KR20180007733A - Supercritical cycle system - Google Patents

Abstract

The present invention relates to a supercritical cycle system. The supercritical cycle system comprises a pump, a first branching unit, a second branching unit, a first merging unit, a first heat exchanger, a power turbine, a drive turbine, a second merging unit, and a cooler. The pump pressurizes a working fluid to circulate the working fluid in an overall working fluid circuit maintained under a critical condition or higher. The first branching unit is fluidically connected to the pump, and allows the working fluid discharged from the pump to branch to a first mass flow and a second mass flow. The second branching unit is fluidically connected to the first branching unit, and receives the second mass flow to allow the second mass flow to branch to a third mass flow and a fourth mass flow. The first merging unit is fluidically connected to the first and the second branching unit, and merges the first mass flow branching from the first branching unit and the third mass flow branching from the second branching unit. The first heat exchanger is fluidically connected to the first merging unit, exchanges heat with a heat source, receives the first mass flow and the third mass flow, and transfers heat energy of the heat source to the first mass flow and the third mass flow. The power turbine is fluidically connected to the first heat exchanger, and expands the first mass flow and the third mass flow passing through the first heat exchanger. The drive turbine is fluidically connected to the second branching unit, and expands the fourth mass flow branching from the second branching unit to drive the pump. The second merging unit is fluidically connected to the power turbine and the drive turbine, and merges the first mass flow and the third mass flow discharged from the power turbine and the fourth mass flow discharged from the drive turbine. The cooler is fluidically connected to the second merging unit, and cools the working fluid discharged from the second merging unit.

Description

Supercritical cycle system < RTI ID = 0.0 >

The present invention relates to a supercritical cycle system, and more particularly, to a supercritical cycle system that drives a turbine by heating a working fluid (e.g., carbon dioxide) compressed at a pressure above a critical condition to a temperature higher than a critical condition.

The power generation technology using supercritical carbon dioxide is a gas-Breton-cycle power generation technology that drives the turbine by using pressurized and heated carbon dioxide under pressure and temperature conditions exceeding critical conditions. In the early 21st century, MIT in the United States theoretically proved that, in the process of developing the next generation nuclear power generation technology, the power generation technology using supercritical carbon dioxide is more efficient than the other nuclear power generation methods, and simple configuration and miniaturization of core devices can be achieved. Over the next decade, empirical research on related technologies is underway in the United States.

The supercritical carbon dioxide power generation cycle can be applied to most of the currently used heat sources (nuclear power, thermal power, solar heat, etc.) and can be applied not only to large power plants, but also to small scale distributed power plants and power plants for offshore plants. Here, supercritical condition refers to a temperature and pressure condition that exceeds a critical point, which is a singular point, in a general material state in which a phase change of the liquid-gas is changed. Most components included in the supercritical carbon dioxide power generation cycle Operating at supercritical conditions of operating temperature and pressure of 32 캜, 74 atm or higher.

Supercritical carbon dioxide has both liquid and gaseous properties at the same time, and it has all the advantages of small condensation days, such as liquids, and small flow resistances, such as gases. The supercritical carbon dioxide exhibits a gas-like viscosity at a high density similar to that of a liquid, which can reduce the size of the turbine, pump, and heat exchanger of the supercritical carbon dioxide cycle. As a result, the construction air and the production unit of the supercritical carbon dioxide power plant And thus it is possible to secure high economical efficiency.

On the other hand, the supercritical carbon dioxide power generation cycle has an advantage of being able to apply not only the conventional water-cooled cooler but also the air-cooled cooler system because it shows improved thermal efficiency due to high energy density even when the entire power generation system is maintained at high temperature and high pressure. In other words, the supercritical carbon dioxide power generation cycle has characteristics such as high thermal efficiency, high power small system configuration, uncomplicated system configuration, and overcoming the site limitation of power plant by making full use of physical property change near the critical point of carbon dioxide.

In terms of recent power generation operations, a new power business model is expected to be derived from power generation capacity of several MW to several hundred MW and diversification of connected heat sources. The supercritical CO2 generation cycle is to improve its efficiency to be utilized in this new power business model Various attempts have been made for this.

In order to increase the performance of the supercritical cycle system, it is necessary to increase the flow rate of the working fluid flowing into the power turbine connected to the external generator. If the total flow circulating in the working fluid circuit is increased, Is required to be higher than the existing one, there is a problem that the whole system is enlarged and the cost is increased.

Korean Registered Patent No. 10-1138223 (Registered on Apr. 13, 2012, entitled: Efficiency Enhancement System of Supercritical Brayton Cycle through Critical Point Movement Using Mixed Gas)

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems occurring in the prior art, and it is an object of the present invention to provide a method for operating a power turbine and a drive turbine by efficiently dividing a flow rate of a working fluid, To thereby provide a supercritical cycle system capable of improving the thermal efficiency of the entire cycle with a predetermined flow rate.

According to an aspect of the present invention, there is provided a supercritical cycle system comprising: a pump for pressurizing a working fluid to circulate a working fluid across a working fluid circuit maintained above a critical condition; A first branch which is fluidly connected with the pump and branches the working fluid discharged from the pump into a first mass flow and a second mass flow; A second branch that is fluidly connected to the first branch and that receives the second mass flow and branches into a third mass flow and a fourth mass flow; A first merging section fluidly connected to the first branch section and the second branch section and having a first mass flow branching at the first branching section and a third mass flow branching at the second branching section; A first mass flow and a third mass flow, the first mass flow and the third mass flow being in fluid connection with the first merging portion and having heat exchange with the heat source, receiving the first mass flow and the third mass flow and transferring the heat energy of the heat source to the first mass flow and the third mass flow, heat transmitter; A power turbine in fluid connection with the first heat exchanger and expanding a first mass flow and a third mass flow via the first heat exchanger; A drive turbine in fluid connection with the second branch and expanding a fourth mass flow diverging from the second branch to drive the pump; A second merging section in fluid connection with the power turbine and the drive turbine, wherein the first mass flow, the third mass flow, and the fourth mass flow emitted from the drive turbine are merged; And a cooler fluidly connected to the second merging portion and cooling the working fluid discharged from the second merging portion.

In the supercritical cycle system according to the present invention, the first branching portion and the first merging portion are fluidly connected to each other and heat-exchanged with the heat source, and heat energy of the heat source flows from the first branching portion to the first merging portion And a second heat exchanger for transferring the heat to the first mass flow.

In a supercritical cycle system according to the present invention, the pump and the first branch are in fluid connection with each other, heat exchange with the heat source is performed, and the thermal energy of the heat source is transferred from the pump to the working fluid flowing into the first branch And a second heat exchanger.

In a supercritical cycle system according to the present invention, heat energy of a first mass flow and a third mass flow, which are fluidly connected with the power turbine and are discharged from the power turbine, flows from the first branch to the second branch And a second regenerator for delivering the first mass flow to the second mass flow.

In the supercritical cycle system according to the present invention, the thermal energy of the working fluid, which is fluidly connected with the second merging portion and the pump, and which is discharged from the second merging portion, To the second player.

In a supercritical cycle system according to the present invention, a second mass flow, which is fluidly connected with the first branch and branches from the first branch to flow to the drive turbine side to raise the inlet temperature of the drive turbine, And a first flow rate valve for controlling the flow rate of the fluid.

In a supercritical cycle system according to the present invention, the second branch is connected in fluid connection with the second branch, and is branched at the second branch such that the output of the drive turbine and the consuming power of the pump become substantially equal, And a second flow rate valve for controlling the flow rate of the fourth mass flow flowing to the second mass flow controller.

In the supercritical cycle system according to the present invention, the working fluid may include carbon dioxide.

According to the supercritical cycle system of the present invention, it is possible to improve the thermal efficiency of the whole cycle with a predetermined flow rate of the working fluid.

Further, according to the supercritical cycle system of the present invention, it is possible to improve the output of the power turbine and increase the inlet temperature of the drive turbine.

Further, according to the supercritical cycle system of the present invention, the overall size of the heat exchanger can be reduced.

Further, according to the supercritical cycle system of the present invention, the inlet temperature of the drive turbine can be further increased through secondary heating of the working fluid flowing into the drive turbine.

1 is a diagram illustrating a supercritical cycle system according to an embodiment of the present invention,
2 is a diagram illustrating a supercritical cycle system in accordance with another embodiment of the present invention.

Hereinafter, embodiments of a supercritical cycle system according to the present invention will be described in detail with reference to the accompanying drawings.

The working fluid m flowing in the supercritical cycle system of the present invention is explained by taking as an example the case where it contains carbon dioxide (CO2).

First, the working fluid m flowing in the supercritical cycle system of the present invention may be carbon dioxide (CO2) and is not limited to any particular type, purity, or grade of carbon dioxide (CO2).

Also, the working fluid m may be a combination of carbon dioxide (CO2) and one or more other miscible fluids. For example, the working fluid can be carbon dioxide (CO2) and propane, or a combination of carbon dioxide (CO2) and ammonia.

1 is a diagram illustrating a supercritical cycle system in accordance with an embodiment of the present invention.

Referring to FIG. 1, the supercritical cycle system 100 according to the present embodiment drives a turbine by heating a working fluid compressed to a pressure higher than a critical condition to a temperature higher than a critical condition. The supercritical cycle system 100 includes a pump 110, A first turbine 161 and a second turbine 162. The first turbine 161 and the second turbine 162 are connected to each other via a first branch 161, a second branch 162, a first branch 171, a first heat exchanger 121, a power turbine 131, A second turbine 132, a second merging portion 172, a cooler 140, a first regenerator 151, a second regenerator 152, a first flow valve 181, And a flow valve 182.

The pump 110 pressurizes the working fluid m to circulate the working fluid m across the working fluid circuit that is maintained above the critical condition.

The working fluid m flowing in the working fluid circuit of the supercritical cycle system 100 of the present embodiment flows in the working fluid circuit while maintaining the condition above the critical condition. In general, the critical temperature and critical pressure of carbon dioxide used as the working fluid (m) are known to be about 32 degrees and 75 atm.

The pump 110 can circulate the working fluid m across the working fluid circuit by pressurizing the low temperature low pressure working fluid m emitted from the cooler 140 to be described later up to the maximum pressure set in the cycle.

The first branch 161 is fluidly connected to the pump 110 and branches the working fluid m discharged from the pump 110 into a first mass flow m1 and a second mass flow m2 . The first mass flow m1 branched at the first branch portion 161 flows toward the power turbine 131 side and the second mass flow m2 branched at the first branch portion 161 flows toward the second branch portion 162).

In the present specification, the flow rate of the sum of the first mass flow m1 and the second mass flow m2 is substantially equal to the flow rate of the working fluid m circulating throughout the working fluid circuit.

The second branch portion 162 is fluidly connected to the first branch portion 161 and receives the second mass flow m2 to branch into the third mass flow m3 and the fourth mass flow m4 . The third mass flow m3 branched at the second branch 162 flows back to the power turbine 131 side and the fourth mass flow m4 branched at the second branch 162 flows to the drive turbine 132 .

In this specification, the flow rate of the sum of the third mass flow m3 and the fourth mass flow m3 is substantially equal to the flow rate of the second mass flow m2.

The first merging portion 171 is fluidly connected to the first branch portion 161 and the second branch portion 162 and the first mass flow m1 and the third mass flow m3 are joined. The first mass flow m1 branched at the first branch 161 and passed through the second heat exchanger 122 and the third mass flow m3 branched at the second branch 162 are connected to the first flow (171), and flows toward the power turbine (131) side.

The first heat exchanger 121 is fluidly connected to the first merging unit 171 and is configured to exchange heat with the heat source 101.

The heat source 101 of the present invention can draw thermal energy Q1 from various high temperature sources. For example, the heat source 101 may be a waste heat stream such as a gas turbine exhaust, a process stream exhaust, a furnace or other combustion production exhaust stream such as a boiler exhaust stream. Thus, the supercritical cycle system 100 can be used in a gas turbine, a diesel engine generator, an industrial waste heat recovery device (e.g., waste heat in an oil refinery and a compression plant), a reactor that causes nuclear reactions such as fission and fusion, . ≪ / RTI > On the other hand, the heat source 101 of the present invention may draw heat energy Q1 from a renewable heat source such as a solar or geothermal source.

The first mass flow m1 and the third mass flow m3 merged in the first merging portion 171 are introduced into the first heat exchanger 121 and the first heat exchanger 121 is connected to the first heat exchanger 121 The heat energy Q1 is transferred to the first mass flow m1 and the third mass flow m3 via the first merging portion 171 and is heated to the maximum temperature set in the cycle.

The second heat exchanger 122 is fluidly connected to the first branch portion 161 and the first merging portion 171 and is configured to exchange heat with the heat source 101.

The first mass flow m1 branched at the first branch 161 flows into the second heat exchanger 122 and the second heat exchanger 122 receives part of the heat energy Q1 of the heat source 101 To the first mass flow m1 flowing from the first branch portion 161 to the first merging portion 171.

A separate fluid for supplying the thermal energy Q1 of the heat source 101 is sequentially passed through the first heat exchanger 121 and the second heat exchanger 122 and then discharged to the outside. In accordance with such a flow of the circulating fluid, a part of the thermal energy Q1 of the heat source 101 is firstly transferred to the first mass flow m1 and the third mass flow m3 in the first heat exchanger 121, The remaining part of the thermal energy Q1 of the heat source 101 is transferred from the second heat exchanger 122 to the first mass flow m1.

Therefore, since the heat energy transmitted from the second heat exchanger 122 is relatively low as compared with the heat energy transmitted from the first heat exchanger 121, the first heat exchanger 121 corresponds to the high temperature heat exchanger, The unit 122 corresponds to the low temperature heat exchanger.

The first mass flow m1 may be preheated by the second heat exchanger 122 before entering the first heat exchanger 121 to reduce the thermal load of the first heat exchanger 121 The size of the heat exchanger as a whole can be reduced.

The first heat exchanger 121 and the second heat exchanger 122 of the present embodiment may be configured in the same manner.

The power turbine 131 is configured to be fluidly connected to the first heat exchanger 121.

The first mass flow m1 and the third mass flow m3 via the first heat exchanger 121 flow into the power turbine 131 and are supplied to the power turbine 131 receives the first mass flow m1 and the third mass flow m3 via the first heat exchanger 121 and expands the first mass flow m1 and the third mass flow m3, And the like.

The power turbine 131 may be operatively connected to a generator or other device or system configured to receive shaft work and the generator may convert the mechanical work generated by the power turbine 131 into useful power .

The drive turbine 132 is configured to be fluidly connected to the second branch 162.

The drive turbine 132 is disposed downstream of the second branch 162 to receive the fourth mass flow m4 diverging from the second branch 162 and to expand the fourth mass flow m4, (110).

By driving the pump 110 using the drive turbine 132 as described above, it is possible to reduce the work required to drive the pump 110, and the net work The amount can be increased.

As described above, in the present embodiment, the first mass flow m1 and the second mass flow m1 at the first branching section 161 before the working fluid m flows into the power turbine 131 and the drive turbine 132, (m2), and the second mass flow m2 is again diverted from the second branch portion 162 to the third mass flow m3 and the fourth mass flow m4. The first mass flow m1 and the third mass flow m3 merge at the first merging portion 171 and then flow into the power turbine 131 and expand. The mass flow m4 flows into the drive turbine 132 and expands.

Meanwhile, the first mass flow m1 and the third mass flow m3, which are expanded and discharged from the power turbine 131, flow into the first regenerator 151, which will be described later.

The first regenerator 151 is configured to be in fluid connection with the power turbine 131.

The first regenerator 151 of the present embodiment can be any device suitable for lowering the temperature of the working fluid such as a direct contact heat exchanger, a trim cooling device, a mechanical cooling device, or a combination thereof. The first regenerator 151 may be provided with one or more printed circuit heat exchange panels, and these heat exchangers or panels are well known in the art, and thus a detailed description thereof will be omitted.

The first regenerator 151 of this embodiment and the second regenerator 152 to be described later may be configured in the same manner.

In the first regenerator 151, the first mass flow m1 and the third mass flow m3 discharged from the power turbine 131 and the second mass flow m3 flowing from the first branch portion 161 to the second branch portion 162 Heat exchange takes place between the second mass flow m2.

That is, in the first regenerator 151, the heat energy of the first mass flow m1 and the third mass flow m3 emitted from the power turbine 131 is transferred from the first branch 161 to the second branch 162 The fourth mass flow m4, which is part of the second mass flow m2, can be heated to the desired inlet temperature in the drive turbine 132. In this way,

The second merging portion 172 is fluidly connected to the power turbine 131 and the drive turbine 132 and is connected in flow communication with the first and second mass flow m1, m3 and m4 Respectively. That is, the entire working fluid m circulating in the working fluid circuit is joined.

The first mass flow m1 and the third mass flow m3 discharged from the power turbine 131 and passed through the first regenerator 151 and the fourth mass flow m4 discharged from the drive turbine 132 Merged at the second merging portion 172, and flow to the cooler 140 side.

The second regenerator 152 is configured to be fluidly connected to the second merging portion 172 and the pump 110.

The second regenerator 152 performs heat exchange between the working fluid m discharged from the second merging portion 172 and the working fluid m flowing from the pump 110 to the first branching portion 161.

That is, in the second regenerator 152, the thermal energy of the working fluid m emitted from the power turbine 131 and the drive turbine 132 and merged with the second merging portion 172 is supplied from the pump 110 to the first M to the working fluid m flowing to the base portion 161 so that the working fluid m passes through the second heat exchanger 122 and the first heat exchanger 121 to a predetermined temperature Can be preheated.

The cooler 140 is configured to be fluidly connected to the second merging portion 172.

Like the first regenerator 151 and the second regenerator 152, the cooler 140 of the present embodiment may be any suitable for lowering the temperature of the working fluid, such as a direct contact heat exchanger, a trim cooling device, a mechanical cooling device, Device. The cooler 140 may be provided with one or more printed circuit heat exchange panels, and these heat exchangers or panels are well known in the art, and therefore, detailed description thereof will be omitted.

The cooler 140 uses the external cooling water or the like to cool the working fluid m emitted from the second regenerator 152 through the second merging portion 172 to a low temperature and the cooled working fluid m And flows into the pump 110 and then is pressurized in the pump 110, thereby forming a circulation cycle as a whole.

The first flow valve 181 is configured to be fluidly connected to the first branch 161.

When the amount of heat energy supplied from the first regenerator 151 is constant, the temperature of the fluid discharged from the first regenerator 151 is determined by the flow rate of the flowing fluid. That is, since the smaller the flow rate of the fluid is, the lower the heat capacity of the first regenerator 151 is, so the temperature of the fluid discharged from the first regenerator 151 is increased.

Since the outlet temperature of the first regenerator 151 and the inlet temperature of the drive turbine 132 are substantially equal to each other, the flow of the second mass flow m2 flowing into the first regenerator 151 The smaller the flow rate, the higher the temperature of the fourth mass flow m4 flowing into the drive turbine 132, that is, the inlet temperature of the drive turbine 132.

As is well known, the output of the turbine is improved as the inlet temperature of the turbine rises. Therefore, the second flow rate valve 181, which branches from the first branch 161 and flows toward the drive turbine 132 side, The inlet temperature of the drive turbine 132 can be increased by adjusting the flow rate of the flow m2 to be not excessive.

In FIG. 1, the first flow valve 181 is shown as being installed in the line through which the second mass flow m2 flows. However, if the first mass flow m1 is to perform the function of regulating the flow rate of the second mass flow m2, it may be installed in a line where the flow rate m1 flows.

The second flow valve 182 is configured to be fluidly connected to the second branch 162.

In order to improve the output of the power turbine 131, it is preferable that the flow rate of the fluid flowing into the power turbine 131 is large. In addition, the flow rate to be inputted to the drive turbine 132 is not required to be an excessive flow rate, but only a flow rate is required to make the output of the drive turbine 132 and the consuming power of the pump 110 substantially equal.

The flow rate of the fourth mass flow m4 flowing into the drive turbine 132 using the second flow valve 182 at the second branching section 162 is controlled by the output of the drive turbine 132 and the output of the pump 110 ) Of the power turbine 131 is controlled so that the consuming power of the power turbine 131 is substantially equal to the flow rate of the power turbine 131 and the remaining flow rate is flowed to the power turbine 131 side as the third mass flow m3, .

Although the second flow valve 182 is shown in FIG. 1 as being installed in the line through which the fourth mass flow m4 flows, if the third mass flow m4 is to perform the function of regulating the flow rate of the fourth mass flow m4, (m < 3 >) flows.

2 is a diagram illustrating a supercritical cycle system in accordance with another embodiment of the present invention.

In Fig. 2, the members denoted by the same reference numerals as those shown in Fig. 1 have the same configuration and function, and a detailed description thereof will be omitted.

Referring to FIG. 2, the supercritical cycle system 200 of the present embodiment differs from the embodiment shown in FIG. 1 in the installation position of the second heat exchanger 222, Are substantially the same as the constituent elements of the embodiment.

The second heat exchanger 222 is fluidly connected to the pump 110 and the first branch 161 and is configured to exchange heat with the heat source 101.

The working fluid m discharged from the pump 110 flows into the second heat exchanger 222 via the second regenerator 152 and the heat energy Q1 of the heat source 101 is introduced into the second heat exchanger 222. [ To the working fluid (m) flowing from the pump (110) to the first branch (161).

1, the fluid introduced into the drive turbine 132 is firstly heated through the second heat exchanger 222 and is secondarily heated through the first regenerator 151, so that the drive turbine 132 can be further increased.

The supercritical cycle system of the present invention constructed as described above efficiently distributes the flow rate of the working fluid required for the power turbine and the drive turbine through a plurality of branches of the working fluid, Can be improved.

In addition, the supercritical cycle system of the present invention constructed as described above can improve the output of the power turbine by adjusting the flow rate to the power turbine and the drive turbine by using the first flow valve and the second flow valve, The effect of increasing the inlet temperature of the turbine can be obtained.

The supercritical cycle system of the present invention constructed as described above is also characterized in that the first mass flow introduced into the power turbine is first preheated through the second heat exchanger and then heated to the turbine inlet temperature through the first heat exchanger, The effect of achieving downsizing of the heat exchanger as a whole can be obtained.

Further, in the supercritical cycle system of the present invention constructed as described above, the working fluid flowing into the drive turbine is heated to a second degree, whereby the inlet temperature of the drive turbine can be further increased.

The scope of the present invention is not limited to the above-described embodiments and modifications, but can be implemented in various forms of embodiments within the scope of the appended claims. It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the present invention as defined by the appended claims.

100: Supercritical cycle system
110: pump
121: first heat exchanger
131: Power turbine
132: drive turbine
140: cooler
161: 1st minute donation
162: 2nd minute donation
171: First merging section
172: second merging portion

Claims (8)

A pump for pressurizing the working fluid to circulate the working fluid across the working fluid circuit maintained above the critical condition;
A first branch which is fluidly connected with the pump and branches the working fluid discharged from the pump into a first mass flow and a second mass flow;
A second branch that is fluidly connected to the first branch and that receives the second mass flow and branches into a third mass flow and a fourth mass flow;
A first merging section fluidly connected to the first branch section and the second branch section and having a first mass flow branching at the first branching section and a third mass flow branching at the second branching section;
A first mass flow and a third mass flow, the first mass flow and the third mass flow being in fluid connection with the first merging portion and having heat exchange with the heat source, receiving the first mass flow and the third mass flow and transferring heat energy of the heat source to the first mass flow and the third mass flow, heat transmitter;
A power turbine in fluid connection with the first heat exchanger and expanding a first mass flow and a third mass flow via the first heat exchanger;
A drive turbine in fluid connection with the second branch and expanding a fourth mass flow diverging from the second branch to drive the pump;
A second merging section in fluid connection with the power turbine and the drive turbine, wherein the first mass flow, the third mass flow, and the fourth mass flow emitted from the drive turbine are merged; And
And a cooler fluidly connected to the second merging portion and cooling the working fluid discharged from the second merging portion. The method according to claim 1,
A second heat exchanger in fluid communication with the first branch and the first junction for heat exchange with the heat source and transferring the thermal energy of the heat source from the first branch to the first mass flow flowing to the first junction, Wherein the supercritical cycle system further comprises: < RTI ID = 0.0 > a < / RTI > The method according to claim 1,
And a second heat exchanger in fluid connection with the pump and the first branch and performing heat exchange with the heat source and transferring the thermal energy of the heat source from the pump to the working fluid flowing into the first branch, Of the supercritical cycle. The method according to claim 1,
A first regenerator coupled in fluid communication with the power turbine and delivering thermal energy of the first mass flow and the third mass flow discharged from the power turbine to a second mass flow flowing from the first branch to the second branch, ≪ / RTI > further comprising: a supercritical cycle system. The method according to claim 1,
And a second regenerator fluidly connected with the second merging section and the pump and transferring thermal energy of the working fluid discharged from the second merging section to the working fluid flowing from the pump to the first branching section ≪ / RTI > The method according to claim 1,
A first flow valve connected in fluid connection with the first branch and regulating a flow rate of a second mass flow branching at the first branch and flowing to the drive turbine to increase the inlet temperature of the drive turbine; Further comprising a supercritical cycle system. The method according to claim 1,
The flow rate of the fourth mass flow branching at the second branch and flowing to the drive turbine is adjusted so that the power of the drive turbine and the power consumption of the pump become substantially equal, Further comprising a second flow valve that is operatively coupled to the first flow rate valve. The method according to claim 1,
Characterized in that the working fluid comprises carbon dioxide.

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