JP6137831B2 - Gas turbine cogeneration system using high humidity air - Google Patents

Description

  The present invention relates to a high-humidity air-utilizing gas turbine cogeneration system capable of simultaneously supplying electric power and steam, and more particularly to a high-humidity air-utilizing gas turbine cogeneration system having a regenerator in a gas turbine exhaust gas system. is there.

  Since the gas turbine cogeneration system can obtain high efficiency in the total efficiency of the combined electric output and heat output, it is widely put into practical use in industrial fields that require electricity and heat.

  An example of a gas turbine cogeneration system having a regenerator in a gas turbine exhaust gas system is disclosed in Japanese Patent Laid-Open No. 6-248974 (Patent Document 1). This Patent Document 1 discloses a gas turbine composed of a compressor, a combustor, and a turbine, a mixer that pressurizes air using water vapor as a driving source and mixes both fluids, and for heating the mixed gas with turbine exhaust. A heat exchanger (regenerator), a waste heat boiler that evaporates water using the turbine exhaust as a heat source, an air line for leading a part of the compressed air from the compressor to the combustor, and a waste heat A partially regenerative two-fluid gas turbine having a main steam line for sending a part of steam from a boiler to a mixer, and a mixed gas line for introducing a mixed gas from the mixer to a combustor through a heat exchanger It is disclosed.

JP-A-6-248974

  In the system described in Patent Document 1, a part of the compressed air from the compressor is mixed with the steam for driving the mixer by the mixer to become humidified air, and this humidified air is preheated by the heat exchanger (regenerator). Supplied to the combustor. As the amount of steam for driving the mixer increases, the amount of compressed air sucked into the mixer also increases, so the amount of heat recovered from the gas turbine exhaust gas to the gas turbine in the heat exchanger increases, and the power generation efficiency is improved. At this time, since the working fluid of the gas turbine is increased by the steam for driving the mixer, the power generation output is increased.

  On the other hand, as the mixer driving steam increases, the amount of recovered heat in the heat exchanger increases and the temperature of the gas turbine exhaust gas flowing into the exhaust heat boiler decreases, so the amount of steam generated in the exhaust heat boiler decreases. . As a result, the amount of steam delivered to other systems decreases.

  That is, in the system described in Patent Document 1, when the gas turbine power generation output is increased, the delivery steam amount is decreased, and when the delivery steam amount is increased, the power generation output is decreased. There is a practical problem that it is difficult to adjust the output and the amount of steam.

  The object of the present invention is to adjust the power generation output and the amount of steam delivered to any output and amount of steam within a specified range in a gas turbine cogeneration system using a high humidity air equipped with a regenerator in the gas turbine exhaust gas system. It is to do.

  A high-humidity air-utilizing gas turbine cogeneration system according to the present invention includes a gas turbine including an air compressor, a combustor, and a turbine, and suctions and pressurizes compressed air from the compressor using steam as a driving source, and A mixer that mixes compressed air with steam to provide humidified air, a regenerator that is provided downstream of the turbine, heats the humidified air from the mixer using turbine exhaust gas as a heat source, and that is provided downstream of the regenerator. Exhaust heat boiler that evaporates water using the exhaust gas as a heat source, a compressed air line that directly leads part of the compressed air from the air compressor to the combustor, a compressed air branch line that leads the remainder to the mixer, and an exhaust heat boiler The steam line for driving the mixer that leads a part of the steam generated in the process to the mixer, the steam delivery line that sends the remaining steam to another steam utilization system, and the humidified air from the mixer. The humidified air line leading to the regenerator, the high-temperature humidified air line leading the high-temperature humidified air from the regenerator to the combustor, and the humidified air line between the mixer and regenerator branch off a portion of the humidified air It has the regenerator bypass line joined to the humidified air line.

  In addition to the above configuration, the present invention directly contacts the humidified air from the mixer with water, lowers the temperature of the humidified air by the latent heat of evaporation of water, and adds the amount of humidified air by adding the evaporated water. It is preferable to provide an auxiliary humidifier to be increased on the humidified air inlet side of the regenerator.

  Furthermore, in the present invention, in addition to the above configuration, it is preferable to provide an air cooling device on the intake side of the air compressor for reducing the compressor power by lowering the specific volume by lowering the air temperature.

  According to the present invention, in a gas turbine cogeneration system using a high-humidity air equipped with a regenerator in a gas turbine exhaust gas system, the power generation output and the amount of steam to be delivered can be set within a range of system operating characteristics. The amount of steam can be adjusted.

  Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

1 is an overall configuration diagram of a gas turbine cogeneration system using high humidity air according to the present invention (Example 1). It is another whole block diagram of the high-humidity air utilization gas turbine cogeneration system by this invention (Example 2). It is another whole block diagram of the high-humidity air utilization gas turbine cogeneration system by this invention (Example 3). It is explanatory drawing which compared the characteristic of the electric power generation output-delivery vapor | steam amount of Example 1 by this invention with the characteristic of a comparative example. It is explanatory drawing which compared the characteristic of the electric power generation output-delivery steam amount of Example 2 by this invention with the characteristic of Example 1 by this invention, and a comparative example. It is explanatory drawing which compared the characteristic of the electric power generation output of the Example 3 by this invention-the amount of delivered steam with the characteristic of Example 2 by this invention, and a comparative example.

  Hereinafter, preferred embodiments for carrying out the present invention will be described with reference to the drawings. In addition, the same code | symbol is used in principle for the common part in each figure.

  FIG. 1 is an overall configuration diagram of Embodiment 1 of a gas turbine cogeneration system using high humidity air according to the present invention.

  In FIG. 1, a high-humidity air-utilizing gas turbine cogeneration system according to the present invention includes a gas turbine, a mixer 9, a regenerator 7, an exhaust heat boiler 4, a feed water heater 6, and a chimney 11 as main equipment. have. The gas turbine includes an air compressor 1 that compresses air A, a combustor 2 that combusts fuel F using air as a combustion support, a turbine 3 that is driven by the combustion gas and drives the air compressor 1 and the generator 5. Consists of The mixer 9 uses the steam S from the exhaust heat boiler 4 as a drive source, sucks the compressed air from the air compressor 1 to increase the pressure, and mixes the compressed air with the steam to obtain humidified air. As the mixer 9, it is desirable to apply a steam ejector that has no mechanical moving parts and can be expected to have high reliability. The regenerator 7 is provided downstream of the turbine 3 and heats humidified air from the mixer 9 using the turbine exhaust gas E as a heat source. The exhaust heat boiler 4 is provided downstream of the regenerator 7 and evaporates the feed water heated by the feed water heater 6 using the turbine exhaust gas E as a heat source. The feed water heater 6 is provided downstream of the exhaust heat boiler 4 and heats the feed water W supplied through the feed water pump 10 using the turbine exhaust gas E as a heat source.

  Further, as main piping lines between the main facilities, a compressed air line 21 for directly guiding a part of the compressed air from the air compressor 1 to the combustor 2 and a compressed air for guiding the remainder to the mixer 9. The branch line 27, the mixer driving steam line 22 that leads a part of the steam S generated in the exhaust heat boiler 4 to the mixer 9 as the mixer driving steam, and the remaining steam S is sent to another steam utilization system. A steam delivery line 25 for performing the operation, a humidified air line 23 for introducing the humidified air HA from the mixer 9 to the regenerator 7, and a high temperature for introducing the high-temperature humidified air HA from the regenerator 7 to the combustor 2. A humidifier air line 24 and a regenerator bypass line 26 for bypassing the regenerator 7 and joining a part of the humidified air HA flowing through the humidified air line 23 to the high-temperature humidified air line 24 are provided.

  The mixer drive steam line 22 is used to drive the mixer for distributing and supplying the steam generated in the exhaust heat boiler 4 to the mixer drive steam to the mixer 9 and the supply steam to other processes. A steam flow control valve 42 is provided. The humidified air line 23 is provided with a regenerator bypass flow rate control valve 43 for controlling the regenerator bypass ratio of the humidified air from the mixer 9. The regenerator bypass flow control valve 43 may be provided in the regenerator bypass line 26. The opening degree of the mixer driving steam flow rate control valve 42 and the regenerator bypass flow rate control valve 43 is controlled by a control device (not shown).

  In this embodiment, the regenerator bypass line 26 is configured so that a part of the humidified air from the mixer 9 can be led to the combustor 2 by bypassing the regenerator 7.

  In such a system configuration, for example, when it is desired to increase the power generation output without changing the amount of delivered steam, the regenerator bypass ratio of the humidified air from the mixer 9 is increased. By increasing the regenerator bypass ratio, the amount of heat recovered in the regenerator 7 decreases, and the amount of evaporation in the exhaust heat boiler 4 increases. Since the delivery steam amount is the same, the increase in the evaporation amount increases the mixer driving steam to the mixer 9 (= exhaust heat boiler evaporation amount−send steam amount). As a result, the humidified air guided to the combustor 2 increases and the power generation output increases. That is, the present embodiment utilizes such an effect, and by adjusting the regenerator bypass ratio, the power generation output can be adjusted while the amount of the delivered steam is constant.

  Further, when it is desired to increase the amount of steam to be sent without changing the power generation output, if the amount of steam to be sent is increased, the steam for driving the mixer to the mixer 9 will decrease and the power generation output will decrease. By increasing the amount to the target value and at the same time increasing the regenerator bypass rate, the required power output can be maintained.

  That is, according to this embodiment, by adjusting the regenerator bypass ratio, the power generation output and the amount of steam to be delivered can be adjusted to an arbitrary output and amount of steam, respectively, within a certain range (within the operating characteristics of the system). There is an effect.

  The effect of the present embodiment will be described with reference to FIG.

  FIG. 4 is an explanatory diagram showing the relationship between the power generation output and the amount of delivered steam in Example 1 of the present invention in comparison with the operating characteristics of the comparative example. The comparative example has a system configuration in which the regenerator bypass line 26 and the regenerator bypass flow rate control valve 43 are not provided in the configuration of FIG. 1 (the same applies to comparative examples in later-described second and third embodiments). ).

  In FIG. 4, the vertical axis represents the power generation output, and the horizontal axis represents the amount of steam delivered. In addition, the amount of steam to be sent is the amount of steam sent to other processes among the steam generated in the exhaust heat boiler 4, and the remaining steam is led to the mixer 9 as steam for driving the mixer (Example 2 described later). The same applies to FIGS. 5 and 6 for explaining the effect of the third embodiment.)

  The characteristic curve (1) in FIG. 4 is the operation characteristic of the comparative example, and corresponds to the case where the regenerator bypass ratio is operated at 0% in Example 1 of the present invention. Characteristic curves (2) and (3) are the operating characteristics of Example 1 of the present invention, (2) is the operating characteristics when the regenerator bypass ratio is 30%, and (3) is the regenerator bypass ratio. It is an operating characteristic at the time of driving | running by making 50%.

  From FIG. 4, it can be seen that Example 1 of the present invention has an operation characteristic that the power generation output at the same delivery steam amount can be increased as the regenerator bypass ratio is increased. Further, this operating characteristic indicates that, for example, by increasing the regenerator bypass ratio, it is possible to increase the amount of delivered steam while keeping the power generation output constant.

  Therefore, according to the first embodiment of the present invention, by controlling the regenerator bypass ratio, the power generation output and the amount of steam to be delivered can be adjusted to arbitrary output and amount of steam, respectively, within the range of the operating characteristics of the system.

  FIG. 2 is an overall configuration diagram showing a second embodiment of a gas turbine cogeneration system using high humidity air according to the present invention. The description of the same parts as those in the first embodiment shown in FIG. In this embodiment, in addition to the configuration of the first embodiment shown in FIG. 1, the auxiliary humidifier 12 and the auxiliary humidified water supply line 29 are provided. The auxiliary humidifier 12 is provided on the humidified air inlet side of the regenerator 7 downstream of the mixer 9, directly contacts the humidified air with water, lowers the temperature of the humidified air by the latent heat of water evaporation, and evaporates the water. Increases the amount of humidified air. The auxiliary humidified water supply line guides part of the water supplied by the feed water heater 6 to the auxiliary humidifier 12. The auxiliary humidifying water supply line 29 is provided with an auxiliary humidifying water pump 13 and an auxiliary humidifying water control valve 41, thereby boosting the auxiliary humidifying water from the feed water heater 6 and supplying the necessary auxiliary humidifying water. The auxiliary humidifier 12 can be guided. The auxiliary humidifying water control valve 41 is controlled by a control device (not shown) in the same manner as the mixer driving steam flow control valve 42 and the regenerator bypass flow control valve 43.

  As the auxiliary humidifier 12 in the present embodiment, a humidifying tower disclosed in Japanese Patent No. 4285781 or a spray type humidifier disclosed in Japanese Patent No. 4167789 can be applied.

  The humidification tower has a structure similar to that of a cooling tower, and the air introduced from the lower part of the vertical container in which the filler is installed and the water introduced from the upper part of the container flow down through the filler. In the process, water and air directly exchange heat, and the flow rate increases as the water evaporates, and the humidified air whose temperature has decreased due to latent heat of vaporization is taken out from the top of the humidification tower. In this humidifying tower system, the relative humidity of the outlet humidified air can be controlled to an arbitrary value of 100% or less by adjusting the amount of water introduced from the top. However, the humidification tower is relatively large and has a built-in filler, so that the heat capacity is large and the response time of relative humidity change is relatively long.

  In the spray-type humidifier, a spray nozzle is installed in the air flow path, and fine water droplets are sprayed by supplying high-pressure water to the spray nozzle, and while the water droplets move on the air flow and move downstream. Evaporates. In this spray type humidifier, by providing a plurality of spray nozzles and controlling the pressure of the supplied high-pressure water and / or the number of spray nozzles to be operated, the relative humidity of the outlet humidified air is an arbitrary value of 100% or less. Can be controlled relatively easily. In addition, since the structure is simple and an internal filler or the like is unnecessary, the heat capacity is smaller than that of the humidification tower, and the response time of the relative humidity change is relatively short.

  Therefore, it is desirable to apply a spray type humidifier as the auxiliary humidifier 12 in the present embodiment.

  In the present embodiment, in addition to the configuration of the first embodiment, an auxiliary humidifier 12 is installed, and the auxiliary humidifier 12 directly contacts the humidified air from the mixer 9 with water to evaporate, and the auxiliary humidifier by latent heat of evaporation. The flow rate of the humidified air can be increased while the humidified air temperature at the outlet is lowered. In this embodiment, in addition to the effects of the first embodiment, the following operational effects are obtained.

  That is, in such a system configuration, for example, if the auxiliary humidification amount in the auxiliary humidifier 12 is increased while the regenerator bypass ratio is constant, the recovered heat amount in the regenerator 7 increases, and the exhaust heat boiler 4 The amount of evaporation decreases. The reduction in the amount of evaporation in the exhaust heat boiler 4 due to this auxiliary humidification acts in the direction of reducing the amount of humidified air at the outlet of the mixer 9 because the amount of steam for driving the mixer is reduced when the amount of steam delivered is constant. However, the increase in the amount of humidified air due to evaporation of water in auxiliary humidification is larger. Therefore, the auxiliary humidification increases the amount of humidified air at the outlet of the auxiliary humidifier 12 and increases the amount of humidified air guided to the combustor 2, and thus acts to increase the power generation output.

  In the present embodiment in which the auxiliary humidifier 12 is provided in addition to the regenerator bypass, the range in which the power generation output and the amount of steam to be delivered can be adjusted to arbitrary output and the amount of steam can be widened by the action of the auxiliary humidifier 12 described above. effective.

  The effect of the present embodiment will be described with reference to FIG.

  FIG. 5 is an explanatory diagram showing the relationship between the power generation output and the amount of delivered steam in Example 2 of the present invention compared with the operating characteristics of the comparative example and Example 1.

  A characteristic curve (1) in FIG. 5 is an operation characteristic of the comparative example. A characteristic curve (2) is an operation characteristic when the regenerator bypass ratio is 30% in the first embodiment of the present invention. Characteristic curves (3) and (4) are operational characteristics of Example 2 of the present invention, and are operational characteristics when auxiliary humidification is performed at a regenerator bypass ratio of 30% and a regenerator bypass ratio of 50%, respectively.

  In FIG. 5, when the characteristic curves (2) and (3) having the same regenerator bypass ratio are compared, the characteristic curve (3) when the auxiliary humidification is performed is the characteristic curve (2) when only the regenerator bypass is used. Compared with, the power generation output at the same amount of steam delivered is larger.

  Further, comparing the characteristic curves (3) and (4) in which both perform auxiliary humidification, the power generation output at the same delivery steam amount increases as the regenerator bypass ratio increases.

  Therefore, it can be seen that by providing the auxiliary humidifier 12 in addition to the regenerator bypass, the range in which the power generation output and the amount of steam to be delivered can be adjusted to any output and amount of steam can be made wider than in the first embodiment.

  In Example 2 of the present invention, it is possible to operate the regenerator bypass ratio at 0% and without auxiliary humidification, and in this case, the characteristic is the same as the characteristic curve (1) of the comparative example. .

  FIG. 3 is an overall configuration diagram showing Embodiment 3 of the gas turbine cogeneration system using high humidity air according to the present invention. Description of the same parts as those in the first embodiment shown in FIG. 1 and the second embodiment shown in FIG. 2 is omitted. In the present embodiment, in addition to the configuration of the second embodiment shown in FIG. 2, an air cooling device 15, an air cooling water supply pump 16, and an air cooling water control valve 44 are provided. The air cooling device 15 is provided on the upstream side of the air inlet of the air compressor 1 (near the air inlet), and reduces the compressor power by lowering the specific volume by lowering the air temperature. The air cooling feed pump 16 supplies water to the air cooling device 15. The air cooling water control valve 44 is controlled by a control device (not shown) in the same manner as the mixer driving steam flow control valve 42, the regenerator bypass flow control valve 43, and the auxiliary humidifying water control valve 41. .

  As the air cooling device 15, an evaporative cooler method, a chiller method, a fogging method, an overfogging method, or the like can be applied.

  In the evaporative cooler method, an element that allows water to flow down is provided downstream of the intake filter chamber of the compressor, and the air temperature at the compressor inlet (air inlet) is lowered by the latent heat of water evaporation. It does n’t go down below.

  The chiller system is a system in which an air cooling coil is provided in the downstream of the intake filter chamber of the compressor and chilled water is supplied from a chiller such as a centrifugal chiller to cool the air at the compressor inlet. Although the intake air temperature can be lowered, the initial investment is increased by installing a chiller.

  The fogging method is a method in which fine water droplets that are evaporated to the compressor inlet are sprayed downstream of the compressor intake filter chamber, and the compressor inlet air temperature is lowered by the latent heat of evaporation. The effect is low at high humidity because it does not drop below the wet bulb temperature as in the TIB cooler system.

  The overfogging method is a method in which a relatively large amount of fine water droplets are sprayed to the wake of the intake filter chamber of the compressor, as disclosed in Japanese Patent No. 2877098 and Japanese Patent No. 42855781, etc. is there. In the overfogging method, as with the fogging method, part of the sprayed water droplets evaporates before being sucked into the air compressor, reducing the air temperature at the compressor inlet (air suction port) and increasing the amount of sucked air. Also, the remaining water droplets (water droplets that have not evaporated at the compressor inlet) evaporate in the compression process to lower the air temperature in the compressor, so that the power for driving the compressor is reduced in the same manner as the intermediate cooler. effective.

  Therefore, it is preferable to apply an overfogging air cooling device as the air cooling device 15 in this embodiment. The overfogging type air cooling device in this embodiment is a control that controls the number of water spray nozzles provided in the air flow path, the pressure of high-pressure water supplied to the water spray nozzles, and / or the number of water spray nozzles to be operated. Equipment.

  In the present embodiment, in addition to the configuration of the second embodiment, an air cooling device 15 is installed, and the air cooling device 15 is configured to reduce the specific volume of air by lowering the air temperature by its operation. In this embodiment, in addition to the effects of the first and second embodiments, the following operational effects are obtained.

  That is, in such a system configuration, if, for example, a fogging system is adopted as the air cooling device 15, the amount of air sucked into the compressor 1 increases due to the decrease in the air specific volume, and the gas turbine output increases. Output increases. Further, when the overfogging method is adopted as the air cooling device 15, the effect of reducing the compressor power due to the effect of the intermediate cooling is added, so that the power generation output is further increased.

  In the present embodiment provided with the air cooler 15 in addition to the regenerator bypass and the auxiliary humidifier 12, the power generation output and the amount of steam to be delivered are adjusted to an arbitrary output and steam amount, respectively, due to the effect of the air cooler 15 described above. This has the effect of further expanding the possible range.

  Therefore, according to the present embodiment, the regenerator bypass line 26, the auxiliary humidifier 12 and the air cooler 15 are combined even when the gas turbine is operated as efficiently as possible, for example, when the combustion gas at the combustor outlet is operated at the rated temperature. By operating, within a certain range (within the operating characteristics of the system), the power generation output and the amount of steam to be delivered can be set to an arbitrary output and amount of steam, respectively. For example, there is an effect that the power generation output can be increased / decreased while the amount of steam delivered is maintained, or the amount of steam delivered can be increased / decreased while the necessary power generation output is maintained.

  The effect of the present embodiment will be described with reference to FIG.

  FIG. 6 is an explanatory diagram showing the relationship between the power generation output and the amount of delivered steam in Example 3 of the present invention compared with the operating characteristics of Comparative Example and Example 2.

  A characteristic curve (1) in FIG. 6 is a characteristic curve of a comparative example. A characteristic curve (2) is a characteristic curve in the case where auxiliary humidification is performed in addition to the regenerator bypass ratio of 30% in the second embodiment. A characteristic curve (3) is a characteristic curve of the third embodiment. In addition to the regenerator bypass ratio of 30% and auxiliary humidification, minute water droplets corresponding to 2% by weight of the intake air flow rate of the compressor 1 are compressed and introduced into the compressor. The characteristics are shown when the air cooling device 15 is operated under the condition that the entire amount evaporates while passing through the machine.

  As shown in FIG. 6, the characteristic curve (3) when the air cooling device 15 is operated is the characteristic curve when the auxiliary humidification is performed at a regenerator bypass ratio of 30% as well as the characteristic curve (1) of the comparative example ( Compared to 2), it shows that the power generation output can be increased with the same amount of delivered steam.

  Therefore, by providing the air cooler 15 in addition to the regenerator bypass line 26 and the auxiliary humidifier 12, the power generation output can be increased or decreased while maintaining the amount of steam delivered, or the amount of steam delivered while maintaining the necessary power generation output. It can be seen that there is an effect that it is possible to further widen the range in which the value can be increased or decreased.

  In this embodiment, in addition to the configuration of the second embodiment shown in FIG. 2, an air cooling device 15 and an air cooling feed water pump 16 are provided. In addition to the configuration of the first embodiment shown in FIG. The air cooling device 15 and the air cooling water supply pump 16 may be provided. Even in this case, there is an effect that the range in which the power generation output can be increased / decreased while the amount of delivered steam is maintained, or the range in which the amount of delivered steam can be increased / decreased while the necessary power generation output is maintained can be widened.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

DESCRIPTION OF SYMBOLS 1 Air compressor 2 Combustor 3 Turbine 4 Exhaust heat boiler 5 Generator 6 Feed water heater 7 Regenerator 9 Mixer 10 Water feed pump 11 Chimney 12 Auxiliary humidifier 13 Auxiliary humidifier water pump 15 Air cooling device 16 Air cooling water pump 21 Compressed air line 22 Steam line for driving mixer 23 Humidified air line 24 High temperature humidified air line 25 Steam delivery line 26 Regenerator bypass line 27 Compressed air branch line 29 Auxiliary humidified water supply line 30 Air cooling water supply line 41 Auxiliary humidified water control Valve 42 Mixer-driven steam flow control valve 43 Regenerator bypass control valve 44 Air cooling water control valve A Air F Fuel S Steam HA Humidified air E Gas turbine exhaust gas W Water supply

Claims (6)

A gas turbine composed of an air compressor, a combustor, and a turbine;
A mixer that mixes compressed air with steam to produce humidified air;
A regenerator provided downstream of the turbine and heating the humidified air using the exhaust gas of the turbine as a heat source;
An exhaust heat boiler that is provided downstream of the regenerator and generates steam using the exhaust gas of the turbine as a heat source;
A compressed air line connecting the air compressor and the combustor;
A compressed air branch line branched from the middle of the compressed air line to reach the mixer;
A mixer driving steam line connecting the exhaust heat boiler and the mixer;
A steam delivery line for delivering steam generated in the exhaust heat boiler to another steam utilization system;
A humidified air line connecting the outlet of the mixer and the inlet of the regenerator;
A high-temperature humidified air line connecting the outlet of the regenerator and the combustor;
A regenerator bypass line branched from the middle of the humidified air line to reach the high-temperature humidified air line;
A regenerator bypass flow control valve provided in the humidified air line or the regenerator bypass line;
A control device for controlling the valve opening of the regenerator bypass flow control valve;
When the control device wants to increase the power generation output generated by the gas turbine without changing the amount of steam delivered to the steam delivery line, the regenerator bypass ratio of the humidified air passing through the regenerator bypass line The high-humidity air-utilized gas turbine cogeneration system is characterized in that the valve opening of the regenerator bypass flow control valve is adjusted so as to increase the value. A gas turbine composed of an air compressor, a combustor, and a turbine;
A mixer that mixes compressed air with steam to produce humidified air;
A regenerator provided downstream of the turbine and heating the humidified air using the exhaust gas of the turbine as a heat source;
An exhaust heat boiler that is provided downstream of the regenerator and generates steam using the exhaust gas of the turbine as a heat source;
A compressed air line connecting the air compressor and the combustor;
A compressed air branch line branched from the middle of the compressed air line to reach the mixer;
A mixer driving steam line connecting the exhaust heat boiler and the mixer;
A steam delivery line for delivering steam generated in the exhaust heat boiler to another steam utilization system;
A humidified air line connecting the outlet of the mixer and the inlet of the regenerator;
A high-temperature humidified air line connecting the outlet of the regenerator and the combustor;
A regenerator bypass line branched from the middle of the humidified air line to reach the high-temperature humidified air line;
A regenerator bypass flow control valve provided in the humidified air line or the regenerator bypass line;
A control device for controlling the valve opening of the regenerator bypass flow control valve;
When the control device wants to increase the amount of steam delivered to the steam delivery line without changing the power generation output generated by the gas turbine, the regenerator bypass line corresponds to the increase in the amount of delivered steam. A high-humidity air-utilizing gas turbine cogeneration system , wherein a valve opening degree of the regenerator bypass flow rate control valve is adjusted so as to increase a regenerator bypass rate of the humidified air passing through the air . A gas turbine composed of an air compressor, a combustor, and a turbine;
A mixer that mixes compressed air with steam to produce humidified air;
A regenerator provided downstream of the turbine and heating the humidified air using the exhaust gas of the turbine as a heat source;
An exhaust heat boiler that is provided downstream of the regenerator and generates steam using the exhaust gas of the turbine as a heat source;
A compressed air line connecting the air compressor and the combustor;
A compressed air branch line branched from the middle of the compressed air line to reach the mixer;
A mixer driving steam line connecting the exhaust heat boiler and the mixer;
A steam delivery line for delivering steam generated in the exhaust heat boiler to another steam utilization system;
A humidified air line connecting the outlet of the mixer and the inlet of the regenerator;
A high-temperature humidified air line connecting the outlet of the regenerator and the combustor;
A regenerator bypass line branched from the middle of the humidified air line to reach the high-temperature humidified air line;
A regenerator bypass flow control valve provided in the humidified air line or the regenerator bypass line;
A control device for controlling the valve opening of the regenerator bypass flow control valve;
When the control device wants to increase the power generation output generated by the gas turbine without changing the amount of steam delivered to the steam delivery line, the humidified air from the mixer passing through the regenerator bypass line. If the regenerator bypass flow control valve opening is adjusted so as to increase the regenerator bypass flow rate and it is desired to increase the amount of steam delivered without changing the power generation output, increase the amount of steam delivered. Correspondingly , the high-humidity air use gas is characterized by adjusting the valve opening of the regenerator bypass flow control valve so as to increase the regenerator bypass rate of the humidified air passing through the regenerator bypass line. Turbine cogeneration system. In the high humidity air utilization gas turbine cogeneration system in any one of Claims 1-3,
A high-humidity air-based gas turbine cogeneration system comprising an auxiliary humidifier that adds water to the humidified air flowing through the humidified air line. In the high humidity air utilization gas turbine cogeneration system according to claim 4 ,
An air cooling device for reducing the temperature of the air at the air inlet of the air compressor or the air inlet of the air compressor and the air during the compression process in the air compressor is provided upstream of the air compressor. A high-humidity air-utilized gas turbine cogeneration system characterized by being provided. In the high humidity air utilization gas turbine cogeneration system in any one of Claims 1-3,
An air cooling device for reducing the temperature of the air at the air inlet of the air compressor or the air inlet of the air compressor and the air during the compression process in the air compressor is provided upstream of the air compressor. A high-humidity air-utilized gas turbine cogeneration system characterized by being provided.

Images