KR101628616B1 - Supercritical CO2 generation system - Google Patents

Supercritical CO2 generation system Download PDF

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Publication number
KR101628616B1
KR101628616B1 KR1020150055368A KR20150055368A KR101628616B1 KR 101628616 B1 KR101628616 B1 KR 101628616B1 KR 1020150055368 A KR1020150055368 A KR 1020150055368A KR 20150055368 A KR20150055368 A KR 20150055368A KR 101628616 B1 KR101628616 B1 KR 101628616B1
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South Korea
Prior art keywords
working fluid
turbine
heat exchanger
flow
pump
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KR1020150055368A
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Korean (ko)
Inventor
김형진
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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
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • 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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

The present invention relates to a supercritical CO2 generating system comprising: a CO2 separator for separating CO2 which is working fluid from exhaust fumes generated by the combustion of fuels; a compressor for compressing the working fluid, connected to the back side of the CO2 separator; a pump for circulating the working fluid which has passed the compressor, connected to the back side of the compressor; a first heat exchanger for exchanging heat with the working fluid provided by the pump, connected to the back side of the pump; at least one turbine operated by the working fluid which has passed the first heat exchanger, connected to the back side of the first heat exchanger; a second heat exchanger for exchanging heat with the working fluid which has passed the turbine; and a first saving tank for saving the working fluid which has passed the compressor. By the composition, the present invention is capable of controlling the pressure and the rate of flow of working fluid as it desires, thereby enhancing the generation efficiency of the system and controlling the discharging of the greenhouse gas from a separate CO2 storage device.

Description

[0001] Supercritical CO2 generation system [0002]

The present invention relates to a supercritical carbon dioxide power generation system, and more particularly, to a supercritical carbon dioxide power generation system capable of controlling a pressure and a flow rate of a working fluid.

Internationally, there is an increasing need for efficient power generation. As the movement to reduce the generation of pollutants becomes more active, various efforts are being made to increase the production of electricity while reducing the generation of pollutants. As one of such efforts, research and development on a supercritical carbon dioxide (CO2) power generation system using supercritical carbon dioxide as a working fluid has been activated as disclosed in Korean Patent Laid-Open Publication No. 2013-0036180.

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 of Celsius is 31.4 degrees, 72.8 atmospheres, and the critical point is much lower than the water at 373.95 degrees, 217.7 atmospheres. 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, in the conventional supercritical carbon dioxide power generation system, pressure control of supercritical carbon dioxide, which is a working fluid, is performed through operation of the pump in a closed cycle. However, when the working fluid is in the liquid state, the control of the pump is easy, but when the working fluid is in the supercritical state or in the gaseous state, the control of the pump is very difficult.

Since the supercritical carbon dioxide power generation system is operated as a closed cycle in which the working fluid is not introduced or discharged, the flow rate of the working fluid can not be controlled. Therefore, the power generation system can be operated and operated only once, There is a problem that it is difficult to actively utilize.

Korean Patent Publication No. 2013-0036180 (Publication date 2013.04.11)

It is an object of the present invention to provide a supercritical carbon dioxide power generation system capable of controlling the pressure and flow rate of a working fluid.

A supercritical carbon dioxide power generation system of the present invention comprises a carbon dioxide separator for separating carbon dioxide which is a working fluid from an exhaust gas generated by combustion of fuel, a compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid, A first heat exchanger connected to a rear end of the first heat exchanger and circulating the working fluid through the compressor, a first heat exchanger connected to a rear end of the pump and performing heat exchange with the working fluid supplied by the pump, At least one turbine connected to the first heat exchanger and driven by the working fluid passed through the first heat exchanger, a second heat exchanger exchanging heat with the working fluid passing through the turbine, and a second heat exchanger 1 < / RTI > storage tank, wherein the turbine includes a first turbine connected to a downstream end of the first heat exchanger, And a second turbine driven by at least a part of the flow rate of the working fluid that has passed through the first turbine, wherein a first recuperator is provided between the first turbine and the second turbine, a second recuperator for recuperating the working fluid may be provided between the second turbine and the second heat exchanger.

Wherein the first storage tank is located downstream of the compressor and at the same time communicates with the downstream side of the second heat exchanger.

And the first heat exchanger supplies heat to the working fluid.

And the second heat exchanger cools the working fluid.

The first storage tank may include a safety valve provided to be openable and closable to exhaust the working fluid.

The first storage tank may further include a flow control valve provided to be openable and closable to send the working fluid to a rear end (branch point A) of the second heat exchanger.

And the inner pressure of the first storage tank is maintained higher than the pressure of the front end of the pump.

And a second storage tank provided between the pump and the first heat exchanger for temporarily storing the working fluid.

The second storage tank may include an oil separator for separating oil that lubricates the pump mixed with the working fluid.

And the oil separated from the oil separator is sent to the pump.

The second storage tank may further include a regulator provided to be openable and closable to discharge the working fluid.

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Wherein the flow of the working fluid is a first flow that is recuperated at the first recuperator and thereafter flows into the second turbine, heat exchanges with the fourth flow from the first recuperator, and then flows through the second turbine And a second flow mixed with the first flow, wherein the first flow and the second flow are mixed and then introduced into the second recuperator.

Wherein the flow of the working fluid includes a third flow flowing into the second heat exchanger from the second recuperator and a second flow branched from the pump to receive heat from the second recuperator and being sent to the first recuperator And the fourth flow.

And the working fluid having passed through the pump is branched and communicated to the front end of the second recirculator.

The supercritical carbon dioxide power generation system of the present invention includes a carbon dioxide separator for separating carbon dioxide, which is a working fluid, from exhaust gas generated by combustion of fuel, a compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid, A first heat exchanger connected to a rear end of the compressor and circulating the working fluid through the compressor, a first heat exchanger connected to a rear end of the pump and heating the working fluid supplied by the pump, A second heat exchanger connected to a rear end of the first heat exchanger and driven by the working fluid passing through the first heat exchanger, a second heat exchanger for cooling the working fluid passing through the turbine, A first storage tank for storing the fluid, and a second storage tank disposed between the first turbine and the second turbine, Is provided between the first buffer liqueur concentrator (recuperator) and the second turbine and the second heat exchanger recuperator may include a second buffer liqueur concentrator to double row the working fluid.

Wherein the first storage tank is located downstream of the compressor and at the same time communicates with the downstream side of the second heat exchanger.

The first storage tank may include a safety valve that is openably and closably provided to discharge the working fluid and a flow control valve that is openably and closably provided to transmit the working fluid to a rear end (branch point A) of the second heat exchanger have.

And the inner pressure of the first storage tank is maintained higher than the pressure of the front end of the pump.

And a second storage tank provided between the pump and the first heat exchanger for temporarily storing the working fluid.

The second storage tank may further include an oil separator for separating oil that lubricates the pump mixed with the working fluid, and a regulator that is openably and closably provided to discharge the working fluid. And the oil is sent to the pump.

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Wherein the flow of the working fluid is a first flow that is recuperated at the first recuperator and thereafter flows into the second turbine, heat exchanges with the fourth flow from the first recuperator, and then flows through the second turbine And a second flow mixed with the first flow, wherein the first flow and the second flow are mixed and then introduced into the second recuperator.

Wherein the flow of the working fluid includes a third flow flowing into the second heat exchanger from the second recuperator and a second flow branched from the pump to receive heat from the second recuperator and being sent to the first recuperator And the fourth flow.

And the working fluid having passed through the pump is branched and communicated to the front end of the second recuperator.

The supercritical carbon dioxide power generation system of the present invention includes a carbon dioxide separator for separating carbon dioxide, which is a working fluid, from exhaust gas generated by combustion of fuel, a compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid, A first heat exchanger connected to a rear end of the compressor and circulating the working fluid through the compressor, a first heat exchanger connected to a rear end of the pump and performing heat exchange with the working fluid supplied by the pump, At least one turbine connected to a downstream end of the turbine and driven by the working fluid passing through the first heat exchanger, a second heat exchanger for exchanging heat with the working fluid passing through the turbine, A first storage tank disposed between the pump and the first heat exchanger, And a second storage tank for temporarily storing the working fluid, wherein the second storage tank includes an oil separator for separating oil that lubricates the pump mixed with the working fluid, and a regulator and a third storage tank including a regulator for storing a working fluid discharged from the second storage tank through the regulator.
Wherein the turbine includes a first turbine connected to a rear end of the first heat exchanger and a second turbine driven by at least a partial flow rate of the working fluid passing through the first turbine, A second recuperator disposed between the second turbine and the second heat exchanger for recuperating the working fluid and a second recuperator provided between the second turbine and the second heat exchanger for recovering the working fluid; The third storage tank may include a control valve provided to be openable and closable to send the working fluid to the front end (branch point C) of the first recirculator.

The supercritical carbon dioxide power generation system according to an embodiment of the present invention can control the pressure and flow rate of the working fluid as desired to improve the power generation efficiency of the system and manage the greenhouse gas emission through a separate carbon dioxide storage device There are advantages.

1 is a block diagram illustrating a supercritical carbon dioxide power generation system according to an embodiment of the present invention,
2 is a block diagram illustrating a supercritical carbon dioxide power generation system according to another embodiment of the present invention.

Hereinafter, a supercritical carbon dioxide power generation system according to an embodiment of the present invention will be described in detail with reference to the drawings.

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.

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 carbon dioxide power generation system that controls the pressure and flow rate of a working fluid by providing a carbon dioxide storage tank and a valve for flow rate control in addition to the basic supercritical carbon dioxide power generation system.

A flow path through which a working fluid flows in the system is defined as a transport pipe, and a flow path separately branched from the transport pipe is defined as a separate name.

The term " supercritical carbon dioxide power generation system " according to various embodiments of the present invention is intended to encompass not only the system in which all of the working fluid flowing in the cycle is a supercritical state but also the supercritical state, System.

Also, in various embodiments of the present invention, carbon dioxide is used as the working fluid, wherein the term " carbon dioxide " refers to pure carbon dioxide in a chemical sense, carbon dioxide in a state of being somewhat impure and carbon dioxide in a general sense, As well as fluids in a mixed state.

1 is a block diagram illustrating a supercritical carbon dioxide power generation system according to an embodiment of the present invention.

1, a supercritical carbon dioxide power generation system according to an embodiment of the present invention includes a CO2 separator 100 for separating carbon dioxide, which is a working fluid, from a discharged exhaust gas as a by-product of a combustion process, A pump 300 for supplying the working fluid to the first heat exchanger 400 and supplying the working fluid to the first heat exchanger 400; a heat exchanger 300 for exchanging heat with the working fluid supplied from the pump 300; A first turbine 500 that is driven by a working fluid that has passed through the first heat exchanger 400 and a second turbine 500 that performs heat exchange with a working fluid that has passed through the first turbine 500. The first heat exchanger 400, And a heat exchanger (700).

Here, the first heat exchanger 400 has a function of a heat source, for example, a heater or a waste heat recovery apparatus can be employed, the second heat exchanger 700 has a function of a cooling source, A first recuperator 730 that recovers the working fluid that has passed through the first turbine 500 and a second recuperator 730 that recirculates the working fluid that has passed through the first recuperator 730 A second turbine 600 driven by the first heat exchanger 400 and a second heat exchanger 400 disposed between the carbon dioxide separator 100 and the second heat exchanger 700 and between the pump 300 and the first heat exchanger 400, And a storage tank for storing the liquid.

The second recuperator 750 is provided to recover the working fluid mixed with the working fluid passing through the first recuperator 730 and the working fluid passing through the second turbine 600. A part of the working fluid recovered in the second recuperator 750 is branched to the first recuperator 730 and the rest is sent to the second heat exchanger 700.

Hereinafter, each configuration of the above-described supercritical carbon dioxide power generation system will be described in detail.

The carbon dioxide separator 100 receives the exhaust gas that is exhausted after burning the fuel, and separates the carbon dioxide from the exhaust gas. The ammonia absorption method, which is a wet separation method, can be used as a separation method of the carbon dioxide separator 100, which is a method using the principle that ammonia absorbs or discharges carbon dioxide according to temperature. The ammonia absorption method has a high price / performance ratio. In addition, various methods such as PSA (Pressure Swing Adsorption), a method of separating by heating, and a method of separating by using a catalyst may be used. After the carbon dioxide is separated in the carbon dioxide separator 100, unnecessary exhaust gas is discharged to the outside of the cycle. Since the carbon dioxide is separated, the greenhouse gas emission amount is not increased.

The working fluid separated in the carbon dioxide separator 100 is compressed to a high pressure in the compressor 200. The working fluid pressurized at the appropriate pressure in the compressor (200) is temporarily stored in the first storage tank (250).

The first storage tank 250 temporarily stores working fluid, and the first storage tank 250 is provided with a safety valve 252 and a flow control valve 254.

The safety valve 252 is provided at one side of the first storage tank 250 to discharge the working fluid stored for safety to the outside of the cycle when the pressure in the first storage tank 250 is higher than a set pressure, (250) is maintained at an appropriate pressure. However, it is preferable that the pressure of the first storage tank 250 is maintained higher than the pressure of the front end of the pump 300 for smooth operation of the pump 300 and flow of the working fluid to the pump side.

The flow control valve 254 is controlled to be opened when an additional supply of working fluid in the cycle is required and the flow rate of the working fluid in the cycle can be adjusted by the flow control valve 254. The flow control valve 254 is opened and the working fluid introduced into the cycle is mixed with the working fluid circulating through the second heat exchanger 700 and supplied to the pump 300 (branch point A).

Most of the working fluid flowing into the pump 300 flows into the second storage tank 350 and a part of the working fluid is branched at the rear end (branch point D) of the second storage tank 350, (A branch flow, which will be described later). Since the pressure of the working fluid on the front end side of the pump 300 is lower than the pressure of the working fluid on the rear end side of the pump 300, a part of the working fluid is branched from the rear end side of the pump 300 and is supplied to the second recirculator 750 The pressure of the working fluid sent to the second turbine 600 through the first recuperator 730 can be maintained at a sufficient level to drive the second turbine 600. [

The second storage tank 350 has the function of separating the oil from the working fluid additionally while passing the high-pressure working fluid discharged from the pump 300. To this end, the second storage tank 350 is provided with an oil separator 254, and the oil separated by the oil separator 354 is supplied to the pump 300 for lubrication of the pump 300. As the oil used for driving the pump 300, oil having a property that the working fluid does not melt well is used. In addition, the second storage tank 350 is provided with a regulator 352.

The regulator 352 is a kind of valve for regulating the pressure in the second storage tank 350 and serves to regulate the pressure of the second storage tank 350 and the oil separator 354 constantly. The pressure gas discharged through the regulator 352 for pressure control in the compressed working fluid may be exhausted out of the cycle or may be stored in an additional reservoir (as described in another embodiment). The working fluid supplied in a compressed state and not discharged through the regulator 352 is supplied to the first heat exchanger 400 and heated and supplied to the first turbine 500 in a high temperature and high pressure state.

The generator 520 is connected to the first turbine 500. When the first turbine 500 is rotationally driven by the high temperature and high pressure working fluid, the generator 520 is driven by the first turbine 500, Production. Since the working fluid is expanded while passing through the first turbine 500, the first turbine 500 also functions as an expander. The expanded working fluid passing through the first turbine 500 recovers the working fluid supplied to the second turbine 600 through the first recuperator 730 and is supplied to the point B.

The generator 620 may be connected to the second turbine 600 and the second turbine 600 is rotationally driven by the working fluid to drive the generator 620 to produce electric power.

In this embodiment, the generator 520 connected to the first turbine 500 and the generator 620 connected to the second turbine 600 are shown as being separate generators. Alternatively, one generator may be connected to the first turbine 500 ) And the second turbine 600, as shown in FIG. In this case, a structure of a transmission, a torque converter, a gear box, or the like capable of compensating the rotational speed and torque difference between the first turbine 500 and the second turbine 600 may be employed.

1 shows the main flow of the working fluid. As described above, the first heat exchanger 400 and the first turbine 500 (see FIG. 1) ) Is defined as the main flow. The flow that the working fluid that has passed through the second storage tank 350 is branched at the branch point D and sent to the second recuperator 750 is defined as a branch flow.

In addition, the first to fourth flows can be classified based on the first recirculator 730 and the second recirculator 750 as the flow direction of the working fluid.

The flow of the working fluid is divided into a first flow flowing into the second turbine 600 after being recuperated by the first recuperator 730 and a second flow flowing from the first recuperator 730 to the fourth flow and after the heat exchange 2 turbine 600 and a second flow that is mixed at point B, as shown in FIG. The third flow is a flow in which the first flow and the second flow are mixed and flowed into the second recuperator 750, then reheated by the second recuperator and introduced into the second heat exchanger 700. In addition, the fourth flow may include a second flow in which the second recuperator 750 exchanges heat with the first flow and the second flow and the recovered branch flow flows into the first recuperator 730.

That is, the working fluid passing through the first recuperator 730 and the working fluid passing through the second turbine 600 are mixed at the branch point B and supplied to the second recuperator 750. The working fluid that is branched from the pump 300 and passes through the second recuperator 750 passes through the branch point B and receives heat from the working fluid passing through the second recuperator 750, And the working fluid passing through the branch point B and the second recuperator 750 in this order is sent to the second heat exchanger 700 and cooled.

The working fluid which has been brought to the low-temperature and low-pressure state through the second heat exchanger 700 can be mixed with the high-pressure working fluid passing through the first storage tank 250 and supplied to the pump 300. Alternatively, a recompressor (not shown) may be provided between the second heat exchanger 700 and the pump 300 to compress the low-temperature and low-pressure working fluid to a high pressure and send it to the pump 300.

As described above, two storage tanks for storing the carbon dioxide working fluid are provided. By controlling the flow rate of the working fluid and the pressure of the storage tank through the valves, the pressure and flow rate of the working fluid can be controlled as desired, Can be improved.

On the other hand, unlike in the above-described embodiment, the effect of responding to environmental problems can be obtained by storing the carbon dioxide discharged from the storage tank in an additional storage.

2 is a block diagram showing a supercritical carbon dioxide power generation system according to another embodiment of the present invention (for the sake of simplicity, the detailed description of the same constitution as the above embodiment will be omitted).

2, the supercritical carbon dioxide power generation system according to another embodiment of the present invention includes a third storage tank 350 for storing a compressed gas (compressed carbon dioxide) discharged through a regulator 352 in a second storage tank 350, A storage tank 370 may be additionally provided.

The third storage tank 370 allows the cycle to be operated in accordance with the GHG emission control standards by preventing the carbon dioxide in the cycle from being discharged directly into the atmosphere. In addition, the high-pressure and low-temperature working fluid discharged before passing through the first heat exchanger 400 is stored and supplied to the front end of the first recuperator 730 so that the first recuperator 730 or the heat- It can be supplied to be used as a cooling source for other parts requiring cooling. To this end, the third storage tank 370 is provided with a control valve capable of supplying a high-pressure and low-temperature working fluid to the branch point C, or a separate control valve 372 is provided between the third storage tank 370 and the branch point C .

The third storage tank 370 may also store high-pressure and low-temperature working fluid discharged through the safety valve 252 of the first storage tank 250. Compressed carbon dioxide can be used for manufacturing foods and beverages such as carbonated water and carbonated beverages, and can be used in industrial fields such as EOR (Enhanced Oil Recovery). Thus, the compressed carbon dioxide can be stored in the third storage tank 370 and used as a cooling source in a cycle, or utilized in other industrial fields in addition to managing greenhouse gas emissions.

In the supercritical carbon dioxide power generation system according to another embodiment of the present invention, the high-temperature low-pressure working fluid passing through the first turbine 500 may be directly delivered to the first recuperator 730, Pressure low-temperature working fluid stored in the storage tank 370 and may be transferred to the first recirculator 730. [ When the temperature of the working fluid passing through the first turbine 500 is excessively high, it is mixed with the high-pressure and low-temperature working fluid stored in the third storage tank 370 so that the high-pressure working fluid flowing into the first recuperator 730 It is possible to prevent the first recuperator 730 from being damaged by the temperature.

That is, there is an effect of controlling the temperature of the cycle with the working fluid stored in the third storage tank 370. The pressure in the storage tank can be controlled by the safety valve 252 and the regulator 352 provided in the first storage tank 250 and the second storage tank 350 and the pressure of the cycle can be controlled accordingly, The temperature and pressure of the cycle can be controlled by the carbon dioxide storage tank.

In the supercritical carbon dioxide power generation system according to another embodiment of the present invention, the flow of the working fluid is branched at the branch point D which is the rear end of the second storage tank 350, and a part of the working fluid is guided to the first heat exchanger 400 , And the rest may be supplied to the second recupilator 750 (branch flow).

Thus, by providing an additional storage tank in addition to the two storage tanks for storing the carbon dioxide working fluid, it is possible to control the flow rate of the working fluid and the pressure of the storage tank, and also to manage the carbon dioxide emissions according to the greenhouse gas emission standards have.

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.

100: carbon dioxide separator 200: compressor
250: first storage tank 300: pump
350: second storage tank 370: third storage tank
400: first heat exchanger 500: first turbine
600: second turbine 700: second heat exchanger
730: first recuperator 750: second recuperator

Claims (26)

A carbon dioxide separator for separating carbon dioxide which is a working fluid from exhaust gas generated by combustion of fuel,
A compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid,
A pump connected to a rear end of the compressor and circulating the working fluid through the compressor;
A first heat exchanger connected to a rear end of the pump and performing heat exchange with the working fluid supplied by the pump,
At least one turbine connected to a downstream end of the first heat exchanger and driven by the working fluid passing through the first heat exchanger,
A second heat exchanger for exchanging heat with the working fluid passing through the turbine,
And a first storage tank for storing the working fluid that has passed through the compressor,
Wherein the turbine includes a first turbine connected to a rear end of the first heat exchanger and a second turbine driven by at least a part of the flow rate of the working fluid passing through the first turbine,
A first recuperator for recuperating the working fluid is provided between the first turbine and the second turbine,
And a second recuperator that recovers the working fluid is provided between the second turbine and the second heat exchanger. The method according to claim 1,
Wherein the first storage tank is located downstream of the compressor and at the same time communicates with the downstream side of the second heat exchanger. 3. The method of claim 2,
Wherein the first heat exchanger supplies heat to the working fluid. 3. The method of claim 2,
And the second heat exchanger cools the working fluid. 3. The method of claim 2,
Wherein the first storage tank is openably and closably provided to discharge the working fluid. 6. The method of claim 5,
The supercritical carbon dioxide generating system of claim 1, wherein the first storage tank is provided to be openable and closable, and further includes a flow control valve for sending the working fluid to a rear end (branch point A) of the second heat exchanger. 6. The method of claim 5,
Wherein the internal pressure of the first storage tank is maintained higher than the pressure of the upstream end of the pump. 3. The method of claim 2,
And a second storage tank provided between the pump and the first heat exchanger for temporarily storing the working fluid. 9. The method of claim 8,
Wherein the second storage tank includes an oil separator that separates oil that lubricates the pump mixed with the working fluid. 10. The method of claim 9,
And the oil separated from the oil separator is sent to the pump. 9. The method of claim 8,
Wherein the second storage tank is provided to be openable and closable and further includes a regulator for exhausting the working fluid. A carbon dioxide separator for separating carbon dioxide which is a working fluid from exhaust gas generated by combustion of fuel,
A compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid,
A pump connected to a rear end of the compressor and circulating the working fluid through the compressor;
A first heat exchanger connected to a rear end of the pump and performing heat exchange with the working fluid supplied by the pump,
At least one turbine connected to a downstream end of the first heat exchanger and driven by the working fluid passing through the first heat exchanger,
A second heat exchanger for exchanging heat with the working fluid passing through the turbine,
A first storage tank for storing the working fluid that has passed through the compressor,
And a second storage tank provided between the pump and the first heat exchanger for temporarily storing the working fluid,
Wherein the second storage tank comprises:
An oil separator for separating oil that lubricates the pump mixed with the working fluid,
And a regulator provided to be openable and closable to exhaust the working fluid,
And a third storage tank for storing a working fluid discharged through the regulator in the second storage tank. 13. The method of claim 12,
The turbine including a first turbine connected to a rear end of the first heat exchanger and a second turbine driven by at least a part of the flow rate of the working fluid passing through the first turbine,
A first recuperator disposed between the first turbine and the second turbine and recuperating the working fluid; a second recuperator disposed between the second turbine and the second heat exchanger, A second recuperator is further provided,
Wherein the third storage tank is provided to be openable and closable and includes a control valve for sending the working fluid to the front end (branch point C) of the first recirculator. The method according to claim 1,
Wherein the flow of the working fluid is a first flow that is recuperated at the first recuperator and thereafter flows into the second turbine, heat exchanges with the fourth flow from the first recuperator, and then flows through the second turbine And the second flow is divided into a second flow mixed with the first flow, and the first flow and the second flow are mixed and then introduced into the second recuperator. 15. The method of claim 14,
Wherein the flow of the working fluid includes a third flow flowing into the second heat exchanger from the second recuperator and a second flow branched from the pump to receive heat from the second recuperator and being sent to the first recuperator And the fourth flow is divided into the fourth flow and the fourth flow. 16. The method of claim 15,
And the working fluid having passed through the pump is branched and communicated to the front end of the second recuperator. A carbon dioxide separator for separating carbon dioxide which is a working fluid from exhaust gas generated by combustion of fuel,
A compressor connected to a downstream end of the carbon dioxide separator for compressing the working fluid,
A pump connected to a rear end of the compressor and circulating the working fluid through the compressor;
A first heat exchanger connected to a rear end of the pump and heating the working fluid supplied by the pump,
A first turbine and a second turbine connected to a rear end of the first heat exchanger and driven by the working fluid passing through the first heat exchanger,
A second heat exchanger for cooling the working fluid passing through the turbine,
A first storage tank for storing the working fluid that has passed through the compressor,
A first recuperator disposed between the first turbine and the second turbine to recover the working fluid;
And a second recuperator disposed between the second turbine and the second heat exchanger and recuperating the working fluid. 18. The method of claim 17,
Wherein the first storage tank is located downstream of the compressor and at the same time communicates with the downstream side of the second heat exchanger. 19. The method of claim 18,
The first storage tank includes a safety valve that is openably and closably provided to exhaust the working fluid, and a flow control valve that is openably and closably provided to transmit the working fluid to the rear end (branch point A) of the second heat exchanger. Critical carbon dioxide power generation system. 20. The method of claim 19,
Wherein the internal pressure of the first storage tank is maintained higher than the pressure of the upstream end of the pump. 21. The method of claim 20,
And a second storage tank provided between the pump and the first heat exchanger for temporarily storing the working fluid. 22. The method of claim 21,
The second storage tank may further include an oil separator for separating oil that lubricates the pump mixed with the working fluid, and a regulator that is openably and closably provided to discharge the working fluid. And the oil is sent to the pump. delete 23. The method of claim 22,
Wherein the flow of the working fluid is a first flow that is recuperated at the first recuperator and thereafter flows into the second turbine, heat exchanges with the fourth flow from the first recuperator, and then flows through the second turbine And the second flow is divided into a second flow mixed with the first flow, and the first flow and the second flow are mixed and then introduced into the second recuperator. 25. The method of claim 24,
Wherein the flow of the working fluid includes a third flow flowing into the second heat exchanger from the second recuperator and a second flow branched from the pump to receive heat from the second recuperator and being sent to the first recuperator And the fourth flow is divided into the fourth flow and the fourth flow. 26. The method of claim 25,
And the working fluid having passed through the pump is branched and communicated to the front end of the second recuperator.
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