WO2012176256A1 - Turbine à gaz en cycle fermé, et procédé d'actionnement de celle-ci - Google Patents

Turbine à gaz en cycle fermé, et procédé d'actionnement de celle-ci Download PDF

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Publication number
WO2012176256A1
WO2012176256A1 PCT/JP2011/064030 JP2011064030W WO2012176256A1 WO 2012176256 A1 WO2012176256 A1 WO 2012176256A1 JP 2011064030 W JP2011064030 W JP 2011064030W WO 2012176256 A1 WO2012176256 A1 WO 2012176256A1
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WO
WIPO (PCT)
Prior art keywords
pressure
temperature
compressor
gas turbine
closed cycle
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PCT/JP2011/064030
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English (en)
Japanese (ja)
Inventor
敏彦 福島
山本　敬
忠彦 高松
幸男 葉山
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熱技術開発株式会社
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Priority to PCT/JP2011/064030 priority Critical patent/WO2012176256A1/fr
Publication of WO2012176256A1 publication Critical patent/WO2012176256A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/10—Closed cycles

Definitions

  • the present invention relates to a closed-cycle gas turbine that can be started without impairing the reliability of a compressor, and an operation method thereof.
  • gas turbines that are widely used generally drive a compressor at about 55% of the turbine output, and the remaining 45% is used as power. For this reason, it is necessary to reduce the compressor driving power as much as possible in order to improve the efficiency of the gas turbine.
  • Patent Document 1 As a means for reducing compressor drive power, compression efficiency is generally improved. However, a significant improvement that can reduce the compression power by half cannot be expected only by improving the efficiency of the compressor. On the other hand, as disclosed in Patent Document 1 and Non-Patent Document 1, if a closed cycle gas turbine using CO 2 as the working fluid is operated at supercritical pressure, the power for driving the compressor is 20 It is known that it can be reduced to about%.
  • the evaluation of the operation at the supercritical pressure where the working fluid is CO 2 is an evaluation when the operation can be performed at the design point, and a method for starting the gas turbine and starting up to the state of the design point.
  • the temperature and pressure of the working fluid in each component device are equal to each other in the state before start-up in which CO 2 is sealed in the closed cycle gas turbine, and is not a supercritical pressure. Therefore, in order to start up from this state to the design point state, it is necessary to perform a start-up operation in which the compressor is driven by a motor, the working fluid is pressurized and circulated, heated by a heater, and the turbine becomes independent.
  • Patent Document 2 discloses a technique related to a closed cycle external combustion engine that performs compression, overheating, expansion, and cooling in a superheated steam region.
  • the working fluid at the compressor inlet is not in a supercritical state in this closed cycle, a significant power reduction effect cannot be expected even if the temperature of the working fluid at the compressor inlet is lowered. For this reason, the temperature change of the working fluid at the compressor inlet from the cycle start to the steady state is not considered.
  • the present invention has been made in view of the above circumstances, and can prevent the working fluid at the compressor inlet from entering a gas-liquid two-phase state at the start of the closed cycle gas turbine, and at the compressor inlet during the turbine output operation. It is an object of the present invention to provide a closed cycle gas turbine capable of reducing the driving power of a compressor by lowering the temperature of a working fluid and an operation method thereof.
  • a closed cycle gas turbine in which a compressor, a regenerator, a heater, a turbine, and a cooler are connected by a flow path so that a working fluid can be circulated, and a starter motor is connected to the compressor and the turbine.
  • a flow rate control valve for adjusting the flow rate of the cooling medium of the cooler, a pressure sensor for measuring the pressure of the working fluid in the inlet channel of the compressor, and an operation in the inlet channel of the compressor
  • a temperature sensor that measures the temperature of the fluid
  • a control signal for adjusting the flow rate control valve based on the pressure sensor and the pressure and temperature measured by the temperature sensor, and the flow rate based on the control signal
  • a closed cycle gas turbine having a control unit for controlling the control valve.
  • the control unit measures the pressure and temperature measured by the pressure sensor and the temperature sensor. And calculating the degree of superheat of the working fluid in the inlet passage of the compressor, and generating the control signal for adjusting the flow rate control valve to a predetermined value by adjusting the degree of superheat. Also good.
  • the control unit displays the temperature measured by the temperature sensor as the flow control valve.
  • the control signal for adjusting to a predetermined value may be generated.
  • control unit inputs the pressure and temperature measured by the pressure sensor and the temperature sensor, and inputs the data processor.
  • a controller inputs the pressure and temperature measured by the pressure sensor and the temperature sensor, and inputs the data processor.
  • An arithmetic unit for calculating the degree of superheat based on the pressure and temperature generated, and the control signal is generated based on the degree of superheat calculated by the arithmetic unit, and the flow control valve is controlled based on the control signal.
  • a controller a controller.
  • control unit inputs the pressure and temperature measured by the pressure sensor and the temperature sensor, and is input to the data processor. And a controller that generates the control signal based on the pressure and temperature and controls the flow control valve based on the control signal.
  • the present invention also provides the following means. (7)
  • a closed cycle gas turbine in which a compressor, a regenerator, a heater, a turbine, and a cooler are connected by a flow path so that a working fluid can be circulated, and a starter motor is connected to the compressor and the turbine.
  • a pressure measuring step for measuring the pressure of the working fluid in the inlet passage of the compressor
  • a temperature measuring step for measuring the temperature of the working fluid in the inlet passage of the compressor
  • a control step of controlling a flow rate control valve that adjusts the flow rate of the cooling medium of the cooler based on the pressure and temperature measured in the pressure measurement step and the temperature measurement step.
  • the pressure measurement step and the temperature measurement are performed in the control step. Based on the pressure and temperature measured in the process, the degree of superheat of the working fluid in the inlet channel of the compressor is calculated, and the flow control valve is controlled so that the degree of superheat becomes a predetermined value. May be.
  • control step measures the pressure in the temperature measurement step.
  • the flow control valve may be controlled so that the temperature becomes a predetermined value.
  • the present invention it is possible to prevent the working fluid at the compressor inlet from entering a gas-liquid two-phase state at the start of the closed cycle gas turbine, and to reduce the temperature of the working fluid at the compressor inlet during the turbine output operation.
  • the driving power of the compressor can be reduced.
  • the pressure and temperature of the working fluid at the compressor inlet are measured at the start for the purpose of preventing the working fluid at the compressor inlet from entering a gas-liquid two-phase state at the start of the closed cycle gas turbine.
  • a control means for controlling the flow rate of the cooling medium of the cooler based on these pressures and temperatures.
  • FIG. 1 shows a closed cycle gas turbine (hereinafter referred to as “cycle”) 100 according to a first embodiment of the present invention.
  • the cycle 100 includes a compressor 1, a turbine 2, a regenerator 3, a heater 4, a cooler 5, and a motor / generator 6 that is a starter motor / generator.
  • the compressor 1 and the turbine 2 are connected to a motor / generator 6 through a shaft 13 so as to be able to transmit power.
  • the cycle 100 forms a closed cycle by the flow paths P1 and P2, and the outlet of the compressor 1 and the inlet of the turbine 2 are connected by the flow path P1, and the regenerator 3 and the heater 4 are connected to the working fluid in the flow path P1.
  • the inlet of the compressor 1 and the outlet of the turbine 2 are connected by a flow path P2, and the regenerator 3 and the cooler 5 are installed in the flow path P2 in order along the flow direction of the working fluid.
  • Both the flow paths P1 and P2 are connected to the regenerator 3, and in the cycle 100, the working fluid exiting the compressor 1 exchanges heat with the working fluid exiting the turbine 2, and then flows into the heater 4. It is supposed to be.
  • a temperature sensor 7 and a pressure sensor 8 are attached to an inlet flow path E of the compressor 1 in the flow path P2, and a temperature signal and a pressure signal obtained from each sensor are a data processor 9, an arithmetic unit 10,
  • the controller 11 is input to the control unit C.
  • the control unit C generates a control signal based on the temperature signal and the pressure signal, and controls the flow rate control valve 12 provided in the cooling medium flow path 14 for supplying a cooling medium (not shown) to the cooler 5. It is configured to transmit (output) a signal.
  • CO 2 is used as a working fluid.
  • the cycle 100 contains a predetermined amount of CO 2 after evacuation.
  • As a heat source of the heater 4 exhaust heat of 300 ° C. or less can be used in addition to various known fuels.
  • the cooler 5 is cooled by a cooling heat medium having a temperature of about the outside air temperature.
  • a cooling heat medium (not shown) is passed through the cooler 5, and then the motor / generator 6 is used as a starter motor to drive the compressor 1 and the turbine 2.
  • the heating speed of the compressor 1 and the turbine 2 is increased while heating the CO 2 with the heater 4.
  • the inlet temperature T ci of the compressor 1 and the inlet pressure p ci of the compressor 1 measured by the temperature sensor 7 and the pressure sensor 8 are converted into electric signals by the data processor 9, and the control shown in FIG. According to the procedure, the superheat degree SH of CO 2 at the inlet of the compressor 1 is controlled.
  • step S1 the pressure sensor 8 measures the inlet pressure p ci of the compressor 1, and in step S2, the temperature sensor 7 measures the inlet temperature T ci of the compressor 1. To do.
  • step S3 the data processor 9 determines whether the inlet pressure p ci is greater than the critical pressure of CO 2, the inlet pressure p ci are critical pressure 7.38MPa of CO 2 (gauge pressure: 7 .28 MPaG) or less, the process proceeds to step S4, and when the inlet pressure p ci is higher than the critical pressure of CO 2 , the process proceeds to step S7.
  • step S4 the electrical signals of the temperature and pressure are transmitted to the computing unit 10, and the computing unit 10 uses the relationship between the pressure of CO 2 and the saturation temperature shown in FIG. 7 to calculate the saturation temperature T corresponding to the inlet pressure p ci. S is calculated.
  • the calculator 10 stores the relationship between the pressure and the saturation temperature as shown in FIG. 7 as a table or an approximate expression, but generally the value measured by the pressure sensor 8 is a gauge pressure. If the saturation temperature is arranged in relation to the gauge pressure as shown in Fig. 7, there is an advantage that the conversion operation from the gauge pressure to the absolute pressure can be omitted (MPaG means the gauge pressure).
  • step S5 the arithmetic unit 10, from the resulting saturation temperature T S and the inlet temperature T ci, by the following equation (1), calculates the degree of superheating SH of the CO 2 at the inlet of the compressor 1, the controller operation result 11 is transmitted.
  • step S6 the controller 11 generates a control signal for setting the superheat degree SH transmitted from the computing unit 10 to a preset target value SH (target), and this signal is used as the flow control valve 12.
  • SH (target) is 5 to 10 deg. (C) degree.
  • the processes in steps S1 to S6 are continued until the target value SH (target) is reached.
  • step S7 when the inlet pressure p ci becomes higher than the CO 2 critical pressure of 7.38 MPa (gauge pressure: 7.28 MPaG), the data processor 9 transmits the inlet temperature T ci to the controller 11. Then, the controller 11 transmits a signal to the flow rate control valve 12 so that the inlet temperature T ci becomes a predetermined target value, T ci (target), and the flow rate of the cooling medium flowing through the cooling medium flow path 14 is determined. adjust.
  • T ci (target) is about 31 ° C. in the present embodiment.
  • the controller 11 a normal PID controller can be used.
  • step S8 the continuation of operation of cycle 100 is monitored, and the processes of steps S1 to S3 and step S7 are continued until the operation is stopped.
  • the temperature of CO 2 at the inlet of the compressor 1 is set to 5 to 10 deg. Since it can be as high as (° C.), CO 2 at the inlet of the compressor 1 will not be in a two-phase state. Further, when the inlet pressure of the compressor 1 becomes higher than the critical pressure and the turbine 2 is in the output operation state, the inlet temperature of the compressor 1 can be lowered, so that the power for driving the compressor 1 can be reduced.
  • FIG. 3 shows a cycle 200 according to the second embodiment of the present invention.
  • the cycle 200 is different from the cycle 100 according to the first embodiment in that the arithmetic unit 10 shown in the cycle 100 is not installed.
  • movement of the cycle 200 is demonstrated.
  • the inlet temperature T ci of the compressor 1 and the inlet pressure p ci of the compressor 1 measured by the temperature sensor 7 and the pressure sensor 8 are converted into electric signals by the data processor 9, and are shown in FIG.
  • the temperature T ci at the inlet of the compressor 1 is controlled according to the control procedure shown.
  • step S11 the pressure sensor 8 measures the inlet pressure p ci of the compressor 1, and in step S12, the temperature sensor 7 detects the inlet temperature T ci of the compressor 1. Measure.
  • step S13 the data processor 9 determines whether the inlet pressure p ci is greater than the critical pressure of CO 2, the inlet pressure p ci are critical pressure 7.38MPa of CO 2 (gauge pressure: 7 .28 MPaG) or less, the process proceeds to step S14, and when the inlet pressure p ci is higher than the critical pressure of CO 2 , the process proceeds to step S15.
  • step S14 the measured compressor inlet temperature T ci is transmitted from the data processor 9 to the controller 11, and the controller 11 adjusts the flow rate so that this value becomes a predetermined target value, T ci (target 1).
  • a control signal is transmitted to the control valve 12 to adjust the flow rate of the cooling medium flowing through the cooling medium flow path 14.
  • T ci (target 1) is about 35 ° C.
  • step S15 when the inlet pressure p ci of the compressor 1 is higher than the critical pressure of CO 2 of 7.38 MPa (gauge pressure: 7.28 MPaG), this value is given as a predetermined target value, T ci (target 2 ),
  • T ci target 2
  • the control signal is transmitted to the flow control valve 12 so as to adjust the flow rate of the cooling medium flowing through the cooling medium flow path 14.
  • T ci target 2, second predetermined temperature
  • step S16 the continuation of operation of cycle 100 is monitored, and steps S11 to S13 and S15 are continued until the operation is stopped.
  • the arithmetic unit 10 is unnecessary, so the cycle configuration and the control procedure are compared with the cycle 100. There is an advantage that can be simplified.
  • FIG. 5 shows the state from the start to the steady operation of the cycle 200 according to the second embodiment on a Mollier diagram in which the vertical axis pressure (MPa) and the horizontal axis specific enthalpy (kJ / kg) are expressed. is there.
  • MPa vertical axis pressure
  • kJ / kg horizontal axis specific enthalpy
  • a broken line extending upward from the critical point is a quasi-critical line connecting points at which the specific heat steeply increases with respect to temperature change at each pressure.
  • the left side of the isothermal line at the critical temperature of 31.06 ° C. is the liquid phase and the right side is the gas phase, but the density changes greatly in the vicinity of the pseudocritical line.
  • the cycle points indicated by white circles ( ⁇ ) in the figure indicate the operation results of the cycle 200 according to the second embodiment.
  • Pre-start and black circles marked ( ⁇ ) (4.8MPa, 25.3 °C ) , after the CO 2 to a predetermined filling amount in the cycle, a state equilibrated at ambient temperature, CO 2 in each component device The temperature and pressure are equal.
  • the state started 15 minutes after starting the cycle in the above procedure is a rectangle connecting the white circles (O) marked 15 minutes later with a straight line, and the left oblique line is the change in CO 2 in the compressor 1 Is shown.
  • the rectangle which connected the white circle ((circle)) described as 60 minutes after with the straight line represents the state which the cycle became a steady operation about 60 minutes after starting.
  • the inlet of the compressor 1 is in a supercritical state of about 7.5 MPa and about 31 ° C.
  • the CO 2 is compressed to about 10.6 MPa and about 43 ° C. by the compressor 1, then heated to about 260 ° C. by the heater 4, expanded to about 7.7 MPa by the turbine 2, and returned to the compressor 1. .
  • the curve that is indicated by a broken line in the figure and that passes from the black circle ( ⁇ ) marked before start to the inlet state of the compressor 1 after 15 minutes through the inlet state of the compressor 1 after 15 minutes is the cycle
  • entrance state change in the compressor 1 from a start to a steady operation is shown.
  • the cycle 200 was started by setting T ci (target 1) shown in FIG. 4 to 35 ° C., but the inlet temperature T ci of the compressor 1 before starting was as low as 25.3 ° C., and the cooler 5 Since the temperature of the cooling medium circulating in the tank was low, T ci did not reach 35 ° C. until the compressor inlet pressure p ci exceeded the critical pressure. However, during this time, the CO 2 at the inlet of the compressor 1 did not enter a gas-liquid two-phase state.
  • T ci slightly overshooted 35 ° C., but eventually reached 31 ° C. and became a steady operation state.
  • FIG. 6 shows the change in the compressor driving power during the period from the point where p ci starts to decrease after reaching a peak after T ci slightly overshoots 35 ° C. This is shown in relation to the temperature T ci .
  • this specific output is indicated by a white circle ( ⁇ ) as a specific output ratio based on the specific output of the light black circle D1 (8.1 MPa, 34.1 ° C.) at the rightmost end in the figure.
  • the specific output of the inverter which is an evaluation index of compressor driving power, decreased by about 50% when the inlet temperature T ci decreased by about 3 ° C. from 34.1 ° C. to 31 ° C. After that, when the heat output of the heater 4 is increased and the inlet temperature of the turbine 2 is increased, the turbine 2 enters a so-called self-sustained operation that does not require the power of the motor / generator 6 and eventually enters a steady state.
  • the compression coefficient indicated by white triangles ( ⁇ ) in the figure is an index representing the non-ideality of a real gas defined by the following formula (2).
  • the value is 1 as the ideal gas is 1 and the non-ideality increases. Move away from 1.
  • p pressure (Pa)
  • v specific volume (m / kg)
  • R is a gas constant (188.92 J / kg ⁇ K)
  • T temperature (K).
  • the temperature of CO 2 at the inlet of the compressor 1 can be made higher than the critical temperature at the start of the cycle 200, so that the CO 2 at the inlet of the compressor 1 is in a two-phase state. Absent. Further, when the inlet pressure of the compressor 1 becomes higher than the critical pressure and the turbine 2 is in the output operation state, the inlet temperature of the compressor 1 can be lowered, so that the power for driving the compressor 1 can be reduced.
  • the closed cycle gas turbine can be started stably without damaging the compressor and the bearing. For this reason, it can be applied to a closed cycle gas turbine using various fuels, solar heat, biomass, industrial exhaust heat, and the like.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)

Abstract

L'invention concerne une turbine à gaz en cycle fermé dans laquelle un compresseur, un récupérateur, un appareil de chauffage, une turbine et un appareil de refroidissement sont connectés par un trajet d'écoulement permettant la circulation d'un fluide de fonctionnement, et dans laquelle un moteur de démarrage est connecté audit compresseur et à ladite turbine. La turbine à gaz en cycle fermé de l'invention possède : une valve de commande de débit qui régule le débit d'un agent de refroidissement dudit appareil de refroidissement; un capteur de pression qui évalue la pression du fluide de fonctionnement à l'intérieur du trajet d'écoulement côté entrée dudit compresseur; un capteur de température qui mesure la température du fluide de fonctionnement à l'intérieur du trajet d'écoulement côté entrée dudit compresseur; et une unité de commande qui produit des signaux de commande destinés à réguler ladite valve de commande de débit, sur la base de la pression et de la température mesurées par lesdits capteurs de pression et de température, et qui commande ladite valve de commande de débit, sur la base de ces signaux de commande.
PCT/JP2011/064030 2011-06-20 2011-06-20 Turbine à gaz en cycle fermé, et procédé d'actionnement de celle-ci WO2012176256A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015025423A (ja) * 2013-07-26 2015-02-05 株式会社東芝 二酸化炭素循環発電システムおよび二酸化炭素循環発電方法
CN114320493A (zh) * 2022-01-14 2022-04-12 中国能源建设集团浙江省电力设计院有限公司 一种9h级联合循环机组增压机组间的无扰切换方法
US20230203988A1 (en) * 2012-01-17 2023-06-29 Peregrine Turbine Technologies, Llc Acoustic System for Determining the Temperature of a Supercritical Fluid in a Conduit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02146227A (ja) * 1988-11-24 1990-06-05 Toshiba Corp 排熱利用システム
WO2006025449A1 (fr) * 2004-08-31 2006-03-09 Tokyo Institute Of Technology Collecteur de chaleur solaire, dispositif de réflexion de collecte de lumière solaire , système de collecte de lumière solaire et système utilisant l’énergie solaire
JP2008297962A (ja) * 2007-05-30 2008-12-11 Denso Corp 廃熱利用装置を備える冷凍装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02146227A (ja) * 1988-11-24 1990-06-05 Toshiba Corp 排熱利用システム
WO2006025449A1 (fr) * 2004-08-31 2006-03-09 Tokyo Institute Of Technology Collecteur de chaleur solaire, dispositif de réflexion de collecte de lumière solaire , système de collecte de lumière solaire et système utilisant l’énergie solaire
JP2008297962A (ja) * 2007-05-30 2008-12-11 Denso Corp 廃熱利用装置を備える冷凍装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230203988A1 (en) * 2012-01-17 2023-06-29 Peregrine Turbine Technologies, Llc Acoustic System for Determining the Temperature of a Supercritical Fluid in a Conduit
JP2015025423A (ja) * 2013-07-26 2015-02-05 株式会社東芝 二酸化炭素循環発電システムおよび二酸化炭素循環発電方法
CN114320493A (zh) * 2022-01-14 2022-04-12 中国能源建设集团浙江省电力设计院有限公司 一种9h级联合循环机组增压机组间的无扰切换方法
CN114320493B (zh) * 2022-01-14 2023-11-03 中国能源建设集团浙江省电力设计院有限公司 一种9h级联合循环机组增压机组间的无扰切换方法

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