KR101628619B1 - generation system having temperature control device for heat exchanger - Google Patents

generation system having temperature control device for heat exchanger Download PDF

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Publication number
KR101628619B1
KR101628619B1 KR1020150062436A KR20150062436A KR101628619B1 KR 101628619 B1 KR101628619 B1 KR 101628619B1 KR 1020150062436 A KR1020150062436 A KR 1020150062436A KR 20150062436 A KR20150062436 A KR 20150062436A KR 101628619 B1 KR101628619 B1 KR 101628619B1
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South Korea
Prior art keywords
working fluid
temperature
heat exchanger
heater
temperature controller
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KR1020150062436A
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Korean (ko)
Inventor
김상현
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두산중공업 주식회사
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/006—Auxiliaries or details not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/26—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines

Abstract

The present invention relates to a power generation system having a temperature control device for a heat exchanger. The power generation system having a temperature control device for a heat exchanger comprises: a circulation device to circulate a working fluid; a heater to heat the working fluid; a turbine to expand the working fluid heated by the heater; a recuperator to exchange heat between the working fluid flowing into the heater and the working fluid passing through the turbine; a cooler to cool the working fluid passing through the recuperator; and a plurality of temperature controllers to exchange heat with the working fluid flowing into the recuperator. According to the present invention, a temperature of a heat exchanger can be controlled even when operating in a condition outside an optimal design point to minimize efficiency degradation of the heat exchanger and improve energy transfer and power generation efficiency of the system.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a temperature control apparatus for a heat exchanger,

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power generation system having a temperature control device for a heat exchanger, and more particularly, to a power generation system having a temperature control device for a heat exchanger capable of improving power generation efficiency of the system.

Internationally, there is a growing need for efficient power generation. As the movement to reduce pollutant emissions becomes more active, various efforts are being made to increase the production of electricity while reducing the generation of pollutants. Research and development of a supercritical carbon dioxide power generation system using supercritical carbon dioxide as a working fluid has been promoted as disclosed in JP-A-2012-145092.

Since supercritical carbon dioxide has a gas-like viscosity at a density similar to that of a liquid state, it can minimize the power consumption required for compression and circulation of the fluid as well as miniaturization of the apparatus. At the same time, the critical point is 31.4 degrees Celsius, 72.8 atmospheres, and the critical point is much lower than the water at 373.95 degrees Celsius and 217.7 atmospheres, which is easy to handle. This supercritical carbon dioxide power generation system shows a net generation efficiency of about 45% when operating at 550 ° C, and it improves the power generation efficiency by more than 20% compared to the existing steam cycle power generation efficiency and reduces the turbo device to one- There are advantages.

However, such a conventional supercritical carbon dioxide power generation system has a problem that the heat exchanger is difficult to exert optimum performance in an operation section outside the optimal design point, because the heat exchanger is designed based on the temperature, pressure, and flow rate corresponding to the optimum design point of the cycle . Particularly, when a fluid having a large change in physical properties such as specific heat, conductivity, and viscosity is used depending on temperature, the performance of the heat exchanger deteriorates greatly.

Japanese Patent Laid-Open Publication No. 2012-145092 (published on Aug. 02, 2012)

It is an object of the present invention to provide a power generation system having a temperature control device for a heat exchanger that can control the temperature of the heat exchanger and thereby improve energy transfer efficiency and power generation efficiency of the system.

A power generation system having a temperature control device for a heat exchanger according to the present invention includes a circulation device for circulating a working fluid, a heater for heating the working fluid, a turbine for expanding the working fluid heated by the heater, A recuperator for exchanging heat between the working fluid and the working fluid through the turbine; a cooler for cooling the working fluid through the recuperator; and a plurality of heat exchangers for heat exchange with the working fluid flowing into the recuperator Of the temperature controller.

The temperature controller may include a first temperature controller provided between the circulator and the recuperator, and a second temperature controller provided between the turbine and the recirculator.

The circulation device may comprise a pump or a compressor.

And the temperature of the working fluid flowing into the first temperature controller is higher than the temperature of the working fluid flowing into the second temperature controller.

Wherein the temperature controller cools the working fluid when the temperature of the recuperator is higher than the set temperature and heats the working fluid when the temperature of the recuperator is lower than the set temperature.

The temperature controller may include at least one of a heater, a cooler, and a heat pump

According to another aspect of the present invention, there is provided a power generation system having a temperature control device for a heat exchanger, including a compressor for compressing a working fluid, a plurality of heaters for heating the working fluid compressed through the compressor, Pressure turbine, a low-pressure turbine for expanding the working fluid that has passed through the high-pressure turbine, and a working fluid passing through the low-pressure turbine and the working fluid sent to one of the heaters through the compressor A cooler that is connected to a front end of the compressor to cool the working fluid that has passed through the heat exchanger to supply the working fluid to the compressor and an inlet end through which the working fluid flows into the heat exchanger, And a temperature controller for controlling the temperature of the substrate.

The heater includes a first heater that heats the working fluid that has passed through the low pressure turbine and a second heater that heats by flowing a part of the working fluid that has passed through the high pressure turbine, And the working fluid passing through the heater is mixed and introduced into the heat exchanger.

The temperature controller includes a first temperature controller and a second temperature controller, and the first temperature controller is disposed between the compressor and the heat exchanger.

The second temperature controller may be provided at a front end of the heat exchanger after a point where the working fluid passing through the first heater and the second heater is mixed.

Wherein the temperature controller cools the working fluid when the temperature of the heat exchanger is higher than the set temperature and heats the working fluid when the temperature of the heat exchanger is lower than the set temperature.

The temperature controller may be a recuperator that exchanges heat between the working fluid that has passed through the first heater and the second heater and the working fluid that has passed through the compressor.

The temperature controller may include at least one of a heater, a cooler, and a heat pump.

The power generation system having the temperature control device for the heat exchanger according to the embodiment of the present invention can control the temperature of the heat exchanger even if the power generation system operates at a condition outside the optimum design point to minimize the efficiency deterioration of the heat exchanger, The power generation efficiency can be improved.

1 is a block diagram showing an example of a temperature controller for controlling the temperature of a heat exchanger,
2 is a block diagram illustrating an example of a power generation system having a temperature controller for a heat exchanger according to an embodiment of the present invention.

Hereinafter, a power generation system having a temperature control device for a heat exchanger according to an embodiment of the present invention will be described in detail with reference to the drawings.

1 is a block diagram showing an example of a temperature controller for controlling the temperature of a heat exchanger.

1, a temperature controller according to an embodiment of the present invention can be used for temperature control of a heat exchanger of a power generation system using a working fluid whose physical properties such as specific heat, conductivity, and viscosity change depending on temperature .

For example, the temperature controller circulates or compresses the working fluid by means of a pump 10 or a compressor (not shown), then supplies the operating fluid to a recuperator (heat exchanger) 20 for heat exchange, 20 through a plurality of turbines 30, 40 while generating a power through a generator connected to the turbines 30, 40. The turbine 30,

In this case, the temperature controller may include a first heat exchanger 15 and a second heat exchanger 45 provided at the inlet on the high-temperature side of the recuperator 20 and the inlet on the low-temperature side. The temperature controller includes the heaters 25 and 27 provided at the front ends of the first turbine 30 and the second turbine 40 and the cooler 23 provided at the rear end of the recuperator 20 You may.

The working fluid can be heated or cooled primarily through the first heat exchanger 15 before the high-pressure working fluid compressed through the pump 10 or the compressor is supplied to the recuperator 20. The high-temperature, high-pressure working fluid heated while passing through the recuperator 20 after passing through the first heat exchanger 15 is heated via the first heater 25 and branched toward the first turbine 30, (30). The working fluid sent to the second heater 27 after passing through the first heater 25 is supplied to the second turbine 40 in a reheated state while passing through the second heater 27 and is supplied to the second turbine 40 ).

The working fluid passing through the first turbine 30 and the working fluid passing through the second turbine 40 are mixed and sent to the recuperator 20 where the second heat exchanger 45 To exchange heat with the working fluid.

Thereafter, the working fluid that has passed through the recuperator 20 is cooled by releasing heat to the outside while passing through the cooler 23, and is circulated to the pump 10 or the compressor in a cooled state.

Although not shown in the drawing, a valve may be provided at a branch point where the flow of the working fluid is branched by the temperature controller. The entire flow rate of the working fluid can be directly sent to the recirculator 20 using a valve or a part or all of the flow rate of the working fluid can be passed through the temperature controller.

The first heat exchanger 15 and the second heat exchanger 45 heat the working fluid when the temperature of the recuperator 20 is insufficient and the recuperator 20 is overheated or the temperature of the working fluid is excessively high The temperature of the recuperator 20 can be controlled by cooling the working fluid when the temperature is high.

More specifically, when a part of the working fluid flow rate is further heated while passing through the temperature controller, the temperature of the working fluid flowing into the recuperator 20 is increased by mixing with the remaining unheated working fluid. On the other hand, when a part of the working fluid flow rate is cooled while passing through the temperature controller, it is mixed with the remaining uncooled working fluid to lower the temperature of the working fluid flowing into the recuperator 20. Thus, the temperature of the recirculator 20 can be controlled.

The temperature controller can be configured in various forms such as a heater or a heat pump, a heat exchanger that receives heat from a heat source and supplies it to a working fluid, or a heat exchanger that takes heat from a working fluid. When the temperature controller is constituted by a heater, the heater may be a heater operated by electric energy or a waste heat recoverer installed in a thermal power plant or the like.

Temperature control using the pump 10 is also possible for temperature control of the temperature controller.

If the temperature of the working fluid (flow flowing under the recuperator based on FIG. 1) flowing into the recuperator 20 through the first turbine 30 or the second turbine 40 is too low, The temperature of the working fluid flowing in the system through reducing the flow rate of the unheated working fluid (flow flowing from the left side of the recuperator based on Fig. 1) supplied to the recuperator 20 via the circulating line 10 Can be controlled.

Conversely, if the temperature of the working fluid (flow flowing under the recuperator based on FIG. 1) flowing into the recuperator 20 through the first turbine 30 or the second turbine 40 is too high, The temperature of the working fluid flowing through the system is increased by increasing the flow rate of the unheated working fluid (the flow flowing from the left side of the recuperator based on Fig. 1) supplied to the recuperator 20 Can be controlled. A valve or the like may be additionally provided at the inlet side of the recuperator 20 for controlling the flow rate of the working fluid.

In the foregoing, the case where the temperature controller is used as a heater, a cooler, or a heat exchanger that can serve as both of them has been described. Hereinafter, a specific power generation system will be described in detail as to how the temperature controller of the present invention is used in the power generation system.

Generally, a supercritical carbon dioxide power generation system forms a closed cycle that does not discharge the carbon dioxide used for power generation, and uses supercritical carbon dioxide as a working fluid.

Since the supercritical carbon dioxide power generation system uses carbon dioxide as the working fluid, it can be used not only in a single power generation system but also in a hybrid power generation system with a thermal power generation system, since exhaust gas discharged from a thermal power plant can be used. The working fluid of the supercritical carbon dioxide power generation system may separate carbon dioxide from the exhaust gas and supply the carbon dioxide separately.

The carbon dioxide in the cycle is passed through a compressor and then heated while passing through a heat source such as a heater to become a high-temperature high-pressure supercritical state, and a supercritical carbon dioxide fluid drives the turbine. The turbine is connected to a generator, which is driven by the turbine to produce power. The carbon dioxide used in the production of electric power is cooled through the heat exchanger, and the cooled working fluid is supplied to the compressor again to circulate in the cycle. A plurality of turbines or heat exchangers may be provided.

The present invention proposes a power generation system having a temperature control device for a heat exchanger capable of improving the efficiency of a system by adding a configuration capable of controlling the temperatures of a plurality of heat exchangers provided in the basic supercritical carbon dioxide power generation system. A flow path through which a working fluid flows in the system is defined as a working fluid feeding pipe, and a flow path branched separately from the working fluid feeding pipe is defined as a separate name.

The supercritical carbon dioxide power generation system according to various embodiments of the present invention is a system in which not only all of the working fluid flowing in a cycle is in a supercritical state but also most of the working fluid is in a supercritical state, It is used to include meaning.

Also, in various embodiments of the present invention, carbon dioxide is used as the working fluid, wherein carbon dioxide refers to pure carbon dioxide in the chemical sense, carbon dioxide in a state where the impurities are somewhat contained in general terms, and carbon dioxide in which at least one fluid is mixed Is used to mean a fluid in a state where the fluid is in a state of being fluidized.

2 is a block diagram illustrating an example of a power generation system having a temperature controller for a heat exchanger according to an embodiment of the present invention.

2, the supercritical carbon dioxide power generation system according to an embodiment of the present invention includes a working fluid supplier 50 that uses carbon dioxide as a working fluid and largely supplies a working fluid, (100), a main compressor (200) for compressing a working fluid, a first heat exchanger (300) for first heat exchange with a working fluid passed through the main compressor (200), a first heat exchanger A first heat exchanger 500 for exchanging heat with a working fluid that has passed through the second heat exchanger 400 and a second heat exchanger 400 for performing an operation through the first heater 500 Pressure turbine 600 driven by the fluid, a second heater 530 for re-heating the working fluid through the high-pressure turbine 600, and a low-pressure turbine 600 driven by the working fluid passing through the second heater 530. [ And a third heat exchanger (not shown) which is finally heat-exchanged with the working fluid before being introduced into the cooler 100 900). A flash tank 150 may be additionally provided between the cooler 100 and the main compressor 200. It is to be understood that each configuration of the present invention is connected by a transfer pipe through which the working fluid flows, and that the working fluid flows along the transfer pipe even if not specifically mentioned. In the case of a separate functioning channel, a further description will be given.

The working fluid is injected into the system through the injection valve 54, which is connected to the working fluid supply 50. The injected gaseous working fluid is injected into the cooler 100 and cooled.

The gaseous working fluid injected into the cooler 100 undergoes a phase change into a liquid state while being cooled. At the rear end of the cooler 100, a cooler flow rate control valve 102 is provided to control the flow rate of the liquid working fluid injected into the flash tank 150.

The flash tank 150 is configured to prevent the liquid working fluid from flowing back toward the cooler 100 because the supercritical carbon dioxide power generation system of the present invention is configured in Rankine cycle so that the working fluid changes phase between the liquid state and the gas state . The front end of the cooler 100 and the flash tank 150 are connected by a tank circulation bypass line 160 and a tank circulation control valve 164 is installed on the tank circulation bypass line 160. When the tank circulation control valve 164 is opened, the working fluid that is not liquefied and remains in a gaseous state is sent to the cooler 100 by the tank circulation bypass line 160. The liquid working fluid passing through the flash tank 150 is compressed to a high pressure by the main compressor 200.

The high-pressure working fluid compressed in the main compressor 200 is sent to the third heat exchanger 900 through the compressor outlet-side regulating valve 202 provided at the rear end of the main compressor 200. A main compressor circulation line 210 is connected between the compressor outlet side regulating valve 202 and the main compressor 200 (branch point A), between the main compressor 200 and the flash tank 150, A main compressor circulation valve 212 is provided on the main compressor 210. The working fluid that has passed through the main compressor 200 by the main compressor circulation valve 212 can be bypassed to the front end of the main compressor 200 without going to the first heat exchanger 300 side. The main compressor circulation valve 212 is opened at the time of initial startup of the system (at the time of initial startup of the main compressor) and serves to circulate the working fluid until the working fluid warms up to drive the turbine . It also serves as an emergency safety valve. When the main compressor circulation valve 212 is opened, the compressor outlet side regulating valve 202 can be closed.

The working fluid recovered through the third heat exchanger 900 flows into the first heat exchanger 300 and the working fluid heated through the first heat exchanger 300 flows through the second heat exchanger 400 to the first And is sent to the heater 500.

The first heat exchanger 300 is a low temperature recuperator that recovers the working fluid and the second heat exchanger 400 is a high temperature recuperator that recovers the working fluid.

Here, the low temperature and high temperature mean that the first heat exchanger 300 is relatively low in temperature compared to the second heat exchanger 400 and the second heat exchanger 400 is relatively high in temperature as compared with the first heat exchanger 300 do. The working fluid passing through the first heat exchanger 300 and the second heat exchanger 400 is sent to the first heater 500 and the working fluid passing through the first heater 500 is sent to the high- (530) to the low-pressure turbine (700).

The first heater 500 and the second heater 530 transfer heat from the heat source to the working fluid of the supercritical carbon dioxide power generation system according to various embodiments of the present invention. Here, the heat source may be, for example, a facility or a device for discharging waste heat such as a steel plant, a chemical plant, a power plant, a fuel transportation line, etc. The first heater 500 receives heat from various heat sources other than the heat sources May be employed.

The high pressure turbine 600 and the low pressure turbine 700 are driven by a working fluid to generate electric power by driving a generator (not shown) connected to at least one of the turbines, And the low pressure turbine (700), the working fluid is expanded and thus also serves as an expander.

When the pressure of the working fluid flowing into the high-pressure turbine 600 becomes excessively high, an exhaust valve 520 serving as a safety valve is provided so that the working fluid can be exhausted to the outside of the cycle. The exhaust valve 520 is provided after the flow control valve 510 and is provided with a branch point between the flow control valve 510 and the exhaust valve 520 at which the working fluid flows into the high pressure turbine 600.

Here, the term high pressure turbine 600 and low pressure turbine 700 have a relative meaning, and it should be understood that a specific pressure is used as a reference value, and a higher pressure is not understood as a high pressure, and a lower pressure is not understood as a low pressure.

The working fluid that has been firstly expanded through the high pressure turbine 600 is sent to the second heater 530 to be reheated and the working fluid passing through the second heater 530 is sent to the low pressure turbine 700 . The working fluid that has been secondarily expanded through the low pressure turbine 700 is recovered to the first heat exchanger 300 and is firstly pressurized by the auxiliary compressor 800 and then flows into the cooler 100, .

A high temperature side working fluid delivery pipe 630 is provided between the high pressure turbine 600 and the second heat exchanger 400 and a high temperature side control valve 632 is provided on the high temperature side working fluid delivery pipe 630 Respectively. The working fluid sent to the second heat exchanger 400 through the high temperature side regulating valve 632 is mixed with the working fluid passing through the first heat exchanger 300 and passed through the auxiliary compressor 800 and then supplied to the cooler 100 .

On the other hand, a bypass flow path may be provided on the high pressure turbine 600, the low pressure turbine 700, and the auxiliary compressor 800, respectively.

The first heater 500 and the high-pressure turbine-side flow control valve 510 and the rear end of the high-pressure turbine 600 are connected by the high-pressure turbine-side turbine bypass line 610. The front end of the low pressure turbine side flow control valve 620 and the rear end of the low pressure turbine 700 are connected by the low pressure turbine side turbine bypass line 710. A high-pressure turbine bypass valve 612 and a low-pressure turbine bypass valve 712 are installed on the high-pressure turbine bypass line 610 and the low-pressure turbine bypass line 710, respectively. The high pressure turbine bypass valve 612 and the low pressure turbine bypass valve 712 can be selectively opened and closed when only the high pressure turbine 600 or the low pressure turbine 700 is to be operated.

The auxiliary compressor bypass line 810 is connected from the rear end of the auxiliary compressor 800 to the auxiliary compressor 800 and the bypass valve 812 is provided on the auxiliary compressor bypass line 810. A bypass bypass line 820 connected to the front end of the flash tank 150 is provided at a rear end (branch point B) of the auxiliary compressor 800 passing through the auxiliary compressor bypass line 810, A boosting regulating valve 822 is provided.

The bypass valve 812 provided on the auxiliary compressor bypass line 810 is opened at the time of initial startup of the system so that the boosting efficiency can be improved as compared with when the main compressor circulation valve 212 is opened only. The boosting control valve 822 is also opened during the initial start-up of the system and can serve to quickly start-up and increase the instantaneous flow rate of the system.

The main compressor circulation valve 212, the bypass valve 812, and the boosting control valve 822 are both closed when the initial operation of the system and the warming up of the working fluid are completed, so that the working fluid, which has passed through the main compressor 200, (300) and the second heat exchanger (400). The working fluid that has been heated by the absorption of heat from the first heater 500 and the second heater 530 is supplied to the high pressure turbine 600 and the low pressure turbine 700 and the high pressure turbine 600 and the low pressure turbine 700, Flow control valves 510 and 620 are provided at the front end of the low pressure turbine 600 and the low pressure turbine 700 to control the flow rate of the working fluid supplied to the high pressure turbine 600 and the low pressure turbine 700, respectively.

In the power generation system according to an embodiment of the present invention having the above-described configuration, a configuration for controlling the temperature of the heat exchanger may be added.

The apparatus for controlling the temperature of the heat exchanger may be provided on a plurality of paths through which the working fluid flows into the third heat exchanger 900.

That is, the first temperature controller 224 may be provided on the transfer pipe 220 through which the working fluid flows from the main compressor 200 to the third heat exchanger 900. In addition, on the transfer pipe through which the working fluid passing through the auxiliary compressor 800 and the second heat exchanger 400 is mixed and introduced into the third heat exchanger 900 after the branch point (branch point D) A temperature controller 830 may be provided.

The first temperature controller 224 is installed at the inlet of the low temperature section of the third heat exchanger 900 and the second temperature controller 830 is installed at the inlet of the high temperature section of the third heat exchanger 900.

The first temperature controller 224 and the second temperature controller 830 serve to introduce heat into the third heat exchanger 900 or to discharge heat from the third heat exchanger 900.

When the temperature of the working fluid sent to the third heat exchanger 900 through the main compressor 200 is expected to be lower than the set temperature, the first temperature controller 224 additionally applies heat to the working fluid, And then sent to the heat exchanger 900.

When the working fluid passing through the auxiliary compressor 800 and the second heat exchanger 400 is mixed at the branch point D and is sent to the third heat exchanger 900 and the temperature after the branch point D is expected to be higher than the set temperature, It is possible to take heat from the working fluid through the heat exchanger in the temperature controller 830 and supply the heat to the third heat exchanger 900.

Here, as the set temperature, a temperature corresponding to the optimum design point at which the thermodynamic cycle can achieve the optimum efficiency can be adopted.

The first temperature controller 224 and the second temperature controller 830 are connected to the third heat exchanger 900 according to whether the third heat exchanger 900 needs additional heat or needs to discharge heat The required temperature condition in the third heat exchanger 900 can be controlled by applying heat to the working fluid or depriving the working fluid of heat. Accordingly, the temperature of the third heat exchanger 900 can be controlled so as to approach the design point where the heat exchange efficiency is optimized, and the specific heat and the conductivity of the working fluid can also be controlled through the temperature control. This is an effective temperature control method over conventional methods which depend on the simple flow rate of the working fluid.

The first temperature controller 224 and the second temperature controller 830 are provided at the inlet of the third heat exchanger 900 on the high temperature side and the low temperature side of the third heat exchanger 900. However, The temperature controller 830 may also be provided at the inlet side of the other heat exchanger.

Here, the term low temperature part and high temperature part have a relative meaning, and it should be understood that a specific temperature is used as a reference value, higher temperature is higher temperature and lower temperature is not lower temperature.

In the above-described embodiment, the temperature control device for the heat exchanger has been described as an example of controlling the temperature of the third heat exchanger by heating the working fluid or depriving the working fluid of heat. However, the temperature control device may be a heater or a working fluid And a cooler for cooling the coolant. When the temperature control device is constituted by a heater or a cooler, it is preferable that a heater and a cooler are used together for temperature control of the heat exchanger.

As described above, the power generation system having the temperature control device for the heat exchanger according to the present invention can control the temperature of the heat exchanger even when operated under conditions outside the optimal design point, minimizing the efficiency deterioration of the heat exchanger, The power generation efficiency of the system can be improved.

One embodiment of the present invention described above and shown in the drawings should not be construed as limiting the technical spirit of the present invention. The scope of the present invention is limited only by the matters described in the claims, and those skilled in the art can improve and modify the technical spirit of the present invention in various forms. Accordingly, it is intended that the present invention cover the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.

10: pump 15: first heat exchanger
20: recuperator 23: cooler
25, 27: heater 30: first turbine
30: first turbine 40: second turbine
45: second heat exchanger
50: Working fluid supply 100: Cooler
150: flash tank 200: main compressor
224: first temperature controller 300: first heat exchanger
400: second heat exchanger 500: first heater
530: Second heater 600: High pressure turbine
700: Low pressure turbine 800: Secondary compressor
830: second temperature controller 900: third heat exchanger

Claims (13)

A circulation device for circulating the working fluid,
A heater for heating the working fluid,
A turbine for expanding the working fluid heated by the heater;
A recuperator that exchanges heat between the working fluid flowing into the heater and the working fluid passing through the turbine,
A cooler for cooling the working fluid through the recuperator,
And a plurality of temperature controllers for performing heat exchange with the working fluid flowing into the recuperator. The method according to claim 1,
Wherein the temperature controller includes a first temperature controller provided between a rear end of the circulation device and a front end of the recirculator and a second temperature controller provided between a rear end of the turbine and a front end of the recirculator, Power generation system with temperature control device. 3. The method of claim 2,
Wherein the circulation device has a temperature control device for a heat exchanger including a pump or a compressor. The method of claim 3,
Wherein the temperature of the working fluid flowing into the first temperature controller is higher than the temperature of the working fluid flowing into the second temperature controller. The method of claim 3,
Wherein the temperature controller cools the working fluid when the temperature of the recuperator is higher than the set temperature and heats the working fluid when the temperature of the recuperator is lower than the set temperature. Power generation system. The method of claim 3,
Wherein the temperature controller has a temperature control device for a heat exchanger including at least one of a heater, a cooler, and a heat pump. A compressor for compressing the working fluid,
A plurality of heaters for heating the working fluid compressed through the compressor,
A high pressure turbine for expanding the working fluid through the heater,
A low pressure turbine for expanding the working fluid that has passed through the high pressure turbine,
A heat exchanger for exchanging heat between the working fluid having passed through the low pressure turbine and the working fluid passing through the compressor and being sent to any one of the heaters;
A cooler connected to a front end of the compressor for cooling the working fluid passing through the heat exchanger and supplying the cooled working fluid to the compressor,
And a temperature controller provided at at least one of inlet ends through which the working fluid flows into the heat exchanger to control a temperature of the working fluid. 8. The method of claim 7,
Wherein the heater includes a first heater that heats the working fluid sent to the high pressure turbine and a second heater that heats a portion of the working fluid that has passed through the high pressure turbine and is heated, And the working fluid passing through the heater is mixed and introduced into the heat exchanger. 9. The method of claim 8,
Wherein the temperature controller includes a first temperature controller and a second temperature controller, wherein the first temperature controller is provided between a rear end of the compressor and a front end of the heat exchanger. . 10. The method of claim 9,
Wherein the second temperature controller is provided after a point (D) where the working fluid passing through the first heater and the second heater is mixed. 11. The method of claim 10,
Wherein the temperature controller cools the working fluid when the temperature of the heat exchanger is higher than the set temperature and heats the working fluid when the temperature of the heat exchanger is lower than the set temperature. system. 12. The method of claim 11,
Wherein the temperature controller is a recuperator that exchanges heat between the working fluid that has passed through the first heater and the second heater and the working fluid that has passed through the compressor. system. 11. The method of claim 10,
Wherein the temperature controller has a temperature control device for a heat exchanger including at least one of a heater, a cooler, and a heat pump.
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JP2012145092A (en) 2011-01-12 2012-08-02 Shintaro Ishiyama Centrifugal blower (compressor) for compressing supercritical carbon dioxide (co2), supercritical co2 gas turbine, and supercritical co2 gas turbine electric power generation technique including electric power generator
KR101431133B1 (en) * 2013-05-13 2014-08-18 한국해양과학기술원 OTEC cycle device that contains the ejector
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KR20070020449A (en) * 2004-06-01 2007-02-21 노보루 마사다 Highly efficient heat cycle device
JP2012145092A (en) 2011-01-12 2012-08-02 Shintaro Ishiyama Centrifugal blower (compressor) for compressing supercritical carbon dioxide (co2), supercritical co2 gas turbine, and supercritical co2 gas turbine electric power generation technique including electric power generator
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JP2015025423A (en) * 2013-07-26 2015-02-05 株式会社東芝 Carbon dioxide circulation type power generation system and carbon dioxide circulation type power generation method

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* Cited by examiner, † Cited by third party
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