include a third preheater that preheats the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium. .

  Since the preheating device includes the third preheater, more heat can be applied to the fuel.

  In the gas turbine fuel preheating apparatus having the first preheating fuel line and the second preheating fuel line, the fuel supplied to the combustor and a preheating medium are heat-exchanged to preheat the fuel. The preheat fuel line may include a third preheat fuel line that supplies the fuel preheated by the third preheater to the first preheater.

  In the preheating device, since the three preheaters are arranged in series with the fuel, higher temperature fuel can be supplied to the combustor.

  In the gas turbine fuel preheating apparatus having the integrated preheating fuel line, the gas turbine fuel preheating apparatus further includes a third preheater that preheats the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium, The preheat fuel line may include a third preheat fuel line that supplies the fuel preheated by the third preheater to each of the first preheater and the second preheater.

  In the preheating device, for example, the temperature of the preheating medium supplied to the third preheater is lower than the temperature of the steam supplied to the first preheater and the temperature of the superheated steam supplied to the second preheater, and When the temperature of the steam supplied to the one preheater and the temperature of the superheated steam supplied to the second preheater are substantially the same, the fuel can be efficiently heated.

  In the gas turbine fuel preheating apparatus having the integrated preheating fuel line, the gas turbine fuel preheating apparatus further includes a third preheater that preheats the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium, The integrated preheat fuel line supplies the fuel preheated by the third preheater to the combustor together with the fuel preheated by the first preheater and the fuel preheated by the second preheater. May be.

  In the preheating device, the first preheater, the second preheater, and the third preheater are arranged in parallel with the fuel. For this reason, the flow rate of the fuel supplied to one preheater decreases, for example, the temperature of the steam supplied to the first preheater, the temperature of the superheated steam supplied to the second preheater, and the third preheater. When the temperature of the preheating medium supplied to the fuel is approximately the same, the fuel can be efficiently heated.

A gas turbine plant as one aspect according to the invention for solving the above problems is as follows:
Any of the above gas turbine fuel preheating apparatus, a gas turbine having the combustor and the turbine, and an exhaust heat recovery apparatus having an exhaust heat recovery boiler that generates steam by the heat of exhaust gas from the turbine The preheating device has a preheating medium line that supplies the steam in the exhaust heat recovery device to the first preheater.

  Since the gas turbine plant includes the preheating device, it is possible to effectively use the heat of the steam and efficiently improve the efficiency of the gas turbine plant while efficiently cooling the fuel of the gas turbine with the steam.

Moreover, the gas turbine plant as another aspect according to the invention for solving the above-described problems is
One of the gas turbine fuel preheating apparatuses having a third preheater, a gas turbine having the combustor and the turbine, and an exhaust heat recovery boiler that generates steam by the heat of exhaust gas from the turbine. An exhaust heat recovery device having a first preheating medium line for supplying steam in the exhaust heat recovery device to the first preheater, and steam or water in the exhaust heat recovery device. And a second preheating medium line that supplies the third preheater.

  Since the gas turbine plant also has the preheating device, it is possible to efficiently use the heat of the steam and efficiently improve the efficiency of the gas turbine plant while efficiently cooling the fuel of the gas turbine with the steam.

A method for preheating a gas turbine fuel as one aspect according to the invention for solving the above-described problems,
A first preheating step for heat-exchanging steam and fuel to preheat the fuel and outflowing steam cooled by preheating the fuel as cooling steam, and a combustor for combusting the fuel to generate combustion gas And a cooling steam supply step for supplying the cooling steam to any one of the turbines driven by the combustion gas, which is in contact with the combustion gas, and the cooling steam that has passed through the high temperature part Heat exchange between the superheated steam and the fuel supplied to the combustor to preheat the fuel, and the fuel preheated in the first preheating step and the second preheating step. And a preheating fuel supply step for supplying to the combustor.

  Also in the preheating method, steam is supplied to the high-temperature parts and the high-temperature parts are cooled in the same manner as in the preheating device, so that the high-temperature parts are extracted from the compressor of the gas turbine along the surface in contact with the combustion gas. It is possible to increase the cooling efficiency of the high-temperature parts and the efficiency of the gas turbine plant rather than supplying air to cool the high-temperature parts. In the preheating method, the steam and the fuel are exchanged in the first preheating step, and after cooling the steam, the cooled steam is supplied to the high-temperature components as cooling steam. Parts can be efficiently cooled.

  In the preheating method, the superheated steam, which is the cooling steam superheated by cooling the high-temperature parts, and the fuel are heat-exchanged in the second preheating step to heat the fuel, so that the heat of the steam, in other words, combustion The heat of the vessel can be used effectively, and the efficiency of the gas turbine plant can be increased.

  Furthermore, in the preheating method, since the fuel is preheated in the first preheating step and the second preheating step, the temperature of the fuel can be further increased.

  In the present invention, it is possible to increase the thermal efficiency of the entire gas turbine plant by effectively using the heat of steam while cooling high-temperature components in the gas turbine.

1 is a system diagram of a gas turbine plant in a first embodiment according to the present invention. It is a typical sectional view of a gas turbine in a first embodiment concerning the present invention. It is a systematic diagram of the gas turbine plant in 2nd embodiment which concerns on this invention. It is a systematic diagram of the gas turbine plant in 3rd embodiment which concerns on this invention. It is a systematic diagram of the gas turbine plant in 4th embodiment which concerns on this invention. It is a systematic diagram of the gas turbine plant in 5th embodiment which concerns on this invention.

  Hereinafter, various embodiments of a gas turbine plant according to the present invention will be described with reference to the drawings.

"First embodiment"
First, with reference to FIG.1 and FIG.2, 1st embodiment of the gas turbine plant which concerns on this invention is described.

  As shown in FIG. 1, the gas turbine plant of the present embodiment generates steam by the heat of the gas turbine 10, the generator 15 that generates power by driving the gas turbine 10, and the exhaust gas EG exhausted from the gas turbine 10. An exhaust heat recovery device 100 to be discharged, a chimney 40 that discharges exhaust gas EG that has passed through the exhaust heat recovery device 100 to the atmosphere, and a fuel preheating device 50 that preheats the fuel F supplied to the gas turbine 10.

  The gas turbine 10 is driven by a compressor 11 that compresses air, a plurality of combustors 21 that combust fuel F in the air compressed by the compressor 11 to generate combustion gas, and high-temperature and high-pressure combustion gas. A turbine 31. The turbine rotor of the turbine 31 and the compressor rotor of the compressor 11 rotate about the same axis, and are connected to each other to form a gas turbine rotor. The rotor of the generator 15 is connected to this gas turbine rotor.

  As shown in FIG. 2, the combustor 21 combusts the fuel F in the air A from the compressor 11 and generates combustion gas, and compresses the combustion cylinder 23 in the combustion cylinder 23. And an injector 22 for injecting air A and fuel F from the machine 11. The member forming the combustion cylinder 23 is formed with a steam flow path 24 through which steam passes to cool the member.

  The turbine 31 includes a turbine rotor 32 that rotates about the axis Ar by combustion gas from the plurality of combustors 21, and a turbine casing 35 that rotatably covers the turbine rotor 32. The turbine rotor 32 includes a rotor main body 33 extending in the axial direction parallel to the axis Ar, and a plurality of moving blades 34 fixed to the outer periphery of the rotor main body 33. A plurality of stationary blades 36 are fixed to the inner peripheral surface of the turbine casing 35. Between the inner peripheral surface of the turbine casing 35 and the outer peripheral surface of the rotor body 33, a combustion gas passage 37 through which the combustion gas from the combustor 21 passes is formed. The plurality of combustors 21 are fixed to the turbine casing 35 side by side in the circumferential direction about the axis Ar.

  As shown in FIG. 1, the exhaust heat recovery apparatus 100 includes an exhaust heat recovery boiler 110 that generates steam by the heat of combustion gas that drives the turbine 31, that is, exhaust gas EG exhausted from the gas turbine 10, and exhaust heat. Steam turbines 121a, 121b, and 121c driven by steam generated in the recovery boiler 110, a generator 122 that generates power by driving the steam turbines 121a, 121b, and 121c, and condensate for returning the steam that has driven the steam turbine 121a to water. And a water supply pump 124 for returning the water in the condenser 123 to the exhaust heat recovery boiler 110.

  The exhaust heat recovery apparatus 100 includes a low pressure steam turbine 121a, an intermediate pressure steam turbine 121b, and a high pressure steam turbine 121c as the steam turbines 121a, 121b, and 121c. Further, the exhaust heat recovery boiler 110 includes a low-pressure steam generator 111a that generates low-pressure steam LS, an intermediate-pressure steam generator 111b that generates intermediate-pressure steam IS, a high-pressure steam generator 111c that generates high-pressure steam HS, A reheating unit 115 that reheats the steam that has driven the high-pressure steam turbine 121c. Here, one generator 122 is provided for a total of three steam turbines including the low-pressure steam turbine 121a, the intermediate-pressure steam turbine 121b, and the high-pressure steam turbine 121c, but each steam turbine 121a, 121b, You may provide a generator in 121c.

  The low-pressure steam generator 111a superheats the low-pressure economizer 112a that heats water, the low-pressure evaporator 113a that converts water heated by the low-pressure economizer 112a into steam, and the steam generated by the low-pressure evaporator 113a. And a low-pressure superheater 114a that generates low-pressure steam LS.

  The intermediate pressure steam generator 111b includes an intermediate pressure pump 116b that pressurizes water heated by the low pressure economizer 112a, an intermediate pressure economizer 112b that heats water pressurized by the intermediate pressure pump 116b, An intermediate pressure evaporator 113b that converts water heated by the economizer 112b into steam, and an intermediate pressure superheater 114b that generates intermediate pressure steam IS by overheating the steam generated in the intermediate pressure evaporator 113b. ing.

  The high-pressure steam generator 111c includes a high-pressure pump 116c that pressurizes water heated by the low-pressure economizer 112a, a first high-pressure economizer 112c that heats water pressurized by the high-pressure pump 116c, and a first high-pressure economizer. Generated by the second high-pressure economizer 112d for further heating the water heated by the carbonizer 112c, the high-pressure evaporator 113c for converting the water heated by the second high-pressure economizer 112d into steam, and the high-pressure evaporator 113c The first high-pressure superheater 114c that superheats the steam and the second high-pressure superheater 114d that further superheats the steam superheated by the first high-pressure superheater 114c to generate the high-pressure steam HS.

  The reheat unit 115 generates a reheat steam RHS by further superheating the steam reheated by the first reheater 115a that heats the steam that has driven the high-pressure steam turbine 121c and the first reheater 115a. Two reheaters 115b.

  The elements constituting each of the reheating unit 115, the high-pressure steam generation unit 111c, the intermediate-pressure steam generation unit 111b, and the low-pressure steam generation unit 111a are second to the downstream side of the exhaust gas EG from the turbine 31 toward the chimney 40. Reheater 115b and second high pressure superheater 114d, first reheater 115a, first high pressure superheater 114c, high pressure evaporator 113c, second high pressure economizer 112d, intermediate pressure superheater 114b and low pressure superheater 114a, The medium pressure evaporator 113b, the first high pressure economizer 112c, the medium pressure economizer 112b, the low pressure evaporator 113a, and the low pressure economizer 112a are arranged in this order.

  The condenser 123 and the low pressure economizer 112 a are connected by a water supply line 131. The water supply line 131 is provided with the above-described water supply pump 124. The low pressure superheater 114a and the steam inlet of the low pressure steam turbine 121a are connected by a low pressure steam line 132 that sends the low pressure steam LS from the low pressure superheater 114a to the low pressure steam turbine 121a. The steam outlet of the low-pressure steam turbine 121 a and the condenser 123 are connected to each other so that the low-pressure steam LS that drives the low-pressure steam turbine 121 a is supplied to the condenser 123. The first high-pressure superheater 114c and the second high-pressure superheater 114d are connected by an inter-superheater steam line 135. The second high pressure superheater 114d and the steam inlet of the high pressure steam turbine 121c are connected by a high pressure steam line 138 that sends the high pressure steam HS from the second high pressure superheater 114d to the high pressure steam turbine 121c. The steam outlet of the high-pressure steam turbine 121c and the steam inlet of the first reheater 115a are connected by a high-pressure steam recovery line 139 that sends the high-pressure steam HS from the high-pressure steam turbine 121c to the first reheater 115a. The steam outlet of the second reheater 115b and the steam inlet of the intermediate pressure steam turbine 121b are a reheat steam line 136 that sends the steam superheated by the second reheater 115b to the intermediate pressure steam turbine 121b as reheated steam RHS. Connected with. An intermediate pressure steam recovery line 137 is connected to the steam outlet of the intermediate pressure steam turbine 121b. The intermediate pressure steam recovery line 137 merges with the low pressure steam line 132. An intermediate pressure steam line 133 is connected to the steam outlet of the intermediate pressure superheater 114b. The intermediate pressure steam line 133 joins the high pressure steam recovery line 139.

  The fuel preheating device 50 is a preheating fuel that connects the first preheater 51 and the second preheater 52 that heat the fuel F supplied to the combustor 21, and the first preheater 51, the second preheater 52, and the combustor 21. A line 71 and a preheating medium line 60 for sucking and exhausting steam to and from the first preheater 51 and the second preheater 52 are provided.

  The first preheater 51 and the second preheater 52 are both heat exchangers that exchange heat between the fuel F and the steam. A fuel supply line 70 extending from the fuel supply source is connected to the inlet of the first preheater 51 inside or outside the tube. The preheat fuel line 71 includes a first preheat fuel line 73 that connects an outlet inside or outside the tube of the first preheater 51 and an inlet inside or outside the tube of the second preheater 52, and the second preheater 52. And a second preheating fuel line 74 that connects the outlet on the inside or outside of the tube and the combustor 21. The preheating medium line 60 includes a preheating steam supply line 61 that connects an extraction port 125 of the high-pressure steam turbine 121c and an inlet outside or inside the pipe of the first preheater 51, and an outside or inside of the pipe of the first preheater 51. The cooling steam line 62 that connects the outlet of the combustion chamber 21 to the combustor 21, the superheated steam line 63 that connects the combustion chamber 21 to the outside of the tube of the second preheater 52 or the inlet inside the tube, and the tube of the second preheater 52 A preheated steam recovery line 64 that connects an outlet on the outside or the inside of the pipe and a high pressure steam recovery line 139;

  As shown in FIG. 2, the second preheating fuel line 74 is connected to the injector 22 of the combustor 21. The cooling steam line 62 is connected to one end of the steam flow path 24 in the combustion cylinder 23 of the combustor 21, and the superheated steam line 63 is connected to the other end of the steam flow path 24.

  Next, operation | movement of the gas turbine plant of this embodiment demonstrated above is demonstrated.

  As shown in FIG. 2, the compressor 11 of the gas turbine 10 compresses air A in the atmosphere and supplies the compressed air A to the combustor 21. The combustor 21 is also supplied with fuel F from the second preheating fuel line 74. In the combustion cylinder 23 of the combustor 21, the fuel F is combusted in the compressed air A, and high-temperature and high-pressure combustion gas is generated. The combustion gas is sent from the combustion cylinder 23 into the combustion gas flow path 37 of the turbine 31, and the turbine rotor 32 of the turbine 31 is rotated. The generator 15 connected to the gas turbine 10 generates power by the rotation of the turbine rotor 32.

  The combustion gas obtained by rotating the turbine rotor 32 of the turbine 31 is exhausted from the gas turbine 10 as exhaust gas EG, and is discharged from the chimney 40 to the atmosphere via the exhaust heat recovery boiler 110. The exhaust heat recovery apparatus 100 recovers heat contained in the exhaust gas EG in the process in which the exhaust gas EG from the gas turbine 10 passes through the exhaust heat recovery boiler 110.

  In the exhaust heat recovery boiler 110, the water from the condenser 123 is supplied through the water supply line 131 to the low-pressure economizer 112a on the most downstream side (chimney 40 side). The low pressure economizer 112a heats this water by exchanging heat with the exhaust gas EG. A part of the water heated by the low pressure economizer 112a is further heated by the low pressure evaporator 113a to become steam. This steam is further heated by the low-pressure superheater 114a and supplied as low-pressure steam LS to the low-pressure steam turbine 121a via the low-pressure steam line 132. The steam that has driven the low-pressure steam turbine 121 a returns to water in the condenser 123. This water is supplied again from the condenser 123 to the low-pressure economizer 112 a through the water supply line 131.

  The other part of the water heated by the low pressure economizer 112a is pressurized by the intermediate pressure pump 116b and sent to the intermediate pressure economizer 112b, and the remaining water heated by the low pressure economizer 112a is high pressure. The pressure is raised by the pump 116c and sent to the first high-pressure economizer 112c.

  The first high-pressure economizer 112c heats the water sent from the high-pressure pump 116c by exchanging heat with the exhaust gas EG. The water heated by the first high pressure economizer 112c is further heated by the second high pressure economizer 112d. This water is further heated by the high-pressure evaporator 113c to become steam. This steam is further superheated by the first high-pressure superheater 114c and the second high-pressure superheater 114d to become high-pressure steam HS. The high-pressure steam HS is supplied to the high-pressure steam turbine 121c via the high-pressure steam line 138.

  The intermediate pressure economizer 112b heats the water sent from the intermediate pressure pump 116b by exchanging heat with the exhaust gas EG. The water heated by the medium pressure economizer 112b is further heated by the intermediate pressure evaporator 113b to become steam. This steam is further superheated by the medium pressure superheater 114b to become medium pressure steam IS. This intermediate pressure steam IS joins with the steam flowing through the high pressure steam recovery line 139 via the intermediate pressure steam line 133, is resuperheated by the first reheater 115a and the second reheater 115b, and reheated steam RHS. It becomes. The reheat steam RHS is supplied to the intermediate pressure steam turbine 121b via the reheat steam line 136.

  The reheated steam RHS that has driven the intermediate pressure steam turbine 121b is supplied to the low pressure steam turbine 121a via the intermediate pressure steam recovery line 137 and the low pressure steam line 132.

  A part of the high-pressure steam HS supplied to the high-pressure steam turbine 121c is supplied from the extraction port 125 of the high-pressure steam turbine 121c to the outer side or the inner side of the first preheater 51 via the preheating steam supply line 61. On the other hand, the fuel F from the fuel supply source is supplied to the inner side or the outer side of the first preheater 51 through the fuel supply line 70. For this reason, in the first preheater 51, the fuel F from the fuel supply source and the high pressure steam HS from the high pressure steam turbine 121c exchange heat, and the fuel F is heated while the high pressure steam HS is cooled ( First preheating step).

  The high-pressure steam HS cooled by the first preheater 51 flows into the steam flow path 24 of the combustor 21 through the cooling steam line 62 as the cooling steam CS (cooling steam supply process). The cooling steam CS exchanges heat with the combustion cylinder 23 heated by the flame and the combustion gas in the process of passing through the steam flow path 24 to cool the combustion cylinder 23. On the other hand, the cooling steam CS is heated to become superheated steam SS.

  The superheated steam SS is supplied to the outside or inside of the pipe of the second preheater 52 through the superheated steam line 63. On the other hand, the fuel F heated by the first preheater 51 is supplied to the inner side or the outer side of the second preheater 52 via the first preheated fuel line 73. Therefore, in the second preheater 52, the fuel F heated by the first preheater 51 and the superheated steam SS, which is the cooling steam CS superheated by the combustion cylinder 23, exchange heat, and the fuel F is further heated. Meanwhile, the superheated steam SS is cooled (second preheating step).

  The fuel F further heated by the second preheater 52 is supplied to the injector 22 of the combustor 21 via the second preheat fuel line 74 (preheat fuel supply step). Further, the superheated steam SS cooled by the second preheater 52 flows into the high-pressure steam recovery line 139 via the preheated steam recovery line 64 as the recovered steam RS. That is, the high-pressure steam HS that is steam from the exhaust heat recovery apparatus 100 returns to the exhaust heat recovery apparatus 100.

  As described above, in the present embodiment, steam is supplied to the steam flow path 24 of the combustion cylinder 23 to cool the combustion cylinder 23, so that the gas turbine 10 of the gas turbine 10 extends along the inner peripheral surface of the combustion cylinder 23. The cooling efficiency of the combustion cylinder 23 and the efficiency of the gas turbine plant can be increased and the generation of NOx can be suppressed as compared with cooling the combustion cylinder 23 by supplying air extracted from the compressor 11.

  Specifically, since steam has a higher thermal conductivity and a larger heat capacity than air, the combustion cylinder 23 can be efficiently cooled. Further, when the compressed air is extracted from the compressor 11 of the gas turbine 10 and this air is used for cooling the combustion cylinder 23, the output of the gas turbine 10 is reduced and the output of the exhaust heat recovery device 100 is also reduced. As a result, the efficiency of the gas turbine plant is reduced. On the other hand, when the steam from the exhaust heat recovery device 100 is used for cooling the combustion cylinder 23 as in the present embodiment, the output of the exhaust heat recovery device 100 decreases, but the output of the gas turbine 10 does not decrease. Therefore, the use of the steam from the exhaust heat recovery device 100 for cooling the combustion cylinder 23 can suppress a decrease in the efficiency of the gas turbine plant, in other words, the efficiency of the gas turbine plant can be increased. Further, the average temperature at the outlet of the combustor 21, that is, the average temperature at the outlet of the combustion cylinder 23 is controlled to a constant temperature from the viewpoint of heat resistance and efficiency of the turbine 31. For this reason, when air is flowed along the inner peripheral surface of the combustion cylinder 23, it becomes necessary to increase the temperature at the center of the outlet opening of the combustion cylinder 23, the maximum temperature of the combustion gas increases, and the thermal NOx increases. To do. On the other hand, as in this embodiment, when steam flows through the steam flow path 24 of the combustion cylinder 23, the maximum temperature of the combustion gas can be suppressed by the amount of air that does not flow into the combustion gas, and generation of thermal NOx occurs. Can be suppressed.

  In the present embodiment, the high pressure steam HS from the high pressure steam turbine 121c and the fuel F from the fuel supply source are heat-exchanged by the first preheater 51, and after cooling the high pressure steam HS, the cooled high pressure steam is cooled. Since HS is supplied to the combustion cylinder 23 as cooling steam CS, the combustion cylinder 23 can be efficiently cooled also from this viewpoint.

  Further, in the present embodiment, the superheated steam SS that is superheated by the cooling of the combustor 21 and the fuel F are heat-exchanged by the second preheater 52 and the fuel F is heated. Heat, in other words, the heat of the combustor 21 can be used effectively. Therefore, in this embodiment, the efficiency of the gas turbine plant can be increased also from this viewpoint.

  By the way, in the technique described in Patent Document 1, the heat of the combustor is returned to the steam of the exhaust heat recovery device to increase the efficiency of the exhaust heat recovery device, but the efficiency of the gas turbine cannot be increased. On the other hand, in this embodiment, since the heat of the combustor 21 is used for preheating the fuel F, the efficiency of both the gas turbine 10 and the exhaust heat recovery device 100 can be improved. The efficiency of the plant can be increased.

  Moreover, in this embodiment, since the 1st preheater 51 and the 2nd preheater 52 are located in a line with the fuel F in series, the temperature of the fuel F can be made high. In particular, when the temperature of the superheated steam SS supplied to the second preheater 52 is higher than the temperature of the high pressure steam HS supplied to the first preheater 51, the temperature of the fuel is increased more efficiently. be able to.

  Furthermore, in this embodiment, since the superheated steam SS cooled by the heat exchange with the fuel F in the second preheater 52 is returned to the exhaust heat recovery device 100, the high-temperature components are cooled as in Patent Document 1. The amount of heat release in the process of returning the steam to the exhaust heat recovery device 100 can be made smaller than returning the superheated steam to the exhaust heat recovery device. Moreover, the heat resistance of the piping that returns the steam to the exhaust heat recovery apparatus 100 can be lowered, and the equipment cost can be reduced.

"Second embodiment"
Next, a second embodiment of the gas turbine plant according to the present invention will be described with reference to FIG. The second embodiment, the third embodiment, and the fourth embodiment described below are modifications of the fuel preheating device 50 of the first embodiment, and other configurations are basically the same. It is. Therefore, in the description of the second embodiment, the third embodiment, and the fourth embodiment, the fuel preheating device will be mainly described.

  The fuel preheating device 50a of this embodiment is obtained by adding a third preheater 53 to the fuel preheating device 50 of the first embodiment. For this reason, the preheating fuel line 71a and the preheating medium line 60a of this embodiment are somewhat different from the first embodiment.

  A fuel supply line 70 extending from the fuel supply source is connected to the inlet of the third preheater 53 on the inside or outside of the tube. The preheating fuel line 71a of the present embodiment has a third preheating fuel line 72 in addition to the first preheating fuel line 73 and the second preheating fuel line 74 in the first embodiment. The third preheating fuel line 72 connects the outlet on the inner side or the outer side of the third preheater 53 and the inlet on the inner side or the outer side of the pipe of the first preheater 51.

  The preheating medium line 60a of this embodiment includes preheating water in addition to the preheating steam supply line (first preheating medium line) 61, the cooling steam line 62, the superheated steam line 63, and the preheated steam recovery line 64 in the first embodiment. A supply line (second preheating medium line) 65 and a preheated water recovery line 66 are provided. The preheated water supply line 65 connects the medium pressure economizer 112 b of the exhaust heat recovery boiler 110 and the inlet of the third preheater 53 on the outer side or the inner side of the pipe. Further, the preheated water recovery line 66 connects the outlet of the third preheater 53 on the outer side or the inner side of the pipe and the water supply line 131 of the exhaust heat recovery device 100.

  In the present embodiment, the heated water HW supplied to the third preheater 53 via the preheated water supply line 65, the high pressure steam HS supplied to the first preheater 51 via the preheated steam supply line 61, and superheat. Of the superheated steam SS supplied to the second preheater 52 via the steam line 63, the temperature of the heated water HW supplied to the third preheater 53 is the lowest, and then supplied to the first preheater 51. It is assumed that the temperature of the high-pressure steam HS is low and the temperature of the superheated steam SS supplied to the second preheater 52 is the highest.

  In the present embodiment, a part of the heated water HW heated by the medium pressure economizer 112 b of the exhaust heat recovery boiler 110 is supplied to the outside or inside of the third preheater 53 via the preheated water supply line 65. The On the other hand, the fuel F from the fuel supply source is supplied to the inner side or the outer side of the third preheater 53 via the fuel supply line 70. In the third preheater 53, the fuel F from the fuel supply source and the heated water HW from the intermediate pressure economizer 112b exchange heat, and the fuel F is heated while the heated water from the intermediate pressure economizer 112b is heated. The HW is cooled. The cooled heated water HW returns to the discharge side of the feed water pump 124 in the feed water line 131 via the preheated water recovery line 66.

  The fuel F heated by the third preheater 53 is heated by the first preheater 51 with the high-pressure steam HS having a temperature higher than that of the heated water HW from the medium pressure economizer 112b. The fuel F heated by the first preheater 51 is further heated by the second preheater 52 by the superheated steam SS having a temperature higher than that of the high-pressure steam HS. The fuel F heated by the second preheater 52 is supplied to the combustor 21.

  As mentioned above, since the fuel preheating apparatus 50a of this embodiment is provided with the fuel preheating apparatus 50 of 1st embodiment, the effect similar to 1st embodiment can be acquired. Furthermore, since the fuel preheating device 50a of the present embodiment includes the third preheater 53, the temperature of the fuel F can be further increased.

  In the present embodiment, the fuel F is sequentially heated from the preheating medium having a low temperature to the preheating medium having a high temperature. Therefore, in the present embodiment, the fuel F can be heated to a higher temperature and more efficiently than when the fuel F is sequentially heated from a high temperature preheating medium to a low temperature preheating medium.

"Third embodiment"
Next, a third embodiment of the gas turbine plant according to the present invention will be described with reference to FIG.

  The fuel preheating device 50b of the present embodiment is also obtained by adding a third preheater 53 to the fuel preheating device 50 of the first embodiment. For this reason, the preheating fuel line 71b and the preheating medium line 60b of this embodiment are also somewhat different from the first embodiment.

  A fuel supply line 70 extending from the fuel supply source is connected to the inlet of the third preheater 53 on the inner side or the outer side of the pipe, as in the second embodiment. In addition, a preheated water supply line 65 and a preheated water recovery line 66 are connected to the outer side or the inner side of the third preheater 53. The preheating fuel line 71b of the present embodiment includes a third preheating fuel line 72b and an integrated preheating fuel line 75b. The third preheating fuel line 72 b connects the outlet inside or outside the tube of the third preheater 53 and the inlet inside or outside the tube of the first preheater 51 and the second preheater 52. Further, the integrated preheating fuel line 75 b connects the outlet of the first preheater 51 and the second preheater 52 inside or outside the tube and the combustor 21.

  In the present embodiment, the heated water HW supplied to the third preheater 53 via the preheated water supply line 65, the high pressure steam HS supplied to the first preheater 51 via the preheated steam supply line 61, and superheat. Among the superheated steam SS supplied to the second preheater 52 via the steam line 63, the temperature of the heated water HW supplied to the third preheater 53 is the lowest, and the high pressure steam supplied to the first preheater 51. It is assumed that the temperature of HS and the temperature of superheated steam SS supplied to the second preheater 52 are substantially the same.

  In the present embodiment, as in the second embodiment, a part of the heated water HW from the medium pressure economizer 112 b of the exhaust heat recovery boiler 110 is outside the pipe of the third preheater 53 via the preheated water supply line 65. Or it is supplied inside the pipe. Further, the fuel F from the fuel supply source is supplied through the fuel supply line 70 to the inside or outside of the tube of the third preheater 53. In the third preheater 53, the fuel F from the fuel supply source and the heated water HW from the intermediate pressure economizer 112b exchange heat, and the fuel F is heated while the heated water from the intermediate pressure economizer 112b is heated. The HW is cooled. The cooled heated water HW returns to the discharge side of the feed water pump 124 in the feed water line 131 via the preheated water recovery line 66.

  The fuel F heated by the third preheater 53 is supplied to each of the first preheater 51 and the second preheater 52 via the third preheat fuel line 72b. Part of the fuel F heated by the third preheater 53 is heated by the first preheater 51 with the high-pressure steam HS having a temperature higher than that of the heated water HW from the intermediate pressure economizer 112b. Further, the remaining part of the fuel F heated by the third preheater 53 is the second preheater 52 and has a temperature higher than that of the heated water HW from the intermediate pressure economizer 112b and substantially the same as the high pressure steam HS. Heated with superheated steam SS at temperature. The fuel F heated by the first preheater 51 and the second preheater 52 is supplied to the combustor 21 via the integrated preheat fuel line 75b.

  As described above, in the present embodiment, similarly to the first embodiment, the cooling steam CS that is the steam cooled by the heat exchange with the fuel F in the first preheater 51 is supplied to the combustor 21. Since the superheated steam SS, which is the superheated steam by the heat exchange, is supplied to the second preheater 52, the same effect as in the first embodiment can be obtained.

  In the present embodiment, the temperature of the high-pressure steam HS supplied to the first preheater 51 and the temperature of the superheated steam SS supplied to the second preheater 52 are substantially the same. By supplying the preheated fuel F to the first preheater 51 and the second preheater 52 in parallel, the preheating efficiency of the fuel F can be increased.

"Fourth embodiment"
Next, a fourth embodiment of the gas turbine plant according to the present invention will be described with reference to FIG.

  The fuel preheating device 50c of the present embodiment is also obtained by adding a third preheater 53 to the fuel preheating device 50 of the first embodiment. For this reason, the preheating fuel line 71c and the preheating medium line 60c of this embodiment are also slightly different from the first embodiment.

  Fuel supply lines 70c extending from the fuel supply source are branched and connected to the inlets inside or outside the tubes of the first preheater 51, the second preheater 52, and the third preheater 53, respectively. As in the second and third embodiments, a preheat water supply line 65 and a preheat water recovery line 66 are connected to the outer side or the inner side of the third preheater 53. The preheating fuel line 71c of this embodiment has an integrated preheating fuel line 75c. The integrated preheating fuel line 75 c connects the combustor 21 with the outlets inside or outside the tubes of the first preheater 51, the second preheater 52, and the third preheater 53.

  In the present embodiment, the heated water HW supplied to the third preheater 53 via the preheated water supply line 65, the high pressure steam HS supplied to the first preheater 51 via the preheated steam supply line 61, and superheat. It is assumed that the temperatures of the superheated steam SS supplied to the second preheater 52 via the steam line 63 are substantially the same.

  In the present embodiment, part of the heated water HW from the medium pressure economizer 112 b of the exhaust heat recovery boiler 110 is supplied to the outside or inside of the third preheater 53 via the preheated water supply line 65. Further, a part of the fuel F from the fuel supply source is supplied to the inner side or the outer side of the third preheater 53 via the fuel supply line 70c. In the third preheater 53, the fuel F from the fuel supply source and the heated water HW from the intermediate pressure economizer 112b exchange heat, and the fuel F is heated while the heated water from the intermediate pressure economizer 112b is heated. The HW is cooled.

  A part of the fuel F from the fuel supply source is also supplied via the fuel supply line 70 c to the inside or outside of the pipe of the first preheater 51. In the first preheater 51, the fuel F from the fuel supply source is heated by the high-pressure steam HS having substantially the same temperature as the heated water HW from the medium pressure economizer 112b. Further, the remaining part of the fuel F from the fuel supply source is supplied to the inner side or the outer side of the second preheater 52 via the fuel supply line 70c. In the second preheater 52, the fuel F from the fuel supply source is heated by the superheated steam SS having substantially the same temperature as the heated water HW from the medium pressure economizer 112b.

  In the present embodiment, similarly to the above embodiments, the cooling steam CS that is the steam cooled by the heat exchange with the fuel F in the first preheater 51 is supplied to the combustor 21. Superheated steam SS that is superheated by heat exchange is supplied to the second preheater 52.

  The fuel F heated by the first preheater 51, the second preheater 52, and the third preheater 53 is supplied to the combustor 21 via the integrated preheat fuel line 75c.

  As described above, in the present embodiment, similarly to the first embodiment, the cooling steam CS that is the steam cooled by the heat exchange with the fuel F in the first preheater 51 is supplied to the combustor 21. Since the superheated steam SS, which is the superheated steam by the heat exchange, is supplied to the second preheater 52, the same effect as in the first embodiment can be obtained.

  In the present embodiment, the temperature of the high-pressure steam HS supplied to the first preheater 51, the temperature of the superheated steam SS supplied to the second preheater 52, and the heating water HW supplied to the third preheater 53 are also shown. Since the temperature is substantially the same, the fuel F from the fuel supply source is supplied in parallel to the first preheater 51, the second preheater 52, and the third preheater 53, so that the preheating efficiency of the fuel F is increased. Can be increased.

"Fifth embodiment"
Next, a fifth embodiment of the gas turbine plant according to the present invention will be described with reference to FIG.

  Similarly to the above embodiment, the gas turbine plant of this embodiment also generates steam by the heat of the gas turbine 10, the generator 15 that generates power by driving the gas turbine 10, and the exhaust gas EG exhausted from the gas turbine 10. An exhaust heat recovery device 100d to be discharged, a chimney 40 that discharges the exhaust gas EG that has passed through the exhaust heat recovery device 100d to the atmosphere, and a fuel preheating device 50a that preheats the fuel F supplied to the gas turbine 10.

  The gas turbine plant of the present embodiment is the same as the gas turbine plant of the second embodiment except for the exhaust heat recovery device 100d.

  The exhaust heat recovery apparatus 100d of the present embodiment includes an exhaust heat recovery boiler 110d that generates steam by the heat of the exhaust gas EG exhausted from the gas turbine 10, and various steam using devices 150a that generate steam generated by the exhaust heat recovery boiler 110d. , 150c, steam supply lines 151a, 151c, a condenser 153 for returning the steam from the various steam using devices 150a, 150c to water, and a water supply pump 124 for returning the water in the condenser 153 to the exhaust heat recovery boiler 110d. And.

  The exhaust heat recovery boiler 110d has a low-pressure steam generator 111a that generates low-pressure steam LS and a high-pressure steam generator 111c that generates high-pressure steam HS.

  The low-pressure steam generator 111a superheats the low-pressure economizer 112a that heats water, the low-pressure evaporator 113a that converts water heated by the low-pressure economizer 112a into steam, and the steam generated by the low-pressure evaporator 113a. And a low-pressure superheater 114a that generates low-pressure steam LS.

  The high-pressure steam generator 111c includes a high-pressure pump 116c that pressurizes water heated by the low-pressure economizer 112a, a high-pressure economizer 112c that heats water pressurized by the high-pressure pump 116c, and a high-pressure economizer 112c. It has a high-pressure evaporator 113c that turns heated water into steam, and a high-pressure superheater 114c that superheats the steam generated in the high-pressure evaporator 113c to generate high-pressure steam HS.

  Examples of the various steam using devices 150a and 150c include a high pressure steam using device 150c that uses the high pressure steam HS and a low pressure steam using device 150a that uses the low pressure steam LS. Examples of the high-pressure steam utilization device 150c include a heater that heats materials and the like in a factory with the high-pressure steam HS, and a reaction tower that reacts the materials and the high-pressure steam HS in the factory. Examples of the low-pressure steam using device 150a include a water heater, a heater, an absorption refrigerator, and the like.

  The condenser 153 and the low pressure economizer 112 a are connected by a water supply line 131. The water supply line 131 is provided with a water supply pump 124. The low pressure superheater 114a and the low pressure steam utilization device 150a are connected by a low pressure steam supply line 151a. Moreover, the high pressure superheater 114c and the high pressure steam utilization apparatus 150c are connected by the high pressure steam supply line 151c. The low-pressure steam utilization device 150a and the condenser 153 are connected by a low-pressure steam recovery line 152a. The high-pressure steam utilization device 150c and the condenser 153 are connected by a high-pressure steam recovery line 152c.

  The preheating steam supply line 61 in the fuel preheating device 50a of this embodiment is connected to the high-pressure steam supply line 151c. The preheated steam recovery line 64 is connected to a line connecting the low pressure evaporator 113a and the low pressure superheater 114a of the low pressure steam generator 111a. The preheated water supply line 65 is connected to a line connecting the high pressure economizer 112c and the high pressure evaporator 113c of the high pressure steam generator 111c. The preheated water recovery line 66 is connected to the water supply line 131 as in the second embodiment.

  As mentioned above, since the gas turbine plant of this embodiment is also provided with the fuel preheating apparatus 50a of 2nd embodiment, the effect similar to 2nd embodiment can be acquired fundamentally.

  As described above, the exhaust heat recovery device of the gas turbine plant may not have the steam turbine as long as it has the steam generation unit. Therefore, the exhaust heat recovery apparatus 100 of the gas turbine plant of the first embodiment, the third embodiment, and the fourth embodiment may not include the steam turbine.

  In addition, the exhaust heat recovery boilers 110 and 110d of each of the above embodiments including this embodiment have a plurality of steam generation units, but it is only necessary to have one steam generation unit. In the case of having only one steam generation part, for example, the steam from the superheater of this steam generation part is supplied to the first preheater 51, and the water heated by the economizer of this steam generation part is The three preheaters 53 may be supplied.

`` Various modifications ''
In the fuel preheating devices of the first to fourth embodiments, the high pressure steam HS extracted from the high pressure steam turbine 121c is supplied to the first preheater 51, and is the superheated steam SS after cooling exhausted from the second preheater 52. The recovered steam RS is returned to the high-pressure steam recovery line 139. However, the high pressure steam HS in the high pressure steam line 138, the medium pressure steam IS in the medium pressure steam line 133, and the like may be supplied to the first preheater 51. Further, the recovered steam RS exhausted from the second preheater 52 may be returned to a line connecting the first reheater 115a and the second reheater 115b. That is, the steam supplied to the first preheater 51 is acquired from any location in the steam flow path of the exhaust heat recovery apparatus 100 as long as the pressure and temperature conditions as the supply steam to the first preheater 51 are satisfied. Also good. Similarly, in the steam flow path of the exhaust heat recovery apparatus 100, the second preheater can be placed at any location as long as the pressure, temperature conditions, and the like as a location for returning the recovered steam RS exhausted from the second preheater 52 are satisfied. The recovered steam RS exhausted from 52 may be returned.

  In the fuel preheating devices of the second to fifth embodiments, the heated water HW is supplied to the third preheater 53, but steam may be supplied instead of the heated water HW.

  In each of the embodiments described above, in the second preheater 52, the superheated steam SS is cooled by heat exchange between the fuel F and the superheated steam SS, but the recovered steam RS from the second preheater 52 remains as a gas vapor. As exhausted. However, the second preheater 52 may condense the superheated steam SS. In this case, the heat of the superheated steam SS can be sufficiently utilized for preheating the fuel F. Furthermore, in this case, by condensing the superheated steam SS by heat exchange with the fuel F, the heat exchange rate between the superheated steam SS and the fuel F increases, and the second preheater 52 can be downsized. In addition, the water obtained by the condensation of the superheated steam SS is returned to the condenser 123, for example.

  In each of the above embodiments, the combustion cylinder 23 of the combustor 21 in the gas turbine 10 is cooled by the cooling steam CS. However, if the components constituting the gas turbine 10 are high-temperature components that are in contact with the combustion gas, for example, of the rotor blades 34 and the stationary blades 36 of the turbine 31 (shown in FIG. 2), and the inner peripheral surface of the turbine casing 35. The high temperature parts such as the split ring constituting the portion facing the moving blade 34 may be cooled by the cooling steam CS. In this case, a steam channel is formed in a high-temperature component such as the moving blade 34 or the stationary blade 36 of the turbine 31, and the cooling steam line 62 is connected to one end of the steam channel.

  Further, the gas turbine plant of each of the above embodiments includes an exhaust heat recovery device. However, the gas turbine plant may be provided with a steam generation source, and the exhaust heat recovery device may not be provided. That is, the steam generation source in the gas turbine plant may be a heat source different from the exhaust gas from the gas turbine 10, for example, a boiler that generates steam by heat generated by separately burning fuel.

  10: Gas turbine, 11: Compressor, 21: Combustor 21, 22: Injector, 23: Combustion cylinder (high temperature part), 24: Steam flow path, 31: Turbine, 32: Turbine rotor, 33: Rotor blade, 35: turbine casing, 36: stationary blade, 40: chimney, 50, 50a, 50b, 50c: fuel preheater, 51: first preheater, 52: second preheater, 53: third preheater, 60, 60a , 60b, 60c: Preheating medium line, 61: Preheating steam supply line (first preheating medium line), 62: Cooling steam line, 63: Superheated steam line, 64: Preheating steam recovery line, 65: Preheating water supply line (No. 1) Two preheating medium lines), 66: preheated water recovery line, 70, 70c: fuel supply line, 71, 71a, 71b, 71c: preheated fuel line, 72, 72b: third preheated fuel line, 73: first preheated fuel IN, 74: second preheating fuel line, 75b, 75c: integrated preheating fuel line, 100, 100d: exhaust heat recovery device, 110, 110d: exhaust heat recovery boiler, 111a: low pressure steam generator, 111b: medium pressure steam generation Part, 111c: high-pressure steam generating part, 115: reheating part, 121a: low-pressure steam turbine, 121b: medium-pressure steam turbine, 121c: high-pressure steam turbine, 123, 153: condenser, 131: water supply line, 133: medium Pressure steam line, 136: Reheat steam line, 138: High pressure steam line, 139: High pressure steam recovery line, 150a: Low pressure steam utilization equipment, 150c: High pressure steam utilization equipment, 151a: Low pressure steam supply line, 151c: High pressure steam supply Line, 152a: low pressure steam recovery line, 152c: high pressure steam recovery line

Claims (10)

A first preheater that preheats the fuel by exchanging heat between the steam and the fuel, and the steam cooled by the preheating of the fuel flows out as cooling steam;
A cooling steam line for supplying the cooling steam to any one of a combustor that burns fuel to generate combustion gas and a turbine that is driven by the combustion gas and that is in contact with the combustion gas When,
A superheated steam line through which the superheated steam that is the cooling steam that has passed through the high-temperature component passes;
A second preheater for preheating the fuel by exchanging heat between the superheated steam supplied from the superheated steam line and the fuel;
A preheat fuel line for supplying the fuel preheated by the first preheater and the second preheater to the combustor;
A preheating device for gas turbine fuel, comprising: In the gas turbine fuel preheating device according to claim 1,
The preheat fuel line includes a first preheat fuel line that supplies the fuel preheated by the first preheater to the second preheater, and the fuel further preheated by the second preheater to the combustor. A second preheating fuel line to supply,
A gas turbine fuel preheating apparatus. In the gas turbine fuel preheating device according to claim 1,
The preheat fuel line has an integrated preheat fuel line that receives the fuel preheated by the first preheater and the fuel preheated by the second preheater and supplies the fuel to the combustor, respectively.
A gas turbine fuel preheating apparatus. In the gas turbine fuel preheating device according to any one of claims 1 to 3,
A third preheater for preheating the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium;
A gas turbine fuel preheating apparatus. In the gas turbine fuel preheating device according to claim 2,
A third preheater for preheating the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium;
The preheat fuel line has a third preheat fuel line that supplies the fuel preheated by the third preheater to the first preheater.
A gas turbine fuel preheating apparatus. In the gas turbine fuel preheating device according to claim 3,
A third preheater for preheating the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium;
The preheat fuel line includes a third preheat fuel line that supplies the fuel preheated by the third preheater to each of the first preheater and the second preheater.
A gas turbine fuel preheating apparatus. In the gas turbine fuel preheating device according to claim 3,
A third preheater for preheating the fuel by exchanging heat between the fuel supplied to the combustor and a preheating medium;
The integrated preheat fuel line supplies the fuel preheated by the third preheater to the combustor together with the fuel preheated by the first preheater and the fuel preheated by the second preheater. To
A gas turbine fuel preheating apparatus. A preheating device for a gas turbine fuel according to any one of claims 1 to 7,
A gas turbine having the combustor and the turbine;
An exhaust heat recovery apparatus having an exhaust heat recovery boiler that generates steam by the heat of exhaust gas from the turbine;
With
The preheating device has a preheating medium line for supplying steam in the exhaust heat recovery device to the first preheater.
A gas turbine plant characterized by that. A preheating device for a gas turbine fuel according to any one of claims 4 to 7,
A gas turbine having the combustor and the turbine;
An exhaust heat recovery apparatus having an exhaust heat recovery boiler that generates steam by the heat of exhaust gas from the turbine;
With
The preheating device includes a first preheating medium line that supplies the steam in the exhaust heat recovery device to the first preheater, and a second that supplies the steam or water in the exhaust heat recovery device to the third preheater. A preheating medium line,
A gas turbine plant characterized by that. A first preheating step in which heat is exchanged between the steam and the fuel to preheat the fuel, and the steam cooled by the preheating of the fuel flows out as cooling steam;
Cooling steam supply for supplying the cooling steam to any one of a combustor that burns fuel to generate combustion gas and a turbine that is driven by the combustion gas and that is in contact with the combustion gas Process,
A second preheating step of preheating the fuel by exchanging heat between the superheated steam that is the cooling steam that has passed through the high-temperature component and the fuel supplied to the combustor;
A preheating fuel supply step for supplying the fuel preheated in the first preheating step and the second preheating step to the combustor;
A method for preheating gas turbine fuel, characterized in that

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