KR20220136289A - Combined power plant and operating method of the same - Google Patents

Abstract

A complex power generation system according to one aspect of the present invention comprises: a gas turbine which combusts fuel to produce rotating force; an exhaust heat recovery boiler which uses combustion gas discharged from the gas turbine to heat water; a fuel preheater which heats fuel supplied to the gas turbine and has a first heating unit and a second heating unit which are arranged in parallel; a water supply pipe which is connected to the exhaust heat recovery boiler to supply a high-pressure water to the fuel preheater; a first branching pipe which is connected to the water supply pipe to deliver water to the first heating unit; and a second branching pipe which is connected to the water supply pipe to deliver water to the second heating unit. Here, the water supplied by means of the high-pressure water supply pipe is made of liquid, and the phase of the water may not be changed in the fuel preheater. Therefore, fuel supplied to the gas turbine may be efficiently preheated.

Description

Combined power generation system and method of driving combined power generation system

The present invention relates to a combined power generation system and a method of driving the combined power generation system. More particularly, the present invention relates to a combined power generation system having a gas turbine and a fuel preheater and a method of driving the combined power generation system.

The combined cycle power generation system is a power generation system that combines a gas turbine and a steam turbine with high efficiency to guide high-temperature exhaust gas from the gas turbine to a heat recovery boiler (HRSG) and generate steam by thermal energy retained in the exhaust gas. This steam enables power generation by the steam turbine and can be combined with the power generated by the gas turbine to improve thermal efficiency equivalent to the thermal energy retained in the exhaust gas when compared to independent power production by the gas turbine. .

A gas turbine is a power engine that mixes and burns compressed air and fuel compressed in a compressor, and rotates the turbine with high-temperature gas generated by combustion. Gas turbines are used to power generators, aircraft, ships, trains, and the like.

In order to improve the efficiency of the gas turbine, it is necessary to preheat the fuel flowing into the gas turbine. As the fuel is preheated to a high temperature, the temperature of the gas turbine increases. However, if the fuel is overheated, a problem of carbonization due to thermal decomposition may occur during the preheating of the fuel.

Based on the technical background as described above, the present invention provides a combined cycle power generation system capable of efficiently preheating fuel supplied to a gas turbine and a method of driving the combined cycle power generation system.

A combined cycle power generation system according to an aspect of the present invention includes a gas turbine generating rotational force by burning fuel, a heat recovery boiler that heats feedwater using combustion gas discharged from the gas turbine, and heating the fuel supplied to the gas turbine. and a fuel preheater having a primary and secondary heating unit arranged in parallel, a water supply pipe connected to the heat recovery boiler to supply high-pressure water to the fuel preheater, and a water supply pipe connected to the primary heating unit to deliver water supply a first branch pipe, and a secondary branch pipe connected to the water supply pipe to deliver water supply to the secondary heating unit, wherein the supply water supplied through the high-pressure water supply pipe consists of a liquid, and the water supply from the fuel preheater may be invariant.

A first discharge pipe connected to the primary heating unit according to an aspect of the present invention to move the water supply discharged from the primary heating unit, and connected to the secondary heating unit to move the water supply discharged from the secondary heating unit It may further include a second discharge pipe, and a feed water recovery pipe connected to the first discharge pipe and the second discharge pipe to deliver feed water to the exhaust heat recovery boiler.

A first control valve for controlling the flow rate of feed water flowing into the primary heating unit is installed in the first discharge pipe according to an aspect of the present invention, and the second discharge pipe controls the flow rate of water supply flowing into the secondary heating unit A second control valve may be installed.

The combined power generation system comprising according to an aspect of the present invention connects the upstream of the primary heating unit and the downstream of the primary heating unit, and a first bypass pipe and the first bypass pipe for moving fuel by bypassing the primary heating unit A first fuel control valve for controlling a flow rate of fuel moving through the bypass pipe may be further included.

By connecting the upstream of the secondary heating unit and the downstream of the secondary heating unit according to an aspect of the present invention, the second bypass pipe bypasses the secondary heating unit and moves fuel through the second bypass pipe and the second bypass pipe It may further include a second fuel control valve for controlling the flow rate of the fuel.

The fuel preheater according to an aspect of the present invention may further include a pre-heater connected to the water supply return pipe and supplied with water discharged from the primary heating unit and the secondary heating unit to heat the fuel in advance. .

A combined power generation system in which a downstream control valve for controlling the flow rate of feed water discharged from the pre-heater is installed on a downstream side of the pre-heater according to an aspect of the present invention.

A water supply control pipe for supplying water to the pre-heater is connected to the pre-heater according to an aspect of the present invention, and an intermediate pressure control valve for controlling the flow rate of water supplied from the water supply control pipe is installed in the water supply control pipe. can

According to an aspect of the present invention, there is provided a method of driving a combined cycle power generation system including a gas turbine, a steam turbine, a heat recovery boiler, and a fuel preheater having a primary heating unit and a secondary heating unit for preheating fuel, in the heat recovery boiler A fuel preheating step of dividing the heated water supply and supplying it to the primary heating unit and the secondary heating unit installed in parallel, measuring the temperature of the supply water discharged from the primary heating unit and the secondary heating unit, and a preset reference temperature Comparing with the feed water temperature determining step, and fuel temperature control for controlling the temperature of the fuel using the first control valve and the second control valve for controlling the movement of the feed water discharged from the primary heating unit and the secondary heating unit step, wherein the feed water supplied in the fuel preheating step may be made of a liquid, and a phase of the feed water may be constant during the fuel preheating process.

In the fuel temperature control step according to an aspect of the present invention, when the temperature of the fuel discharged from the primary heating unit is lower than a preset first reference temperature, the opening degree of the first control valve installed on the downstream side of the primary heating unit , and when the temperature of the fuel discharged from the primary heating unit is higher than the first reference temperature, the opening degree of the first control valve may be decreased.

In the fuel temperature control step according to an aspect of the present invention, when the temperature of the fuel discharged from the secondary heating unit is lower than a preset second reference temperature, the opening degree of the second control valve installed on the downstream side of the secondary heating unit , and when the temperature of the fuel discharged from the secondary heating unit is higher than the first reference temperature, the opening degree of the second control valve may be decreased.

The fuel temperature control step according to an aspect of the present invention includes a first control valve installed on a downstream side of the primary heating unit and a first bypass pipe for supplying fuel to a downstream side of the primary heating unit by bypassing the primary heating unit. The temperature of the fuel is controlled by adjusting the first fuel control valve installed in the and, when the first fuel control valve is closed, the opening degree of the first control valve may be increased.

In the fuel temperature control step according to an aspect of the present invention, when the temperature of the fuel discharged from the primary heating unit is higher than the first reference temperature, the opening degree of the first fuel control valve is increased, and the first fuel When the control valve is fully opened, the opening degree of the first control valve may be reduced.

The fuel temperature control step according to an aspect of the present invention includes a second control valve installed on the downstream side of the secondary heating unit and a second bypass pipe for supplying fuel to the downstream side of the secondary heating unit by bypassing the secondary heating unit. The temperature of the fuel is controlled by adjusting the second fuel control valve installed in the When the second fuel control valve is closed, the opening degree of the second control valve is increased, and when the temperature of the fuel discharged from the secondary heating unit is higher than the second reference temperature, the second fuel control valve is The opening degree may be increased, and if the second fuel control valve is fully opened, the opening degree of the first control valve may be decreased.

In the fuel preheating step according to an aspect of the present invention, the preheated fuel is heated after preheating the fuel using a pre-heater that receives the supply water discharged from the primary heating unit and the secondary heating unit and heats the fuel in advance. It is possible to reduce the supply to the primary heating unit and the secondary heating unit.

As described above, in the combined cycle power generation system according to an aspect of the present invention, the primary heating unit and the secondary heating unit are installed in parallel to divide the water supply of the high-pressure unit and supply the primary heating unit and the secondary heating unit to efficiently supply fuel. can be heated with

1 is a configuration diagram illustrating a combined power generation system according to a first embodiment of the present invention.
2 is a block diagram illustrating a fuel preheater and a heat recovery boiler according to the first embodiment of the present invention.
3 is a configuration diagram illustrating a fuel preheater according to a first embodiment of the present invention.
4 is a flowchart illustrating a method of driving the combined cycle power generation system according to the first embodiment of the present invention.
5 is a configuration diagram illustrating a fuel preheater according to a second embodiment of the present invention.
6 is a block diagram illustrating a fuel preheater and a heat recovery boiler according to a third embodiment of the present invention.
7 is a configuration diagram illustrating a fuel preheater according to a third embodiment of the present invention.

Since the present invention can apply various transformations and can have various embodiments, specific embodiments are illustrated and described in detail in the detailed description. However, this is not intended to limit the present invention to specific embodiments, and should be understood to include all modifications, equivalents, and substitutes included in the spirit and scope of the present invention.

The terms used in the present invention are only used to describe specific embodiments, and are not intended to limit the present invention. The singular expression includes the plural expression unless the context clearly dictates otherwise. In the present invention, terms such as 'comprise' or 'have' are intended to designate that the features, numbers, steps, operations, components, parts, or combinations thereof described in the specification exist, and one or more other features It is to be understood that this does not preclude the possibility of the presence or addition of numbers, steps, operations, components, parts, or combinations thereof.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. At this time, it should be noted that in the accompanying drawings, the same components are denoted by the same reference numerals as much as possible. In addition, detailed descriptions of well-known functions and configurations that may obscure the gist of the present invention will be omitted. For the same reason, some components are exaggerated, omitted, or schematically illustrated in the accompanying drawings.

Hereinafter, a gas turbine according to a first embodiment of the present invention will be described.

1 is a configuration diagram showing a combined cycle power generation system according to a first embodiment of the present invention, FIG. 2 is a configuration diagram showing a fuel preheater and a heat recovery boiler according to the first embodiment of the present invention, and FIG. 3 is A configuration diagram illustrating a fuel preheater according to a first embodiment of the present invention.

1 to 3 , the combined cycle power generation system 100 according to the first embodiment includes a plurality of turbines to generate electric power. The combined cycle power system 100 includes a gas turbine 110 , a generator 130 , a heat recovery boiler 140 , a steam turbine 120 , a fuel preheater 150 , a water supply pipe 153 , a first branch pipe 154 , It may include a second branch pipe 155 , a first control valve 161 , and a second control valve 162 .

The gas turbine 110 according to this embodiment sucks atmospheric air, compresses it to a high pressure, burns fuel in a static pressure environment to release thermal energy, expands this high temperature combustion gas to convert it into kinetic energy, and then converts the residual energy into kinetic energy. Exhaust gases containing

The gas turbine 110 may include a compressor 112 , a combustor 115 , and a main turbine 113 . The compressor 112 of the gas turbine 110 may suck air from the outside and compress it. The compressor 112 may supply compressed air compressed by the compressor blades to the combustor 115 , and may also supply cooling air to a high temperature region requiring cooling in the gas turbine 110 . At this time, since the sucked air undergoes an adiabatic compression process in the compressor 112 , the pressure and temperature of the air passing through the compressor 112 are increased.

The compressor 112 is designed as centrifugal compressors or axial compressors. A centrifugal compressor is applied to a small gas turbine, whereas a multi-stage axial compressor is applied to the same large gas turbine 110 .

On the other hand, the combustor 115 may mix the compressed air supplied from the outlet of the compressor 112 with the fuel and perform isostatic combustion to produce combustion gas of high energy.

The high-temperature, high-pressure combustion gas produced in the combustor 115 is supplied to the main turbine 113 . In the main turbine 113, the thermal energy of the combustion gas is converted into mechanical energy in which the rotating shaft rotates by colliding with a plurality of blades radially disposed on the rotating shaft of the main turbine 113 while the combustion gas expands adiabatically, and by giving a reaction force. A part of the mechanical energy obtained from the main turbine 113 is supplied as energy required to compress the air in the compressor 112 , and the remainder is utilized as effective energy such as driving the generator 130 to generate electric power.

The combustion gas discharged from the main turbine 113 is cooled through the heat recovery boiler 140 and then purified and discharged to the outside. The heat recovery boiler 140 not only cools the combustion gas, but also generates high-temperature and high-pressure steam using the heat of the combustion gas and delivers it to the steam turbine 120 .

The steam generated in the heat recovery boiler 140 is transmitted to the steam turbine 120 through the steam supply line 181 , and the feed water cooled in the steam turbine 120 is transferred to the heat recovery boiler through the turbine feed water recovery line 182 . (140).

The steam turbine 120 rotates blades using the steam generated by the heat recovery boiler 140 and transfers rotational energy to the generator 130 . The steam turbine 120 supplies the cooled steam back to the heat recovery boiler 140 .

In the first embodiment, the main turbine 113 and the steam turbine 120 are exemplified as being connected to one generator 130, but the present invention is not limited thereto, and the steam turbine 120 and the main turbine 113 are not limited thereto. ) can be placed in parallel and connected to different generators.

The turbine feedwater recovery line 182 includes a condenser 121 for condensing steam, a condensate storage tank 122 for storing condensed feedwater, and a condensate pump 123 for supplying the condensed water stored in the condensed water storage tank 122 to the heat recovery boiler. can be installed.

The steam moving inside the heat recovery boiler 140 may have a pressure of two or three stages, and accordingly, the feed water is pressurized to two or three or more pressure levels. In this embodiment, the heat recovery boiler 140 is exemplified as having three stages of pressure.

The heat recovery boiler 140 may include a low-pressure part G1 having a relatively low pressure, a medium-pressure part G2 having a medium pressure, and a high-pressure part G3 having a relatively high pressure. The high-pressure part (G3) is disposed adjacent to the inlet side where the combustion gas is introduced and is heated by the high-temperature combustion gas, and the low-pressure part (G1) is disposed adjacent to the exit side where the combustion gas is discharged and is heated by the low-temperature combustion gas. can be

Inside the heat recovery boiler 140, a condensate preheater 141, a low pressure evaporator 142, a medium pressure economizer 143, a medium pressure evaporator 144, a high pressure economizer 145, and a high pressure evaporator 146 are installed. In addition, each superheater (not shown) may be additionally installed on the upstream side of the evaporators. The combustion gas discharged from the heat recovery boiler 140 may be discharged through the stack.

The low-pressure unit G1 includes a condensate preheater 141 , a low-pressure evaporator 142 , and a low-pressure drum 147 . The condensate stored in the condensate storage tank 122 is transferred to the condensate preheater 141 by the condensate pump 123 , and the condensate preheater 141 heats the condensate through heat exchange with combustion gas. The feed water heated in the condensate preheater 141 is transferred to the deaerator 175 to remove gas from the condensate.

Feed water is supplied from the deaerator 175 to the low pressure drum 147, and the low pressure evaporator 142 is connected to the low pressure drum 147 to heat the feed water stored in the low pressure drum 147 and convert it into steam. 147), it can be transferred to the superheater after being separated.

Meanwhile, the intermediate pressure unit G2 includes a medium pressure economizer 143 , a medium pressure evaporator 144 , and a medium pressure drum 148 . The feed water of the deaerator 175 is supplied to the medium pressure economizer 143 by the medium pressure pump 172, and the medium pressure economizer 143 heats the water supply through heat exchange with combustion gas. The feed water heated by the medium pressure economizer 143 is supplied to the medium pressure drum 148, and the medium pressure evaporator 144 is connected to the medium pressure drum 148 to heat the feed water stored in the medium pressure drum 148 and convert it into steam. After being separated from the medium pressure drum 148, it may be transferred to the superheater.

The high-pressure part G3 includes a high-pressure economizer 145 , a high-pressure evaporator 146 , and a high-pressure drum 149 . The feed water of the deaerator 175 is supplied to the high pressure economizer 145 by the high pressure pump 173, and the high pressure economizer 145 heats the feed water through heat exchange with combustion gas. The feed water heated by the high pressure economizer 145 is supplied to the high pressure drum 149, and the high pressure evaporator 146 is connected to the high pressure drum 149 to heat the feed water stored in the high pressure drum 149 and convert it into steam. After degassing in the high-pressure drum, it can be transferred to the superheater.

The steam stored in the low pressure drum 147 , the medium pressure drum 148 , and the high pressure drum 149 may be supplied to the respective low pressure, medium pressure, and high pressure steam turbines after being heated in the superheater.

The water supply pipe 153 connects the high-pressure part G3 and the fuel preheater 150 to supply high-temperature, high-pressure water to the fuel preheater 150 . A high-pressure valve 176 for controlling the flow rate of water supplied to the water supply pipe 153 may be installed at an upstream side of the high-pressure drum 149 .

The fuel preheater 150 receives fuel from the fuel supply unit 117 through the fuel supply pipe 191 , heats it, and then supplies it to the combustor 115 . Here, the fuel may be a gas, but the present invention is not limited thereto.

The fuel preheater 150 includes a primary heating unit 151 and a secondary heating unit 152 for heating fuel. The primary heating unit 151 and the secondary heating unit 152 are connected in parallel, and the primary heating unit 151 and the secondary heating unit 152 have the same capacity.

The fuel supply pipe 191 is connected to the first supply pipe 192 and the second supply pipe 193 , and the first supply pipe 192 is connected to the primary heating unit 151 to provide fuel to the primary heating unit 151 . and the second supply pipe 193 is connected to the secondary heating unit 152 to supply fuel to the secondary heating unit 152 .

The water supply pipe 153 is connected to the first branch pipe 154 and the second branch pipe 155 , and the first branch pipe 154 is connected to the primary heating unit 151 to form the primary heating unit 151 . Water is supplied, and the second branch pipe 155 is connected to the secondary heating unit 152 to supply water supply to the secondary heating unit 152 .

The water supply pipe 153 is connected between the high-pressure economizer 145 and the high-pressure drum 149 to supply water heated by the high-pressure economizer 145 to the primary heating unit 151 and the secondary heating unit 152 . have. Here, the high-pressure water supply is made of a liquid rather than a vapor, and the phase of the water supply does not change in the fuel preheater 150 and maintains a liquid state. When the phase of water supply is changed in the fuel preheater 150 , vibration may occur due to a sudden change in pressure.

A first discharge pipe 167 for moving water discharged from the primary heating unit 151 is connected to the primary heating unit 151 , and the secondary heating unit 152 is discharged from the secondary heating unit 152 . A second discharge pipe 168 for moving the water supply is connected. The first discharge pipe 167 and the second discharge pipe 168 are connected to the water supply return pipe 158 , and the water return pipe 158 arranges the water supplied from the first discharge pipe 167 and the second discharge pipe 168 . transferred to the recovery boiler.

A first thermometer T1 for measuring the temperature of fuel discharged from the primary heating unit 151 is installed in the first supply pipe 192 on the downstream side of the primary heating unit 151, and the secondary heating unit 152 ), a second thermometer T2 for measuring the temperature of the fuel discharged from the secondary heating unit 152 is installed in the second supply pipe 193 on the downstream side.

In addition, the first control valve 161 for controlling the flow rate of the feed water discharged from the primary heating unit 151 is installed in the first discharge pipe 167 . The first control valve 161 controls the flow rate of the feed water flowing into the primary heating unit 151 .

On the other hand, a second control valve 162 for controlling the flow rate of the feed water discharged from the secondary heating unit 152 is installed in the second discharge pipe 168 . The second control valve 162 controls the flow rate of the feed water flowing into the secondary heating unit 152 .

As described above, according to the first embodiment, the feed water heated in the high-pressure economizer 145 through the water supply pipe 153 is transferred to the primary heating unit 151 and the secondary heating unit 152 so that the fuel is heated to a high temperature. In addition to being able to be heated, the primary heating unit 151 and the secondary heating unit 152 are arranged in parallel, and the high-pressure water supply is divided and supplied to the primary heating unit 151 and the secondary heating unit 152 . Therefore, the fuel can be heated more easily.

Hereinafter, a method of driving the combined cycle power generation system according to the first embodiment of the present invention will be described. 4 is a flowchart illustrating a method of driving the combined cycle power generation system according to the first embodiment of the present invention.

3 and 4, the driving method of the combined cycle power generation system according to the present embodiment may include a fuel preheating step (S101), a fuel temperature determining step (S102), and a fuel temperature controlling step (S103). .

In the fuel preheating step ( S101 ), the water supplied from the high-pressure unit G1 is divided and supplied to the primary heating unit 151 and the secondary heating unit 152 installed in parallel. In the fuel preheating step S101, water is supplied to the primary heating unit 151 and the secondary heating unit 152 through the water supply pipe 153 connected between the high-pressure economizer 145 and the high-pressure drum 149 in the high-pressure unit G3. to supply

In the fuel temperature determination step (S102), the temperature of the fuel discharged from the primary heating unit 151 and the temperature of the fuel discharged from the secondary heating unit 152 are measured and compared with a reference temperature. In the fuel temperature determination step ( S102 ), the temperature of the fuel is measured using the first thermometer T1 installed on the downstream side of the primary heating unit 151 and compared with the first reference temperature. In addition, in the fuel temperature determination step ( S102 ), the temperature of the fuel is measured using the second thermometer T2 installed on the downstream side of the secondary heating unit 152 and compared with the second reference temperature. Here, the first reference temperature and the second reference temperature may be set in the same range. In addition, the first reference temperature and the second reference temperature may be set in various ranges according to the capacity of the gas turbine, the type of fuel, and the like.

In the fuel temperature control step (S103), the first control valve 161 for controlling the flow rate of the feed water discharged from the primary heating unit 151 and the second control valve 161 for controlling the flow rate of the feed water discharged from the secondary heating unit 152 The control valve 162 is adjusted to control the temperature of the fuel.

In the fuel temperature control step ( S103 ), when the temperature of the fuel discharged from the primary heating unit 151 is lower than the first reference temperature, the opening degree of the first control valve 161 is increased, and the primary heating unit 151 . When the temperature of the fuel discharged from the is higher than the first reference temperature, the opening degree of the first control valve 161 is reduced.

In addition, in the fuel temperature control step (S103), when the temperature of the fuel discharged from the secondary heating unit 152 is lower than the second reference temperature, the opening degree of the second control valve 162 is increased, and the secondary heating unit ( When the temperature of the fuel discharged from 152 is higher than the second reference temperature, the opening degree of the second control valve 162 is reduced.

As described above, according to the first embodiment, it is possible to efficiently preheat the fuel while preventing the fuel from being overheated by including the fuel temperature control step S103.

Hereinafter, a combined power generation system according to a second embodiment of the present invention will be described. 5 is a configuration diagram illustrating a fuel preheater according to a second embodiment of the present invention.

5, the combined cycle power generation system according to the second embodiment except for the first bypass pipe 156 and the second bypass pipe 157, the combined power generation system according to the first embodiment Since it has the same structure as the system, redundant description of the same structure will be omitted.

A first bypass pipe 156 that bypasses the primary heating unit 151 and supplies fuel to the downstream side of the primary heating unit 151 is connected to the first supply pipe 192 . In addition, a first fuel control valve 163 for controlling the flow rate of fuel moving through the first bypass pipe 156 is installed in the first bypass pipe 156 .

A second bypass pipe 157 for supplying fuel to the downstream side of the secondary heating unit 152 by bypassing the secondary heating unit 152 is connected to the second supply pipe 193 . In addition, a second fuel control valve 164 for controlling the flow rate of fuel moving through the second bypass pipe 157 is installed in the second bypass pipe 157 .

The first fuel control valve 163 controls the flow rate of fuel bypassing the primary heating unit 151 , and the second fuel control valve 164 controls the flow rate of fuel bypassing the secondary heating unit 152 . Thus, it is possible to more easily control the heating temperature of the fuel.

Hereinafter, a method of driving a combined cycle power generation system according to a second embodiment of the present invention will be described.

Since the driving method of the combined cycle power generation system according to the second embodiment is the same as the driving method of the combined cycle power generation system according to the second embodiment, except for the fuel temperature control step, a redundant description of the same configuration will be omitted.

The fuel temperature control step includes a first control valve 161 for controlling the flow rate of feed water discharged from the primary heating unit 151 and a second control valve for controlling the flow rate of feed water discharged from the secondary heating unit 152 ( 162) and the primary heating unit 151 to bypass the first fuel control valve 163 and the secondary heating unit 152 installed in the first bypass pipe 156 for moving fuel The temperature of the fuel is controlled by adjusting the second fuel control valve 164 installed in the second bypass pipe 157 .

In the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit 151 is lower than a preset first reference temperature, the opening degree of the first fuel control valve 163 is reduced, and the first fuel control valve 163 is ) is closed, the degree of opening of the first control valve 161 is increased.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit 151 is higher than the first reference temperature, the opening degree of the first fuel control valve 163 is increased, and the first fuel control valve 163 is ) is fully opened, the degree of opening of the first control valve 161 is reduced.

When the opening degree of the first fuel control valve 163 is decreased, the amount of bypassed fuel is reduced, so that the temperature of the fuel increases. As the flow rate of the incoming feedwater increases, the temperature of the fuel may rise.

On the other hand, if the opening degree of the first fuel control valve 163 is increased, the amount of bypassed fuel is increased, so that the temperature of the fuel is decreased, and when the opening degree of the first control valve 161 is decreased, the primary heating unit ( 151), the flow rate of the feed water flowing into it is reduced, so that the temperature of the fuel may drop.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the secondary heating unit 152 is lower than the preset second reference temperature, the opening degree of the second fuel control valve 164 is reduced, and the second fuel control valve When 164 is closed, the degree of opening of the second control valve 162 is increased.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the secondary heating unit 152 is higher than the second reference temperature, the opening degree of the second fuel control valve 164 is increased, and the second fuel control valve 164 is ) is fully opened, the degree of opening of the second control valve 162 is reduced.

As in the second embodiment, when the first bypass pipe 156, the second bypass pipe 157, the first fuel control valve 163, and the second fuel control valve 164 are installed, it is necessary to preheat the fuel. It is possible to effectively prevent overheating of the fuel while minimizing the flow rate of the used feed water.

Hereinafter, a combined power generation system according to a third embodiment of the present invention will be described. 6 is a configuration diagram illustrating a fuel preheater and a heat recovery boiler according to a third embodiment of the present invention, and FIG. 7 is a configuration diagram illustrating a fuel preheater according to a third embodiment of the present invention.

6 and 7, the combined power generation system according to the third embodiment includes the combined power generation system according to the first embodiment except for the pre-heater 210 and the water supply control pipe 230 and Since they have the same structure, a duplicate description of the same structure will be omitted.

The fuel preheater 150 further includes a pre-heater 210 for pre-heating the fuel, and the pre-heater 210 is installed in the water supply return pipe 158 and includes a primary heating unit 151 and a secondary heating unit 152 . ) and preheat the fuel by supplying water discharged from it. In addition, the preheater 210 divides the preheated fuel and supplies it to the primary heating unit 151 and the secondary heating unit 152 .

A water supply return pipe 158 and a fuel supply pipe 191 are connected to the pre-heater 210 , and the fuel supplied from the fuel supply unit 117 is heated by the pre-heater 210 and then is heated by the primary heating unit 151 and 2 It is supplied to the car heating unit 152 . In addition, a downstream control valve 240 for controlling the flow rate of feed water discharged from the pre-heater 210 is installed on the downstream side of the pre-heater 210 in the water supply return pipe 158 .

A water supply control pipe 230 is connected and installed on the upstream side of the pre-heater 210 from the water supply return pipe 158, and the water supply control pipe 230 connects the intermediate pressure part G2 and the fuel preheater 150 to supply medium pressure water. It is supplied to the fuel preheater 150 . A medium pressure control valve 231 for controlling the flow rate of water supplied from the water supply control pipe 230 to the pre-heater 210 may be installed in the water supply control pipe 230 .

The water supply control pipe 230 is connected to the downstream side of the intermediate pressure pump 172 and supplies the water pressurized by the intermediate pressure pump 172 to the water supply return pipe 158 . In addition, since the water supply control pipe 230 is connected between the medium pressure pump 172 and the medium pressure economizer 143 , the unheated water supply from the medium pressure unit G2 is supplied to the supply water supplied to the primary heating unit 151 . The temperature can be easily adjusted to prevent the fuel from overheating.

In addition, since the water supply control pipe 230 is connected to the downstream side of the medium pressure pump 172 , it can be operated independently without affecting the medium pressure economizer 143 . In addition, since the water supply that is not heated in the intermediate pressure unit G2 is supplied to the primary heating unit 151, the water supply temperature is low, so that the possibility of steam-induced vibration is reduced. In addition, since the feed water pressurized at a high pressure is supplied from the intermediate pressure pump 172 , the possibility that the fuel gas leaks to the water feed side is lowered due to the high feed water pressure.

When the pipe supplying water supply is connected to the downstream side of the medium pressure economizer 143, it is difficult to control the temperature of the water supply supplied to the primary heating unit 151, the temperature of the water supply is high, and vibration occurs, and the pressure of the water supply is low. Low problems may arise.

A first bypass pipe 156 that bypasses the primary heating unit 151 and supplies fuel to the downstream side of the primary heating unit 151 is connected to the first supply pipe 192 . In addition, a first fuel control valve 163 for controlling the flow rate of fuel moving through the first bypass pipe 156 is installed in the first bypass pipe 156 .

A second bypass pipe 157 for supplying fuel to the downstream side of the secondary heating unit 152 by bypassing the secondary heating unit 152 is connected to the second supply pipe 193 . In addition, a second fuel control valve 164 for controlling the flow rate of fuel moving through the second bypass pipe 157 is installed in the second bypass pipe 157 .

Hereinafter, a method of driving a combined cycle power generation system according to a third embodiment of the present invention will be described.

Since the driving method of the combined cycle power generation system according to the third exemplary embodiment is the same as the driving method of the combined cycle power generation system according to the second exemplary embodiment except for the fuel temperature control step, a redundant description of the same configuration will be omitted.

The fuel temperature control step includes a first control valve 161 for controlling the flow rate of feed water discharged from the primary heating unit 151 and a second control valve for controlling the flow rate of feed water discharged from the secondary heating unit 152 ( 162) and the primary heating unit 151 to bypass the first fuel control valve 163 and the secondary heating unit 152 installed in the first bypass pipe 156 for moving fuel The temperature of the fuel is controlled by adjusting the second fuel control valve 164 installed in the second bypass pipe 157 and the downstream control valve 240 that controls the flow rate of feed water discharged from the pre-heater 210 .

In the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit 151 is lower than the preset first reference temperature, the opening degree of the first fuel control valve 163 is reduced, and the downstream control valve 240 is The degree of opening is increased, and when the first fuel control valve 163 is closed, the degree of opening of the first control valve 161 is increased.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit 151 is higher than the first reference temperature, the opening degree of the first fuel control valve 163 is increased, and the downstream control valve 240 is The degree of opening is reduced, and when the first fuel control valve 163 is fully opened, the degree of opening of the first control valve 161 is decreased.

When the opening degree of the first fuel control valve 163 is decreased, the amount of bypassed fuel is reduced, so that the temperature of the fuel increases. As the flow rate of the incoming feedwater increases, the temperature of the fuel may rise.

On the other hand, if the opening degree of the first fuel control valve 163 is increased, the amount of bypassed fuel is increased, so that the temperature of the fuel is decreased, and when the opening degree of the first control valve 161 is decreased, the primary heating unit ( 151), the flow rate of the feed water flowing into it is reduced, so that the temperature of the fuel may drop.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the secondary heating unit 152 is lower than the preset second reference temperature, the opening degree of the second fuel control valve 164 is reduced, and the downstream control valve 240 ) increases, and when the second fuel control valve 164 is closed, the opening degree of the second control valve 162 is increased.

In addition, in the fuel temperature control step, when the temperature of the fuel discharged from the secondary heating unit 152 is higher than the second reference temperature, the opening degree of the second fuel control valve 164 is increased, and the The opening degree is reduced, and when the second fuel control valve 164 is fully opened, the opening degree of the second control valve 162 is reduced.

As described above, according to the third embodiment, since the pre-heater 210 and the water supply control pipe 230 are installed, the fuel can be heated more easily and the temperature of the fuel can be controlled.

* In the above, an embodiment of the present invention has been described, but those of ordinary skill in the art can add, change, delete or The present invention may be variously modified and changed by addition and the like, and this will also be included within the scope of the present invention.

100: combined cycle power system 110: gas turbine
112: compressor 115: combustor
113: main turbine 120: steam turbine
121: condenser 122: condensate storage tank
123: condensate pump 130: generator
140: heat recovery boiler 141: condensate preheater
142: low pressure evaporator 143: medium pressure economizer
144: medium pressure evaporator 145: high pressure economizer
146: high pressure evaporator 147: low pressure drum
148: medium pressure drum 149: high pressure drum
150: fuel preheater 151: primary heating unit
152: secondary heating unit 153: water supply pipe
154: first branch pipe 155: second branch pipe
156: first bypass tube 157: second bypass tube
158: water return pipe 161: first control valve
162: second control valve 163, 167: fuel control valve
167: first discharge pipe 168: second discharge pipe
172: medium pressure pump 173: high pressure pump
175: deaerator 176: high pressure valve
181: steam supply line 182: turbine feed water return line
191: fuel supply pipe 192: first supply pipe
193: second supply pipe 230: water supply control pipe
240: downstream control valve

Claims (15)

a gas turbine that burns fuel to generate rotational force;
an exhaust heat recovery boiler for heating feedwater using combustion gas discharged from the gas turbine;
a fuel preheater heating the fuel supplied to the gas turbine and having a primary heating unit and a secondary heating unit disposed in parallel;
a water supply pipe connected to the heat recovery boiler to supply water to the fuel preheater;
a first branch pipe connected to the water supply pipe to deliver water supply to the primary heating unit;
a secondary branch pipe connected to the water supply pipe to deliver water supply to the secondary heating unit;
includes,
The water supply supplied through the water supply pipe is made of a liquid, and the phase of the water supply in the fuel preheater is constant. The method of claim 1,
A first discharge pipe connected to the primary heating unit to move the water supply discharged from the primary heating unit, a second discharge pipe connected to the secondary heating unit to move the water supply discharged from the secondary heating unit, and the The combined power generation system further comprising a feed water recovery pipe connected to the first discharge pipe and the second discharge pipe to deliver feed water to the exhaust heat recovery boiler. 3. The method of claim 2,
A first control valve for controlling the flow rate of feed water flowing into the primary heating unit is installed in the first discharge pipe, and a second control valve for controlling the flow rate of water supply flowing into the secondary heating unit is installed in the second discharge pipe combined power generation system. The method of claim 1,
By connecting the upstream of the primary heating unit and the downstream of the primary heating unit, a first bypass pipe that bypasses the primary heating unit and moves fuel and a flow rate of fuel moving through the first bypass pipe is controlled. Combined power generation system further comprising a first fuel control valve. 5. The method of claim 4,
By connecting the upstream of the secondary heating part and the downstream of the secondary heating part, a second bypass pipe for bypassing the secondary heating part and moving fuel and controlling the flow rate of fuel moving through the second bypass pipe Combined power generation system further comprising a second fuel control valve. 3. The method of claim 2,
The fuel preheater is connected to the water supply return pipe and further includes a pre-heater configured to receive the feed water discharged from the primary heating unit and the secondary heating unit to pre-heat the fuel, and the fuel heated in the pre-heater The combined power generation system is divided and supplied to the primary heating unit and the secondary heating unit. 7. The method of claim 6,
A combined power generation system in which a downstream control valve for controlling the flow rate of feed water discharged from the pre-heater is installed on the downstream side of the pre-heater. 8. The method of claim 7,
A water supply control pipe for supplying water to the pre-heater is connected to the pre-heater, and an intermediate pressure control valve for controlling the flow rate of water supplied from the water supply control pipe is installed in the water supply control pipe. A method of driving a combined cycle power generation system comprising a gas turbine, a steam turbine, a heat recovery boiler, and a fuel preheater having a primary heating unit and a secondary heating unit for preheating fuel, the method comprising:
a fuel preheating step of dividing the feedwater heated in the heat recovery boiler and supplying it to the primary heating unit and the secondary heating unit installed in parallel;
a water supply temperature determination step of measuring the temperature of the water supply discharged from the primary heating unit and the secondary heating unit and comparing it with a preset reference temperature; and
a fuel temperature control step of controlling the temperature of the fuel using a first control valve and a second control valve for controlling the movement of feed water discharged from the primary heating unit and the secondary heating unit;
includes,
The feed water supplied in the fuel preheating step is made of a liquid, and the phase of the feed water is constant during the fuel preheating process. 10. The method of claim 9,
In the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit is lower than a preset first reference temperature, the opening degree of the first control valve installed on the downstream side of the primary heating unit is increased, and the first When the temperature of the fuel discharged from the heating unit is higher than the first reference temperature, the driving method of the combined cycle power system for reducing the opening degree of the first control valve. 11. The method of claim 10,
In the fuel temperature control step, when the temperature of the fuel discharged from the secondary heating unit is lower than a preset second reference temperature, the opening degree of the second control valve installed on the downstream side of the secondary heating unit is increased, and the second When the temperature of the fuel discharged from the heating unit is higher than a preset first reference temperature, the driving method of the combined cycle power generation system for reducing the opening degree of the second control valve. 11. The method of claim 10,
The fuel temperature control step includes a first control valve installed on the downstream side of the primary heating unit and a first fuel control valve installed on a first bypass pipe that bypasses the primary heating unit and supplies fuel to the downstream side of the primary heating unit. to control the fuel temperature,
When the temperature of the fuel discharged from the primary heating unit is lower than a preset first reference temperature, the degree of opening of the first fuel control valve is reduced, and when the first fuel control valve is closed, the temperature of the first control valve is closed. A method of driving a combined cycle power system to increase the degree of openness. 13. The method of claim 12,
In the fuel temperature control step, when the temperature of the fuel discharged from the primary heating unit is higher than the first reference temperature, the opening degree of the first fuel control valve is increased, and when the first fuel control valve is completely opened, the A method of driving a combined cycle power system for reducing an opening degree of a first control valve. 11. The method of claim 10,
The fuel temperature control step is
A second control valve installed on the downstream side of the secondary heating part and a second fuel control valve installed on a second bypass pipe that bypasses the secondary heating part and supplies fuel to the downstream side of the secondary heating part are adjusted to control the temperature of the fuel but adjust
When the temperature of the fuel discharged from the secondary heating unit is lower than the preset second reference temperature, the opening degree of the second fuel control valve is reduced, and when the second fuel control valve is closed, the second control valve is increase the degree of openness,
When the temperature of the fuel discharged from the secondary heating unit is higher than the second reference temperature, the opening degree of the second fuel control valve is increased, and when the second fuel control valve is fully opened, the first control valve is opened A method of driving a combined cycle power system to reduce the degree. 11. The method of claim 10,
In the fuel preheating step, the fuel is preheated using a pre-heater that receives the feedwater discharged from the primary heating unit and the secondary heating unit and heats the fuel in advance, and then divides the preheated fuel into the primary heating unit and A method of driving a combined cycle power generation system for supplying to the secondary heating unit.

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