JP4512506B2 - Reformed fuel-fired gas turbine equipment - Google Patents

Description

  The present invention relates to a reformed fuel-fired gas turbine facility that operates with a reformed fuel obtained by reforming heavy oil.

  Low-grade fuel such as heavy oil contains a large amount of impurities such as heavy metals, sulfur, nitrogen and ash that cause high temperature corrosion of gas turbines. Hydrothermal heat of supercritical water (critical point: 374 ° C, high-temperature high-pressure water of 22.1 MPa or higher) or subcritical water (high-temperature high-pressure water near the critical point) to reform this low-grade fuel into a clean fuel A technique using a reaction is known. Supercritical water or subcritical water acts as a reaction solvent that easily dissolves organic substances such as heavy oil and thermally decomposes, hydrolyzes, or oxidatively decomposes organic substances in the presence of an oxidizing agent. In recent years, a reformed fuel-fired gas turbine facility that is operated with a reformed fuel obtained by reforming heavy oil by the hydrothermal reaction of supercritical water or subcritical water has been developed.

  As an example of the reformed fuel-fired gas turbine equipment, conventionally, heavy oil is mixed with water (supercritical water or subcritical water) under high temperature and high pressure conditions (for example, about 300 ° C. to 500 ° C., about 20 to 30 MPa). The reformed fuel is depressurized and cooled and allowed to stand in the separator to separate it into gas and liquid oil and moisture, and the oil is distilled to distillate with a low boiling point (lighter ) And a residue with a high boiling point, and gas components and distillate are supplied to the combustor and burned to generate power by driving the turbine, while the remainder is supplied to the boiler. A configuration in which power is generated by driving a steam turbine with steam generated by combustion and a boiler is disclosed (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 11-80750

However, the following problems exist in the above-described conventional technology.
That is, in the above prior art, the reformed fuel is depressurized and cooled to, for example, room temperature (below the water saturation temperature) and allowed to stand in the separator, thereby separating the oil component and water components as gas components and liquid components. It is like that. However, heavy oil is completely dissolved in supercritical water or subcritical water, and ultrafine oil droplets and water droplets are produced in a mixed state by decompression and cooling of the reformed fuel. Is not easy. Moreover, since the gas component supplied to the combustor is cooled to room temperature, it is not preferable from the viewpoint of the thermal efficiency of the entire system. Therefore, a method may be considered in which the reformed fuel is not cooled to room temperature, for example, the cooling temperature of the reformed fuel is set to a water saturation temperature or higher, and gas components including water vapor and oil components are separated. However, in such a case, there is a possibility that the temperature of the gas component is lowered due to natural heat dissipation in the pipe for supplying the gas component to the combustor, and the gas component is liquefied to generate drain. For example, if fuel mixed with gas and liquid is supplied to the gas fuel burner of the combustor, problems such as unstable combustion due to intermittent combustion, clogging of the burner fuel injection holes, and fluctuations in the load on the turbine may occur. Also, for example, when the combustor is composed of a plurality of cans, if fuel mixed with gas and liquid is supplied to a manifold for distributing fuel to each combustor, a fuel supply deviation and a combustion temperature deviation occur in each can, and the turbine May cause damage.

  The present invention has been made in view of the above matters, and an object of the present invention is to provide a reformed fuel-fired gas turbine facility that can reduce the amount of drain generation in the gas reformed fuel supply pipe and improve the reliability. Is to provide.

(1) In order to achieve the above-mentioned object, the present invention mixes heavy oil with supercritical water or subcritical water in a reformed fuel-fired gas turbine facility operated with reformed fuel obtained by reforming heavy oil. The reformer reformed in this way, the gas-liquid separator that separates the reformed fuel reformed by the reformer into the gas reformed fuel and the liquid reformed fuel, and the gas reformer separated by the gas-liquid separator. Temperature adjusting means for adjusting the temperature of the quality fuel to a predetermined temperature within the range from the oil distillation start temperature to the water saturation temperature, and compressed air in which the gas reformed fuel introduced from the gas-liquid separator is introduced from the compressor A combustor that burns with the gas, a turbine that is driven by the combustion gas generated in the combustor , an exhaust heat recovery boiler that generates steam by using exhaust heat of the turbine, and steam that is generated by the exhaust heat recovery boiler. and a steam supply pipe for supplying the gas-liquid separator, wherein Gas reforming fuel supply pipe supplies gas reformed fuel into the combustor from the liquid separator is provided with a temperature of the gas reforming fuel to hold above the water saturation temperature.

  (2) In the above (1), preferably, the gas reformed fuel supply pipe has a pipe length corresponding to the temperature of the gas reformed fuel adjusted by the temperature adjusting means, and the pipe length is 800 m. It arrange | positions so that it may become the following.

In the present invention, the steam supply pipe supplies steam generated in the exhaust heat recovery boiler to the gas-liquid separator, and the gas-liquid separator uses this steam (however, the steam temperature is equal to or lower than the reforming temperature). Then, the reformed fuel is cooled and separated into gas reformed fuel and liquid reformed fuel containing water vapor. Thus, the gas reformed fuel than when cooled to below room temperature water saturation temperature, it is possible to improve the thermal efficiency of the entire system if example embodiment. The steam supply pipe is disposed so as to keep the temperature of the gas reformed fuel supply pipe warm or warm. As a result, there is no need to separately provide a heat source for warming or warming the gas reformed fuel supply pipe, so that the gas reformed fuel supply pipe can be warmed or warmed without lowering the thermal efficiency of the entire system. This can reduce the amount of drain generated in the gas reformed fuel supply pipe. Therefore, it is possible to suppress various problems that occur when drain is included in the gas reformed fuel supplied to the combustor and improve reliability.

( 3 ) In the above ( 1 ) or ( 2 ), preferably, the gas reformed fuel supply pipe and the steam supply pipe include an inner peripheral side pipe and an outer peripheral side pipe in a double pipe, respectively. To do.

( 4 ) In any one of the above (1) to ( 3 ), preferably, a drain trap is provided below the gas reformed fuel supply pipe.

  Thus, when drain is generated in the gas reformed fuel supply pipe, the generated drain is discharged from the drain trap, so that it is possible to reliably prevent the gas reformed fuel supplied to the combustor from containing drain. .

( 5 ) In the above ( 4 ), preferably, there is provided a merging pipe means for merging the drain discharged from the gas reformed fuel supply pipe via the drain trap with the liquid reformed fuel separated by the gas-liquid separator. .

  In some cases, the drain generated in the gas reformed fuel supply pipe can be handled as a liquid reformed fuel. In such a case, the drain discharged from the gas reformed fuel supply pipe via the drain trap is removed by the gas-liquid separator. The separated liquid reformed fuel is joined through a joining pipe means. Thereby, the utilization factor of reformed fuel can be improved.

  ADVANTAGE OF THE INVENTION According to this invention, the amount of drain generation in gas reforming fuel supply piping can be reduced, and reliability can be improved.

  Embodiments of the present invention will be described below with reference to the drawings.

A first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a schematic diagram illustrating the overall configuration of a reformed fuel-fired gas turbine facility according to the present embodiment.

  In FIG. 1, a reformed fuel-fired gas turbine facility includes a heavy oil tank 1 that stores heavy oil, a heavy oil pressure pump 2 that pressurizes heavy oil from the heavy oil tank 1, A water tank 3 for storing water, a pump 4 for pressurizing water from the water tank 3, a heat exchanger 5 for heating heavy oil and water pressurized by the pumps 2 and 4 to a high temperature, and this heat exchange A reformer 6 for reforming by mixing heavy oil and water introduced from the reformer 5 under high temperature and high pressure conditions, and a reformed fuel reformed by the reformer 6 as a gas reformed fuel and a liquid reformed fuel And a combustor 9 that combusts one or both of the liquid reformed fuel and the gas reformed fuel separated by the gas-liquid separator 7 together with the compressed air from the compressor 8. , Which is connected to a rotor (not shown) of the compressor 8 and is driven by combustion gas generated in the combustor 9 And down 10, and a gas turbine generator 11 which generates electric power by driving the turbine 10.

  The heat exchanger 5 introduces the heated gas generated by the heated gas generator 12 and heats heavy oil and water by heat exchange with the heated gas. The reformer 6 mixes heavy oil with supercritical water or subcritical water under high temperature and high pressure conditions, decomposes and softens the heavy oil, separates heavy metals such as vanadium, and the separated heavy metals are modified. It reacts with the trapping agent filled in the mass container 6 and is removed. The high temperature and high pressure conditions in the reformer 6 are preferably about 450 ° C. and 20 MPa, for example, from the viewpoint of impurity removal efficiency and prevention of coking.

  The gas-liquid separator 7 depressurizes the reformed fuel introduced from the reformer 6 and cools it with, for example, cooling water to separate it into gas reformed fuel and liquid reformed fuel. The liquid reformed fuel separated by the gas-liquid separator 7 is temporarily stored in the liquid reformed fuel tank 13 and supplied to the combustor 9 through the liquid reformed fuel supply pipe 15 by driving the supply pump 14. It has become. Further, the gas reformed fuel separated by the gas-liquid separator 7 is supplied to the combustor 9 via the gas reformed fuel supply pipe 16.

  Here, as a major feature of the present embodiment, the gas-liquid separator 7 is provided with a temperature adjusting unit 17 (temperature adjusting means) for adjusting the temperature of the gas reformed fuel. The temperature adjusting unit 17 adjusts the amount of cooling water for cooling the reformed fuel introduced into the gas-liquid separator 7 so as to adjust the temperature of the reformed fuel, that is, the temperatures of the gas reformed fuel and the liquid reformed fuel. It has become. Next, the temperature of the gas reformed fuel adjusted by the temperature adjusting unit 17 will be described with reference to FIG. FIG. 2 is a characteristic diagram showing the relationship between the temperature of the gas reformed fuel and the liquefaction rate.

In FIG. 2, the horizontal axis represents the temperature of the gas reforming fuel, the vertical axis represents taking liquefaction rate when the temperature of the gas reforming fuel is decreased from the state of the reforming temperature T _1. Range of temperature of the gas reforming fuel from the reforming temperatures T ₁ to temperature T _{2 (inflection} point), and the range of temperature T ₂ to the oil still starting temperature T _3, the liquefaction rate respectively as the temperature is lowered Monotonically increasing. In the range of temperature of the gas reforming fuel from the oil distillation starting temperature T ₃ until the water saturation temperature T ₄ (the temperature range is about 50 ° C.), slight slope in the liquefaction rate as temperature decreases monotonically increases. In the range where the temperature of the gas reforming fuel is water saturation temperature T ₄ less, liquefied ratio with a relatively large gradient as the temperature decreases monotonically increases. From the above, when the temperature of the gas reforming fuel is changed in the range from oil distillation starting temperature T ₃ until the water saturation temperature T _4, it is understood that the liquefaction amount is small best. In the range from the reforming temperatures T ₁ until the water saturation temperature T _4, when the temperature of the gas reforming fuel is decreased, mainly oil is generated as a drain, the range of water saturation temperature T ₄ less When the temperature of the gas reformed fuel decreases, moisture is generated as drain.

Temperature adjustment unit 17 of the present embodiment, the temperature of the separated in the gas-liquid separator 7 gas reformed fuel, the predetermined temperature in the range from oil distillation starting temperature T ₃ until the water saturation temperature T _4, preferably oil The distillation start temperature T ₃ is adjusted. As a result, the gas-liquid separator 7 separates the gas reformed fuel containing water vapor into the liquid reformed fuel.

The A major feature of this embodiment, the gas reforming fuel supply pipe 16, so that the temperature of the gaseous reformed fuel is held in the water saturation temperature T ₄ or more, the gas reforming adjusted by the temperature adjuster 17 The pipe length corresponding to the temperature of the fuel (in this embodiment, the pipe length from the gas-liquid separator 7 to the combustor 9) is provided. Details thereof will be described with reference to FIG. FIG. 3 is a characteristic diagram showing the relationship between the pipe length in the gas reformed fuel supply pipe 16 and the temperature drop of the gas reformed fuel.

  In FIG. 3, the horizontal axis represents the length L of the gas reformed fuel supply pipe 16, and the vertical axis represents the gas reformed fuel supply pipe 16 constituted by a pipe wound with a heat insulating material. In this case, the temperature drop ΔT of the gas reformed fuel due to natural heat dissipation is shown. As the pipe length L of the gas reformed fuel supply pipe 16 becomes longer, the temperature drop ΔT of the gas reformed fuel due to natural heat dissipation increases monotonously.

The gas reformed fuel supply pipe 16 of the present embodiment takes into account the temperature drop ΔT of the gas reformed fuel due to natural heat dissipation, and an allowable range ΔT _{max of the} temperature drop (the temperature of the gas reformed fuel adjusted by the temperature adjusting unit 17) i.e. arranged so that the gas-liquid separator 7 outlet temperature of the gas reforming fuel, the following equivalent piping length L _max the difference) between the water saturation temperature T _4. That is, for example, when the temperature of the gas reforming fuel adjusted to the oil still starting temperature _{T 3} at a temperature adjusting unit 17 is about 50 ° C. tolerance [Delta] T _max temperature drop ₍₌ T 3 -T _4, see FIG. 2) Accordingly, the corresponding pipe length L _max is 800 m (see FIG. 3). In this case, by disposing as the pipe length of the gas reforming fuel supply pipe 16 becomes 800m or less, and the temperature of the gas reforming fuel adapted to hold the water saturation temperature T ₄ or more.

In the present embodiment configured as described above, the temperature adjustment unit 17, a predetermined temperature in the range of the temperature of the gas reforming fuel from the oil distillation starting temperature T ₃ until the water saturation temperature T _4, for example oil still to adjust to the starting temperature _{T 3.} Thus, for example, a gas reforming fuel compared with the case of cooling to room temperature follows the water saturation temperature T _4, it is possible to improve the thermal efficiency of the entire system. Further, the gas reformed fuel supply pipe 16 has an oil distillation start temperature T _{3 of} the gas reformed fuel adjusted by the temperature adjusting unit 17 so that the temperature of the gas reformed fuel is maintained at the water saturation temperature T ₄ or higher (ie, The pipe length is 800 m or less corresponding to the temperature drop allowable width ΔT = about 50 ° C.). Thus, the gas reformed fuel in the gas reforming fuel supply pipe 16 is held within the range of from the oil distillation starting temperature T ₃ liquefied small amount due to the temperature drop until the water saturation temperature T _4, the drain generation amount Can be reduced. Therefore, various problems (for example, unstable combustion in the combustor 9, clogging of the burner fuel injection hole, load fluctuation of the turbine 10, etc.) that occur when the gas reformed fuel supplied to the combustor contains drain are suppressed. , Reliability can be improved.

  Moreover, in this embodiment, the combustor 9 burns gas reformed fuel containing water vapor together with compressed air. Thereby, compared with the case where the gas reformed fuel which does not contain water vapor | steam is burned, for example, effects, such as reduction of nitrogen oxide generation, can be acquired by the effect | action of flame temperature fall.

In the above embodiment, the gas reforming fuel supply pipe 16, the pipe length of the temperature of the gas reforming fuel to keep the water saturation temperature T ₄ or more, from the gas-liquid separator 7 to combustor 9 Although the case where the length L is limited has been described as an example, it is not limited thereto. That is, for example, when a heat retaining means for retaining or warming the gas reformed fuel is provided in the middle of the gas reformed fuel supply pipe 16, the pipe length from the gas-liquid separator 7 to the heat retaining means and the heat retaining means to the combustor. limit the pipe length up to 9, the temperature of the gas reforming fuel may be held in the water saturation temperature T ₄ or more. In such a case, the same effect as described above can be obtained.

  A second embodiment of the present invention will be described with reference to FIG. The present embodiment is an embodiment in which piping means for discharging the drain generated in the gas reformed fuel supply piping 16 is provided.

  FIG. 4 is a schematic diagram showing the overall configuration of the reformed fuel-fired gas turbine facility according to the present embodiment. In FIG. 4, parts that are the same as in the first embodiment are given the same reference numerals, and descriptions thereof are omitted as appropriate.

In this embodiment, a drain trap 18 is provided below the gas reformed fuel supply pipe 16, a three-way valve 19 is connected to the downstream side of the drain trap 18, and a drain discharge pipe is connected to one outlet side of the three-way valve 19. 20, and a drain confluence pipe 21 is connected to the other outlet side of the three-way valve 19. For example turbine startup such low temperature of the gas reforming fuel supply pipe 16, there is a possibility that the drain is produced the temperature of the gas reforming fuel becomes water saturation temperature T ₄ less water. Therefore, when the drain trap 18 and the drain discharge pipe 20 are communicated by switching the three-way valve 19, the drain generated in the gas reformed fuel supply pipe 16 is drain trap 18, the three-way valve 19, and the drain discharge pipe. 20 and discharged as waste liquid. Thereby, it can prevent reliably that drain is contained in the gas reforming fuel supplied to the combustor 9.

Further, for example if the temperature of the gas reforming fuel turbine operation or the like gas reforming fuel supply pipe 16 to have been retained in the water saturation temperature T ₄ or more, the drain occurring in the gas reforming fuel supply pipe 16 liquid reforming It can be handled as fuel (oil). Therefore, when the three-way valve 19 is switched to connect the drain trap 18 and the drain merging pipe 21, the drain generated in the gas reformed fuel supply pipe 16 is drained by the drain trap 18, the three-way valve 19, and the drain merging pipe. 21 is joined to the liquid reforming fuel tank 13 via 21. Thereby, the utilization factor of reformed fuel can be improved.

  A third embodiment of the present invention will be described with reference to FIG. In the present embodiment, an exhaust heat recovery boiler that generates steam by exhaust heat of the turbine is provided, and a steam supply pipe that supplies steam generated by the exhaust heat recovery boiler to a gas-liquid separator is provided.

  FIG. 5 is a schematic diagram showing the overall configuration of the reformed fuel-fired gas turbine facility according to the present embodiment. In FIG. 5, the same parts as those in the first and second embodiments are denoted by the same reference numerals, and description thereof will be omitted as appropriate.

  The reformed fuel-fired gas turbine facility according to the present embodiment is a so-called combined power generation facility, and an exhaust heat recovery boiler 22 that generates water by heating water with the exhaust gas from the turbine 10 and the exhaust heat recovery boiler 22. The steam turbine 23 driven by the steam generated in the above, the steam turbine generator 24 for generating electricity by driving the steam turbine 23, and the steam generated in the exhaust heat recovery boiler 22 are supplied to the gas-liquid separator 25, and the gas The reformed fuel supply pipe 26 is provided with a steam supply pipe 27 disposed so as to keep warm or warm.

  The gas reformed fuel supply pipe 26 and the steam supply pipe 27 are configured to include an inner peripheral side pipe line and an outer peripheral side pipe line of the double pipe 28, respectively. Specifically, the gas reformed fuel supply pipe 26 is, for example, a pipe connected between the inner circumference side pipe of the double pipe 28 and the inner circumference side pipe of the double pipe 28 and the gas-liquid separator 25. 29 and a pipe 30 connected between the inner peripheral side pipe of the double pipe 28 and the combustor 9, and the gas reformed fuel separated by the gas-liquid separator 25 is supplied to the combustor 9. It is supposed to be. The steam supply pipe 27 includes, for example, an outer peripheral side pipe of the double pipe 28, a pipe 31 connected between the outer peripheral side pipe of the double pipe 28 and the exhaust heat recovery boiler 22, and the outer circumference of the double pipe 28. The side pipe and the pipe 32 connected to the gas-liquid separator 25 are configured to supply steam generated by the exhaust heat recovery boiler 22 to the gas-liquid separator 25. In addition, it is good also as a structure which abbreviate | omits any of piping 29-32 and connects the double pipe 28 directly to the combustor 9 or the gas-liquid separator 25. FIG.

Gas-liquid separator 25, the steam introduced via the steam supply pipe 27 (where steam temperature is less than reforming temperature T _1, of course is the water saturation temperature T ₄ or higher) using a reformer 6 The reformed fuel introduced from is cooled and separated into gas reformed fuel and liquid reformed fuel containing steam. Thus, the same first embodiment, for example, a gas reforming fuel compared with the case of cooling to room temperature follows the water saturation temperature T _4, it is possible to improve the thermal efficiency of the entire system.

  Further, the outer peripheral side pipe of the double pipe 28 constituting the steam supply pipe 27 keeps or warms the inner peripheral side pipe of the double pipe 28 constituting the gas reformed fuel supply pipe 26. Accordingly, it is not necessary to separately provide a heat source for keeping or warming the gas reforming fuel supply pipe 26, so that the gas reforming fuel supply pipe 26 is kept warm or warm without lowering the thermal efficiency of the entire system. As a result, the amount of drain generated in the gas reformed fuel supply pipe 26 can be reduced. Therefore, it is possible to suppress various problems that occur when the gas reformed fuel supplied to the combustor 9 contains drain and improve reliability.

  A fourth embodiment of the present invention will be described with reference to FIG. The present embodiment is an embodiment in which a steam supply pipe for supplying steam generated by the exhaust heat recovery boiler to the heat exchanger is provided.

  FIG. 6 is a schematic diagram showing the overall configuration of the reformed fuel-fired gas turbine facility according to the present embodiment. In FIG. 6, the same parts as those in the third embodiment are denoted by the same reference numerals, and description thereof will be omitted as appropriate.

  In the present embodiment, the steam generated by the exhaust heat recovery boiler 22 is supplied to the heat exchanger 5, and the steam supply pipe 33 arranged to keep the gas reformed fuel supply pipe 26 warm or warm is provided. I have. The steam supply pipe 33 includes, for example, an outer pipe on the double pipe 28, a pipe 34 connected between the outer pipe on the double pipe 28 and the exhaust heat recovery boiler 22, and the double pipe 28. And a pipe 35 connected to the heat exchanger 5. When the temperature difference between the steam and the gas reformed fuel in the double pipe 28 is large, it is preferable to provide a heat insulating member between the inner peripheral side pipe line and the outer peripheral side pipe line of the double pipe 28.

  The heat exchanger 5 of the present embodiment heats heavy oil and water pressurized by the pumps 2 and 4 by heat exchange with steam introduced via the steam supply pipe 33. Thereby, it is not necessary to provide the heated gas generation device 12 of the above embodiment, and the thermal efficiency of the entire system can be improved and the cost can be reduced.

  Further, the outer peripheral side pipe of the double pipe 28 constituting the steam supply pipe 33 keeps or warms the inner peripheral side pipe of the double pipe 28 constituting the gas reformed fuel supply pipe 26. Accordingly, it is not necessary to separately provide a heat source for keeping or warming the gas reforming fuel supply pipe 26, so that the gas reforming fuel supply pipe 26 is kept warm or warm without lowering the thermal efficiency of the entire system. As a result, the amount of drain generated in the gas reformed fuel supply pipe 26 can be reduced. Therefore, it is possible to suppress various problems that occur when the gas reformed fuel supplied to the combustor 9 contains drain and improve reliability.

  The drain trap 18, the three-way valve 19, the drain discharge pipe 20, and the drain described in the second embodiment are provided below the gas reformed fuel supply pipe 26 in the third and fourth embodiments. A junction pipe 21 may be provided. In such a case, as in the second embodiment, the drain generated in the gas reformed fuel supply pipe 26 is discharged and the gas reformed fuel supplied to the combustor 9 is reliably prevented from being drained. Further, the switching operation of the three-way valve 19 allows the drain generated in the gas reformed fuel supply pipe 26 to merge with the liquid reformed fuel tank 13 and improve the utilization rate of the reformed fuel.

It is the schematic showing the whole structure of 1st Embodiment of the reformed fuel-fired gas turbine equipment of this invention. It is a characteristic view showing the relationship between the temperature and liquefaction rate of the gas reformed fuel in the first embodiment of the reformed fuel-fired gas turbine equipment of the present invention. It is a characteristic view showing the relationship between the pipe length and the temperature drop in the gas reformed fuel supply pipe constituting the first embodiment of the reformed fuel-fired gas turbine equipment of the present invention. It is the schematic showing the whole structure of 2nd Embodiment of the reformed fuel burning gas turbine installation of this invention. It is the schematic showing the whole structure of 3rd Embodiment of the reformed fuel burning gas turbine installation of this invention. It is the schematic showing the whole structure of 4th Embodiment of the reformed fuel burning gas turbine installation of this invention.

Explanation of symbols

6 Reformer 7 Gas-liquid separator 8 Compressor 9 Combustor 10 Turbine 16 Gas reformed fuel supply pipe 17 Temperature adjusting unit (temperature adjusting means)
18 Drain trap 19 Three-way valve (Meeting piping means)
21 Drain merging piping (merging piping means)
22 Waste heat recovery boiler 25 Gas-liquid separator 26 Gas reforming fuel supply pipe 27 Steam supply pipe 28 Double pipe 33 Heat exchanger 34 Steam supply pipe L Pipe length of gas reforming fuel supply pipe T ₃ Oil distillation start temperature T ₄ water saturation temperature

Claims (5)

In the reformed fuel-fired gas turbine facility that operates with the reformed fuel that reformed heavy oil,
A reformer for reforming by mixing heavy oil with supercritical water or subcritical water;
A gas-liquid separator for separating the reformed fuel reformed by the reformer into a gas reformed fuel and a liquid reformed fuel;
Temperature adjusting means for adjusting the temperature of the gas reformed fuel separated by the gas-liquid separator to a predetermined temperature within the range from the oil distillation start temperature to the water saturation temperature;
A combustor for combusting the gas reformed fuel introduced from the gas-liquid separator together with the compressed air introduced from the compressor;
A turbine driven by combustion gas generated in the combustor ;
An exhaust heat recovery boiler that generates steam using the exhaust heat of this turbine;
A steam supply pipe for supplying steam generated in the exhaust heat recovery boiler to the gas-liquid separator ;
A gas reforming fuel supply pipe for supplying gas reforming fuel from the gas-liquid separator to the combustor is provided so as to maintain the temperature of the gas reforming fuel at or above the water saturation temperature. Fuel-fired gas turbine equipment. In the reformed fuel-fired gas turbine equipment according to claim 1,
The gas reformed fuel supply pipe has a pipe length corresponding to the temperature of the gas reformed fuel adjusted by the temperature adjusting means, and the pipe length is arranged to be 800 m or less. Reformed fuel-fired gas turbine equipment. In reformed-fuel-burning gas turbine equipment according to claim 1 or 2, wherein,
The gas reformed fuel supply pipe and the steam supply pipe are each configured to include an inner peripheral side pipe and an outer peripheral side pipe in a double pipe, respectively. In the reformed fuel-fired gas turbine equipment according to any one of claims 1 to 3 ,
A reformed fuel-fired gas turbine facility, wherein a drain trap is provided below the gas reformed fuel supply pipe. In the reformed fuel-fired gas turbine equipment according to claim 4 ,
A reformed fuel-fired gas turbine characterized by comprising a joining pipe means for joining the drain discharged from the gas reformed fuel supply pipe via the drain trap to the liquid reformed fuel separated by the gas-liquid separator. Facility.

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