CN113123839A - Supercritical carbon dioxide circulation system - Google Patents
Supercritical carbon dioxide circulation system Download PDFInfo
- Publication number
- CN113123839A CN113123839A CN201911395091.2A CN201911395091A CN113123839A CN 113123839 A CN113123839 A CN 113123839A CN 201911395091 A CN201911395091 A CN 201911395091A CN 113123839 A CN113123839 A CN 113123839A
- Authority
- CN
- China
- Prior art keywords
- inlet
- outlet
- regenerator
- carbon dioxide
- pressure turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Carbon And Carbon Compounds (AREA)
Abstract
The invention relates to the technical field of supercritical carbon dioxide circulation, in particular to a supercritical carbon dioxide circulation system which comprises a heat source, a high-pressure turbine, a low-pressure turbine and a first heat regenerator, the heat recovery system comprises a second heat regenerator, a pre-compressor, a cooler and a main compressor, wherein a first gas outlet of a heat source is connected with a gas inlet of a high-pressure turbine, a gas outlet of the high-pressure turbine is connected with a gas inlet of a low-pressure turbine, a gas outlet of the low-pressure turbine is connected with a hot end inlet of the first heat regenerator, a hot end outlet of the first heat regenerator is connected with a hot end inlet of the second heat regenerator, a hot end outlet of the second heat regenerator is connected with an inlet of the pre-compressor, an outlet of the pre-compressor is connected with an inlet of the cooler, an outlet of the cooler is connected with an inlet of the main compressor, an outlet of the main compressor is connected with a cold end inlet of the second heat regenerator, a cold end outlet of the second. The exhaust pressure of the low-pressure turbine can be reduced, and the circulation efficiency is improved.
Description
Technical Field
The invention relates to the technical field of supercritical carbon dioxide circulation, in particular to a supercritical carbon dioxide circulation system.
Background
Supercritical carbon dioxide (sCO)2) In recent years, cyclic power generation technology has been favored by researchers worldwide due to its wide energy utilization field and high power generation efficiency.
The supercritical carbon dioxide Brayton cycle is based on sCO2As a circulating working medium. CO 22Has the advantages of relatively stable chemical properties, good physical properties, reliable safety, low price, easy acquisition and the like, and CO2The critical temperature and the critical pressure are respectively 31.4 ℃ and 7.38MPa, and are relatively low, so that the supercritical state is easily achieved. When CO is present2In a supercritical state, between liquid and gas, has the special physical characteristics of low gas viscosity and high fluid density, and has the advantages of good fluidity, small specific volume, small compressibility, high heat transfer efficiency and the like, so that the sCO is2Is one of the most widely used supercritical fluids. Based on sCO2Various advantages of, sCO2The Brayton cycle power generation system has the advantages of small occupied space, high power generation efficiency, good economy and the like, so that sCO is actively put into practice in domestic and foreign research institutions, enterprises and the like at present2Brayton cycle as each of the new power cycle systemsAttempts in the field of electrical systems. sCO2The circulation is easy to reach the temperature and pressure of the critical point due to the particularity of the supercritical working medium, and the application field is wide, for example, sCO can be adopted for solar energy, nuclear energy, geothermal energy, gas turbine bottom circulation, fossil energy, waste heat and the like2And (6) circulating.
In the design of the supercritical carbon dioxide circulating system, how to improve the circulating efficiency of the system and optimize the energy utilization rate are the problems which must be considered for realizing the advantages of the supercritical carbon dioxide circulating system.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a supercritical carbon dioxide circulating system, which can optimize the energy utilization rate and improve the circulating efficiency so as to overcome the defects in the prior art.
In order to solve the technical problems, the invention adopts the following technical scheme: a supercritical carbon dioxide circulating system comprises a heat source, a high-pressure turbine, a low-pressure turbine, a first regenerator, a second regenerator, a pre-compressor, a cooler and a main compressor, wherein the heat source is provided with a first air inlet and a first air outlet which are communicated; the first gas outlet of the heat source is connected with the gas inlet of the high-pressure turbine, the gas outlet of the high-pressure turbine is connected with the gas inlet of the low-pressure turbine, the gas outlet of the low-pressure turbine is connected with the hot end inlet of the first regenerator, the hot end outlet of the first regenerator is connected with the hot end inlet of the second regenerator, the hot end outlet of the second regenerator is connected with the inlet of the pre-compressor, the outlet of the pre-compressor is connected with the inlet of the main compressor, the outlet of the main compressor is connected with the cold end inlet of the second regenerator, the cold end outlet of the second regenerator is connected with the cold end inlet of the first regenerator, and the cold end outlet of the first regenerator is connected with the first gas.
Preferably, the hot end outlet of the second heat regenerator is connected with the inlet of the precompressor through a precooler, the hot end outlet of the second heat regenerator is connected with the inlet of the precooler, and the outlet of the precooler is connected with the inlet of the precompressor.
Preferably, the outlet of the precompressor is connected with the inlet of the cooler through a third regenerator, the outlet of the precompressor is connected with the hot end inlet of the third regenerator, the hot end outlet of the third regenerator is connected with the inlet of the cooler, the outlet of the main compressor is also connected with the cold end inlet of the third regenerator, and the cold end outlet of the third regenerator is connected with the cold end inlet of the first regenerator.
Preferably, the outlet of the primary compressor is connected simultaneously to the cold side inlet of the second regenerator and the cold side inlet of the third regenerator via a first flow splitter.
Preferably, the heat recovery device further comprises a recompressor, wherein the outlet of the precompressor is also connected with the inlet of the recompressor, and the outlet of the recompressor is connected with the cold end inlet of the first heat regenerator.
Preferably, the outlet of the precompressor is connected simultaneously to the inlet of the cooler and to the inlet of the recompressor via a second flow divider.
Preferably, the recompressor is connected to the rotor of the high-pressure turbine.
Preferably, the exhaust of the high-pressure turbine is connected to the inlet of the low-pressure turbine via a heat source.
Preferably, the main compressor and the precompressor are both connected to the rotor of the high-pressure turbine.
Compared with the prior art, the invention has the remarkable progress that:
according to the supercritical carbon dioxide circulation system, through the design of the pre-compressor, the carbon dioxide working medium is compressed and boosted before entering the main compressor, so that the design value of the exhaust pressure of the low-pressure turbine can be reduced to be below the critical pressure of the carbon dioxide working medium, and the exhaust of the low-pressure turbine can be compressed by the pre-compressor firstly, and the pressure is increased to be above the critical pressure of the carbon dioxide working medium and then enters the main compressor, so that the carbon dioxide working medium entering the main compressor is ensured to be in a supercritical state, and the guarantee is provided for the safe and stable operation of the main compressor. Therefore, the supercritical carbon dioxide circulation system can effectively reduce the designed exhaust pressure of the low-pressure turbine, thereby increasing the output power of the system, improving the circulation efficiency, improving the work capacity of fluid per unit mass and improving the energy utilization rate.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of a supercritical carbon dioxide cycle system according to an embodiment of the present invention.
Fig. 2 is a schematic structural diagram of another embodiment of a supercritical carbon dioxide cycle system according to an embodiment of the present invention.
FIG. 3 is a temperature entropy diagram of a carbon dioxide working fluid of a supercritical carbon dioxide cycle system according to an embodiment of the present invention.
Wherein the reference numerals are as follows:
1. heat source 1a, first inlet of heat source
1b, a first air outlet 1c of the heat source, and a second air inlet of the heat source
1d, a second outlet 1e of the heat source, a reheat inlet of the heat source
2a, an inlet 2b of the high-pressure turbine, an outlet of the high-pressure turbine
3. Low pressure turbine 3a, inlet of low pressure turbine
3b, exhaust port 4 of low pressure turbine, first regenerator
4a, a hot end inlet 4b of the first heat regenerator, and a hot end outlet of the first heat regenerator
4c, cold end inlet 4d of the first regenerator, cold end outlet of the first regenerator
5. Second regenerator 5a, hot end inlet of second regenerator
5b, hot end outlet 5c of the second regenerator, and cold end inlet of the second regenerator
5d, cold end outlet 6 of second regenerator, and precompressor
6a, inlet 6b of the precompressor, outlet of the precompressor
7. Cooler 7a, cooler inlet
7b, outlet 8 of the cooler, main compressor
8a, inlet 8b of the main compressor, outlet of the main compressor
9. Precooler 9a, inlet of precooler
9b, outlet 10 of precooler, third regenerator
10a, hot side inlet 10b of the third regenerator, and hot side outlet of the third regenerator
10c, cold end inlet 10d of third regenerator, cold end outlet of third regenerator
11. First shunt 12, recompression machine
12a, inlet 12b of the recompressor, outlet of the recompressor
13. Second shunt 14, converging device
15. Driven equipment 16, intermediate turbine
16a, an inlet 16b of the intermediate turbine, an outlet of the intermediate turbine
Detailed Description
The following describes embodiments of the present invention in further detail with reference to the accompanying drawings. These embodiments are merely illustrative of the present invention and are not intended to limit the present invention.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In addition, in the description of the present invention, "a plurality" means two or more unless otherwise specified.
Referring to fig. 1 to 3, an embodiment of a supercritical carbon dioxide cycle system according to the present invention is shown.
Referring to fig. 1, the supercritical carbon dioxide cycle system of the present embodiment includes a heat source 1, a high-pressure turbine 2, a low-pressure turbine 3, a first recuperator 4, a second recuperator 5, a precompressor 6, a cooler 7, and a main compressor 8.
The heat source 1 is provided with a first air inlet 1a and a first air outlet 1b, the first air inlet 1a and the first air outlet 1b of the heat source 1 are communicated to form a first circulating working medium heating channel, carbon dioxide gas serving as a circulating working medium can enter the first circulating working medium heating channel from the first air inlet 1a of the heat source 1 and exchanges heat with the heat source 1 in the process of flowing through the first circulating working medium heating channel, and the carbon dioxide gas absorbs heat of the heat source 1 to form high-temperature gas and then flows out from the first air outlet 1b of the heat source 1.
The high-pressure turbine 2 is provided with an air inlet 2a and an air outlet 2b, carbon dioxide working medium can enter the high-pressure turbine 2 from the air inlet 2a of the high-pressure turbine 2 to do work, heat energy is converted into mechanical energy, and the gas after doing work is discharged from the air outlet 2b of the high-pressure turbine 2.
The low pressure turbine 3 is provided with an air inlet 3a and an air outlet 3b, the carbon dioxide working medium can enter the low pressure turbine 3 from the air inlet 3a of the low pressure turbine 3 to do work, the heat energy is converted into mechanical energy, and the gas after doing work is discharged from the air outlet 3b of the low pressure turbine 3.
The first recuperator 4 has a hot side inlet 4a, a hot side outlet 4b, a cold side inlet 4c and a cold side outlet 4 d. The hot end inlet 4a and the hot end outlet 4b of the first heat regenerator 4 are communicated to form a first hot end channel, and the carbon dioxide working medium with relatively high temperature can enter the first hot end channel from the hot end inlet 4a of the first heat regenerator 4 and flow out from the hot end outlet 4b of the first heat regenerator 4. The cold end inlet 4c and the cold end outlet 4d of the first heat regenerator 4 are communicated to form a first cold end channel, and the carbon dioxide working medium with relatively low temperature can enter the first cold end channel from the cold end inlet 4c of the first heat regenerator 4 and flow out from the cold end outlet 4d of the first heat regenerator 4. And the high-temperature carbon dioxide working medium and the low-temperature carbon dioxide working medium exchange heat when flowing through the first hot end channel and the first cold end channel of the first heat regenerator 4 respectively to release and absorb heat respectively.
The precompressor 6 has an inlet 6a and an outlet 6b, and carbon dioxide working fluid can enter the precompressor 6 from the inlet 6a of the precompressor 6 and flow out from the outlet 6b of the precompressor 6 after being compressed and boosted in the precompressor 6.
The cooler 7 is provided with an inlet 7a and an outlet 7b, and the carbon dioxide working medium can enter the cooler 7 from the inlet 7a of the cooler 7 and flows out from the outlet 7b of the cooler 7 after being cooled and cooled in the cooler 7.
The main compressor 8 is provided with an inlet 8a and an outlet 8b, and carbon dioxide working medium can enter the main compressor 8 from the inlet 8a of the main compressor 8 and flows out from the outlet 8b of the main compressor 8 after being compressed and boosted in the main compressor 8.
In this embodiment, the first air outlet 1a of the heat source 1 is connected to the air inlet 2a of the high-pressure turbine 2, the air outlet 2b of the high-pressure turbine 2 is connected to the air inlet 3a of the low-pressure turbine 3, the air outlet 3b of the low-pressure turbine 3 is connected to the hot-end inlet 4a of the first regenerator 4, the hot-end outlet 4b of the first regenerator 4 is connected to the hot-end inlet 5a of the second regenerator 5, the hot-end outlet 5b of the second regenerator 5 is connected to the inlet 6a of the pre-compressor 6, the outlet 6b of the pre-compressor 6 is connected to the inlet 7a of the cooler 7, the outlet 7b of the cooler 7 is connected to the inlet 8a of the primary compressor 8, the outlet 8b of the primary compressor 8 is connected to the cold-end inlet 5c of the second regenerator 5, the cold-end outlet 5d of the second regenerator 5 is connected to the cold-end inlet 4c of the first regenerator 4. Thereby forming a carbon dioxide working medium circulation loop, and the circulation process is as follows.
The carbon dioxide working medium after the heat source 1 absorbs heat has high temperature and pressure, flows out from the first air outlet 1b of the heat source 1, enters the high-pressure turbine 2 from the air inlet 1a of the high-pressure turbine 2 to do work, drives the rotor of the high-pressure turbine 2 to rotate, and enables the rotor of the high-pressure turbine 2 to output power. The carbon dioxide working medium which does work in the high-pressure turbine 2 is discharged from an exhaust port 2b of the high-pressure turbine 2, then enters the low-pressure turbine 3 from an air inlet 3a of the low-pressure turbine 3 to do work, and drives a rotor of the low-pressure turbine 2 to rotate, so that the rotor of the low-pressure turbine 3 outputs power. The carbon dioxide working medium which has performed work in the low-pressure turbine 3 is discharged from an exhaust port 3b of the low-pressure turbine 3, and sequentially flows through a first hot end channel of the first regenerator 4 (a hot end inlet 4a to a hot end outlet 4b of the first regenerator 4) and a second hot end channel of the second regenerator 5 (a hot end inlet 5a to a hot end outlet 5b of the second regenerator 5). Carbon dioxide working medium flowing out of hot end outlet 5b of second regenerator 5 enters precompressor 6 from inlet 6a of precompressor 6, and flows out of outlet 6b of precompressor 6 after being compressed and boosted in precompressor 6. The carbon dioxide working medium flowing out of the outlet 6b of the pre-compressor 6 enters the inlet 7a of the cooler 7, is cooled in the cooler 7 and then flows out of the outlet 7b of the cooler 7, then enters the main compressor 8 from the inlet 8a of the main compressor 8, is compressed and boosted in the main compressor 8 and then flows out of the outlet 8b of the main compressor 8, then flows through the second cold end channel (the cold end inlet 5c to the cold end outlet 5d of the second regenerator 5) of the second regenerator 5 and absorbs the heat of the carbon dioxide working medium flowing through the second hot end channel of the second regenerator 5, and then flows through the first cold end channel (the cold end inlet 4c to the cold end outlet 4d of the first regenerator 4) of the first regenerator 4 and absorbs the heat of the carbon dioxide working medium flowing through the first hot end channel of the first regenerator 4. The carbon dioxide working medium flowing out of the cold end outlet 4d of the first heat regenerator 4 enters the heat source 1 from the first air inlet 1a of the heat source 1 to absorb heat, and then a new cycle is started.
The supercritical carbon dioxide circulation system of the embodiment compresses and boosts the carbon dioxide working medium before entering the main compressor 8 through the design of the pre-compressor 6, so that the design value of the exhaust pressure of the low-pressure turbine 3 can be reduced to be lower than the critical pressure of the carbon dioxide working medium, because the exhaust of the low-pressure turbine 3 can be compressed by the pre-compressor 6, the pressure is increased to be higher than the critical pressure of the carbon dioxide working medium and then enters the main compressor 8, the carbon dioxide working medium entering the main compressor 8 is ensured to be in a supercritical state, and the safe and stable operation of the main compressor 8 is guaranteed. Therefore, the supercritical carbon dioxide circulation system of the embodiment can effectively reduce the designed exhaust pressure of the low-pressure turbine 3, thereby increasing the output power of the system, improving the circulation efficiency, improving the work capacity of fluid per unit mass and improving the energy utilization rate.
In this embodiment, it is preferable that the hot end outlet 5b of second regenerator 5 and the inlet 6a of pre-compressor 6 be connected by precooler 9. Precooler 9 has an inlet 9a and an outlet 9b, and carbon dioxide working medium can enter precooler 9 from inlet 9a of precooler 9 and flows out from outlet 9b of precooler 9 after being cooled and cooled in precooler 9. The hot end outlet 5b of the second regenerator 5 is connected to the inlet 9a of the precooler 9, and the outlet 9b of the precooler 9 is connected to the inlet 6a of the precompressor 6. Therefore, in the carbon dioxide working medium circulation circuit, the carbon dioxide working medium flowing out of the hot end outlet 5b of the second heat regenerator 5 firstly enters the inlet 9a of the precooler 9, is cooled in the precooler 9 and then flows out of the outlet 9b of the precooler 9, and then enters the inlet 6a of the precompressor 6. The carbon dioxide working medium before entering the precompressor 6 is cooled by the precooler 9, the specific volume of the carbon dioxide working medium can be reduced, the power consumption of the precompressor 6 is reduced, the cycle efficiency is improved, meanwhile, the pressure of the carbon dioxide working medium flowing out of the hot end outlet 5b of the second reheater 5 is lower than the critical pressure of the carbon dioxide working medium, and the carbon dioxide working medium can be kept in a gas state area after being cooled by the precooler 9, so that the phenomenon that the physical property of the carbon dioxide working medium in the precompressor 6 is in a liquid state is avoided when the carbon dioxide working medium enters the precompressor 6 and is compressed and boosted to a supercritical state.
In this embodiment, the outlet 6b of the precompressor 6 and the inlet 7a of the cooler 7 may be connected by a third regenerator 10. Third regenerator 10 has a hot side inlet 10a, a hot side outlet 10b, a cold side inlet 10c, and a cold side outlet 10 d. The hot end inlet 10a and the hot end outlet 10b of the third regenerator 10 are communicated to form a third hot end channel, and the carbon dioxide working medium with relatively high temperature can enter the third hot end channel from the hot end inlet 10a of the third regenerator 10 and flow out from the hot end outlet 10b of the third regenerator 10. The cold end inlet 10c and the cold end outlet 10d of the third regenerator 10 are communicated to form a third cold end channel, and the carbon dioxide working medium with relatively low temperature can enter the third cold end channel from the cold end inlet 10c of the third regenerator 10 and flow out from the cold end outlet 10d of the third regenerator 10. The high and low temperature carbon dioxide working media exchange heat when flowing through the third hot end channel and the third cold end channel of the third heat regenerator 10, respectively, to release and absorb heat. The outlet 6b of the precompressor 6 is connected with the hot end inlet 10a of the third regenerator 10, the hot end outlet 10b of the third regenerator 10 is connected with the inlet 7a of the cooler 7, the outlet 8b of the main compressor 8 is also connected with the cold end inlet 10c of the third regenerator 10, and the cold end outlet 10d of the third regenerator 10 is connected with the cold end inlet 4c of the first regenerator 4. Thus, in the carbon dioxide working medium circulation loop, the carbon dioxide working medium flowing out of the outlet 6b of the precompressor 6 flows through the third hot end channel of the third regenerator 10 (from the hot end inlet 10a to the hot end outlet 10b of the third regenerator 10), then enters the inlet 7a of the cooler 7, is cooled by the cooler 7, is compressed and boosted by the main compressor 8 in sequence, and then flows out of the outlet 8b of the main compressor 8 to be divided into two streams, one stream flows through the second cold end channel of the second regenerator 5 and absorbs the heat of the carbon dioxide working medium flowing through the second hot end channel of the second regenerator 5, the other stream flows through the third cold end channel of the third regenerator 10 (from the cold end inlet 10c to the cold end outlet 10d of the third regenerator 10) and absorbs the heat of the carbon dioxide working medium flowing through the third hot end channel of the third regenerator 10, and flows out of the cold end outlet 5d of the second regenerator 5 and flows out of the cold end channel of the third regenerator 10 And the carbon dioxide working medium flowing out of the end outlet 10d enters a cold end inlet 4c of the first heat regenerator 4. The temperature of the carbon dioxide working medium compressed and boosted by the pre-compressor 6 can be increased, and partial heat energy of the carbon dioxide working medium compressed and boosted by the pre-compressor 6 can be recycled through the design of the third heat regenerator 10, so that the utilization rate of energy is increased.
In this embodiment, preferably, the outlet 8b of the primary compressor 8 may be connected to the cold side inlet 5c of the second regenerator 5 and the cold side inlet 10c of the third regenerator 10 simultaneously by the first flow divider 11. The carbon dioxide working medium flowing out of the outlet 8b of the main compressor 8 is split into two flows by the first splitter 11, and the two flows of carbon dioxide working medium enter the cold-end inlet 5c of the second regenerator 5 and the cold-end inlet 10c of the third regenerator 10 respectively. The first flow divider 11 may employ a three-way valve.
Preferably, the supercritical carbon dioxide cycle system of the embodiment may further include a recompressor 12, the recompressor 12 has an inlet 12a and an outlet 12b, and the carbon dioxide working medium may enter the recompressor 12 from the inlet 12a of the recompressor 12 and flow out from the outlet 12b of the recompressor 12 after being compressed and boosted in the recompressor 12. The outlet 6b of the precompressor 6 is also connected to the inlet 12a of the recompressor 12, and the outlet 12b of the recompressor 12 is connected to the cold-end inlet 4c of the first recuperator 4. In this embodiment, the outlet 6b of the pre-compressor 6 and the inlet 12a of the recompressor 12 are also connected by the third regenerator 10, that is, the outlet 6b of the pre-compressor 6 is connected to the hot end inlet 10a of the third regenerator 10, and the hot end outlet 10b of the third regenerator 10 is simultaneously connected to the inlet 7a of the cooler 7 and the inlet 12a of the recompressor 12. Therefore, in the carbon dioxide working medium circulation loop, the carbon dioxide working medium flowing out of the outlet 6b of the precompressor 6 flows through the third hot end channel of the third heat regenerator 10 for heat exchange, the carbon dioxide working medium flowing out of the hot end outlet 10b of the third heat regenerator 10 is divided into two parts, one part of the carbon dioxide working medium enters the inlet 7a of the cooler 7, the other part of the carbon dioxide working medium enters the inlet 12a of the recompressor 12, the carbon dioxide working medium flows out of the outlet 12b of the recompressor 12 after being compressed and boosted in the recompressor 12, and the carbon dioxide working medium flowing out of the outlet 12b of the recompressor 12 enters the cold end inlet 4c of the first heat regenerator. Through the design of the secondary compressor 12, the exhaust of the low-pressure turbine 3 is divided into two parts after flowing out from the hot end outlet 10b of the third heat regenerator 10, wherein one part is cooled and cooled by the cooler 7 and compressed and boosted by the main compressor 8, and the other part is directly compressed and boosted by the secondary compressor 12 without being cooled and consumed by the cooler 7, so that the circulation efficiency can be effectively improved, the recovery of the exhaust waste heat of the low-pressure turbine 3 is more thorough, and the high-efficiency utilization of energy is realized. Meanwhile, partial heat energy of the carbon dioxide working medium compressed and boosted by the pre-compressor 6 is recycled through the third heat regenerator 10, the specific volume of the carbon dioxide working medium entering the re-compressor 12 is reduced, the power consumption of the re-compressor 12 can be effectively reduced, and the circulation efficiency is improved.
Preferably, the outlet 6b of the precompressor 6 may be connected simultaneously to the inlet 7a of the cooler 7 and to the inlet 12a of the recompressor 12 by means of a second flow divider 13. In this embodiment, outlet 6b of precompressor 6 is connected to hot side inlet 10a of third regenerator 10, and hot side outlet 10b of third regenerator 10 is connected to both inlet 7a of cooler 7 and inlet 12a of recompressor 12 via second flow divider 13. The carbon dioxide working fluid flowing out of the hot end outlet 10b of the third regenerator 10 is split into two streams by the second splitter 13, and the two streams of carbon dioxide working fluid are introduced into the inlet 7a of the cooler 7 and the inlet 12a of the recompressor 12, respectively. The second flow splitter 13 may be a three-way valve.
In this embodiment, the cold end outlet 5d of the second regenerator 5, the cold end outlet 10d of the third regenerator 10, and the outlet 12b of the recompressor 12 are all connected to the cold end inlet 4c of the first regenerator 4, so that the carbon dioxide working medium flowing out of the cold end outlet 5d of the second regenerator 5, the carbon dioxide working medium flowing out of the cold end outlet 10d of the third regenerator 10, and the carbon dioxide working medium flowing out of the outlet 12b of the recompressor 12 all enter the cold end inlet 4c of the first regenerator 4. Preferably, the cold end outlet 5d of the second regenerator 5, the cold end outlet 10d of the third regenerator 10, and the outlet 12b of the recompressor 12 may all be connected to the cold end inlet 4c of the first regenerator 4 through a flow combiner 14, the flow combiner 14 combines the carbon dioxide working medium flowing out from the cold end outlet 5d of the second regenerator 5, the carbon dioxide working medium flowing out from the cold end outlet 10d of the third regenerator 10, and the carbon dioxide working medium flowing out from the outlet 12b of the recompressor 12 into one flow, and the combined flow of carbon dioxide working medium enters the cold end inlet 4c of the first regenerator 4, and the flow combiner 14 may adopt a four-way valve.
In this embodiment, preferably, the exhaust port 2b of the high-pressure turbine 2 is connected to the intake port 3a of the low-pressure turbine 3 through the heat source 1, so that in the carbon dioxide working medium circulation loop, after the carbon dioxide working medium doing work in the high-pressure turbine 2 is exhausted from the exhaust port 2b of the high-pressure turbine 2, the carbon dioxide working medium passes through the heat source 1 and absorbs heat of the heat source 1 to be reheated, and then enters the low-pressure turbine 3 from the intake port 3a of the low-pressure turbine 3 to do work. The design that the heat source 1 reheats the exhaust gas at the exhaust port 2b of the high-pressure turbine 2 improves the inlet temperature of the low-pressure turbine 3, and can effectively increase the specific power of the system and improve the output power of the system. In this embodiment, the exhaust gas at the exhaust port 2b of the high pressure turbine 2 may be subjected to single reheating or multiple reheating by the heat source 1 and then enters the low pressure turbine 3 from the inlet 3a of the low pressure turbine 3 to perform work.
Referring to fig. 1, in one embodiment, the exhaust gas at the exhaust port 2b of the high pressure turbine 2 may be subjected to a single reheating by the heat source 1 and then enters the low pressure turbine 3 from the inlet port 3a of the low pressure turbine 3 to perform work. Specifically, the heat source 1 is provided with a second air inlet 1c and a second air outlet 1d, the second air inlet 1c and the second air outlet 1d of the heat source 1 are communicated to form a second circulating working medium heating channel, carbon dioxide gas serving as a circulating working medium can enter the second circulating working medium heating channel from the second air inlet 1c of the heat source 1 and exchanges heat with the heat source 1 in the process of flowing through the second circulating working medium heating channel, and flows out from the second air outlet 1d of the heat source 1 after absorbing heat of the heat source 1. The exhaust port 2b of the high-pressure turbine 2 is connected to the second inlet port 1c of the heat source 1, and the second outlet port 1d of the heat source 1 is connected to the inlet port 3a of the low-pressure turbine 3. Therefore, in the carbon dioxide working medium circulation loop, the carbon dioxide working medium which does work in the high-pressure turbine 2 is discharged from the exhaust port 2b of the high-pressure turbine 2, enters the second air inlet 1c of the heat source 1, absorbs the heat of the heat source 1, is reheated, then flows out of the second air outlet 1d of the heat source 1, and then enters the low-pressure turbine 3 from the air inlet 3a of the low-pressure turbine 3 to do work.
Referring to fig. 2, in another embodiment, the exhaust gas at the exhaust port 2b of the high pressure turbine 2 may be reheated several times by the heat source 1 and then enter the low pressure turbine 3 from the inlet port 3a of the low pressure turbine 3 to perform work. Specifically, the heat source 1 is provided with a second air inlet 1c and a second air outlet 1d, the second air inlet 1c and the second air outlet 1d of the heat source 1 are communicated to form a second circulating working medium heating channel, carbon dioxide gas serving as a circulating working medium can enter the second circulating working medium heating channel from the second air inlet 1c of the heat source 1 and exchanges heat with the heat source 1 in the process of flowing through the second circulating working medium heating channel, and flows out from the second air outlet 1d of the heat source 1 after absorbing heat of the heat source 1. In addition, at least one intermediate turbine 16 is arranged between the heat source 1 and the air inlet 3a of the low-pressure turbine 3, the intermediate turbines 16 are sequentially arranged, each intermediate turbine 16 is provided with an air inlet 16a and an air outlet 16b, carbon dioxide working medium can enter the intermediate turbine 16 from the air inlet 16a of the intermediate turbine 16 to do work, heat energy is converted into mechanical energy, and the gas after doing work is discharged from the air outlet 16b of the intermediate turbine 16; the heat source 1 is also provided with at least one group of reheating air inlets 1e and reheating air outlets 1f, each group of reheating air inlets 1e and reheating air outlets 1f are communicated to form a cycle working medium reheating channel, so that the heat source 1 is provided with at least one cycle working medium reheating channel, carbon dioxide gas serving as cycle working medium can enter the corresponding cycle working medium reheating channel from the reheating air inlets 1e of the heat source 1, and can exchange heat with the heat source 1 in the process of flowing through the cycle working medium reheating channel, and flows out of the corresponding reheating air outlets 1f after absorbing the heat of the heat source 1. The number of the reheating channels of the circulating medium is matched with the number of the intermediate turbines 16. An exhaust port 2b of the high-pressure turbine 2 is connected with a second inlet port 1c of the heat source 1, a second outlet port 1d of the heat source 1 is connected with an inlet port 16a of a first intermediate turbine 16, an exhaust port 16b of the first intermediate turbine 16 is connected with a reheating inlet port 1e of a first cycle working medium reheating channel of the heat source 1, a reheating outlet port 1f of the first cycle working medium reheating channel of the heat source 1 is connected with an inlet port 16a of a second intermediate turbine 16, an exhaust port 16b of the second intermediate turbine 16 is connected with a reheating inlet port 1e of a second cycle working medium reheating channel of the heat source 1, a reheating outlet port 1f of the second cycle working medium reheating channel of the heat source 1 is connected with an inlet port 16a of, in this way, the intermediate turbines 16 are connected with the cycle medium reheating channels of the heat source 1 in sequence in a one-to-one correspondence manner, and the exhaust port 16b of the last intermediate turbine 16 is connected with the air inlet 3a of the low-pressure turbine 3. In the carbon dioxide working medium circulation loop, after the carbon dioxide working medium doing work in the high-pressure turbine 2 is discharged from the exhaust port 2b of the high-pressure turbine 2, the carbon dioxide working medium firstly enters the second air inlet 1c of the heat source 1, absorbs the heat of the heat source 1, flows out from the second air outlet 1d of the heat source 1 after being reheated, then sequentially enters each intermediate turbine 16 to do work, in addition, the carbon dioxide working medium doing work in each intermediate turbine 16 flows through one circulation working medium reheating channel of the heat source 1, absorbs the heat of the heat source 1, then enters the next intermediate turbine 16 after being reheated, and the carbon dioxide working medium doing work in the last intermediate turbine 16 flows through the corresponding circulation working medium reheating channel in the heat source 1, absorbs the heat of the heat source 1, is reheated, and then enters the low-pressure turbine 3 from the air inlet 3a of the. The second working fluid heating channel and the working fluid reheating channel of the heat source 1 thus form a multi-stage reheating of the exhaust gas at the exhaust port 2b of the high-pressure turbine 2.
In this embodiment, the recompressor 12, the main compressor 8 and the precompressor 6 may be connected to the rotor of the high-pressure turbine 2. The recompressor 12, the main compressor 8 and the precompressor 6 are operated as driven by the high-pressure turbine 2. The rotor of low-pressure turbine 3 may then be connected to driven device 15, and driven device 15 may be a generator, so that the power output by the rotor of low-pressure turbine 3 may be converted into electrical energy.
In summary, referring to fig. 1 to 3, when the supercritical carbon dioxide cycle system of the present embodiment works, the cycle flow of the carbon dioxide working medium is as follows.
The carbon dioxide working medium flowing through the first circulating working medium heating channel (the first air inlet 1a to the first air outlet 1b of the heat source 1) of the heat source 1 has very high temperature and pressure after absorbing heat, the carbon dioxide working medium flows out of the first air outlet 1b of the heat source 1 and then enters the high-pressure turbine 2 to do work to drive the rotor of the high-pressure turbine 2 to rotate, and the rotor of the high-pressure turbine 2 drives the re-compressor 12, the main compressor 8 and the pre-compressor 6 to operate. The carbon dioxide working medium which is expanded to a certain pressure by acting in the high-pressure turbine 2 is discharged from an exhaust port 2b of the high-pressure turbine 2 and flows through a second circulating working medium heating channel (from a second air inlet 1c to a second air outlet 1d of the heat source 1) of the heat source 1 to absorb heat, the reheated and heated carbon dioxide working medium flows out of the second air outlet 1d of the heat source 1 and then enters the low-pressure turbine 3 to act to drive a rotor of the low-pressure turbine 3 to rotate, and the rotor of the low-pressure turbine 3 drives the driven device 15 to operate. Or the carbon dioxide working medium which is expanded to a certain pressure by acting in the high-pressure turbine 2 is discharged from the exhaust port 2b of the high-pressure turbine 2, and flows through a second circulating working medium heating channel (a second air inlet 1c to a second air outlet 1d of the heat source 1) of the heat source 1 to absorb heat, the reheated and heated carbon dioxide working medium flows out of the second air outlet 1d of the heat source 1 and then sequentially enters each intermediate turbine 16 to do work, the working carbon dioxide working medium in each intermediate turbine 16 absorbs heat after flowing through a cycle working medium reheating channel of the heat source 1, and enters the next intermediate turbine 16 after reheating and temperature rising, the carbon dioxide working medium acting in the last intermediate turbine 16 flows through the corresponding circulating working medium reheating channel in the heat source 1 to absorb heat and then enters the low-pressure turbine 3 to act, the rotor of the low-pressure turbine 3 is driven to rotate, and the rotor of the low-pressure turbine 3 drives the driven equipment 15 to operate. The pressure of the carbon dioxide working medium after the work is applied in the low-pressure turbine 3 can be sufficiently expanded to be lower than the critical pressure thereof (the design value of the exhaust pressure of the low-pressure turbine 3 is lower than the critical pressure of the carbon dioxide working medium). The carbon dioxide working medium discharged from the exhaust port 3b of the low-pressure turbine 3 sequentially flows through the first hot end channel of the first heat regenerator 4 and the second hot end channel of the second heat regenerator 5, then enters the precooler 9 for cooling, and the temperature of the carbon dioxide working medium passing through the precooler 9 is reduced to be close to the critical temperature (higher than the critical point temperature). The carbon dioxide working medium flowing out of the outlet 9b of the precooler 9 enters the precompressor 6 to be compressed and boosted, and the pressure of the carbon dioxide working medium passing through the precompressor 6 is boosted to be higher than the critical pressure. Carbon dioxide working medium flowing out of outlet 6b of pre-compressor 6 flows through the third hot end channel of third regenerator 10, and then is split into two flows by second flow splitter 13. The first flow of carbon dioxide working medium divided by the second flow divider 13 is sequentially cooled by the cooler 7, compressed and boosted by the main compressor 8, and then divided into two flows by the first flow divider 11, the two flows of carbon dioxide working medium divided by the first flow divider 11 respectively flow through the second cold end channel of the second heat regenerator 5 to absorb the heat of the carbon dioxide working medium flowing through the second hot end channel of the second heat regenerator 5, the third cold end channel of the third heat regenerator 10 to absorb the heat of the carbon dioxide working medium flowing through the third hot end channel of the third heat regenerator 10, and then the two flows are converged at the junction station 14; the second flow of carbon dioxide working medium split by the second splitter 13 enters the re-compressor 12 to be compressed and boosted, and then is merged with the first flow of carbon dioxide working medium split by the second splitter 13 into one flow at the confluence device 14. The carbon dioxide working medium merged into one stream at the junction station 14 flows through the first cold end channel of the first heat regenerator 4 and absorbs the heat of the carbon dioxide working medium flowing through the first hot end channel of the first heat regenerator 4. The carbon dioxide working medium flowing out of the cold end outlet 4d of the first heat regenerator 4 enters the heat source 1 from the first air inlet 1a of the heat source 1 to absorb heat, and then a new cycle is started.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.
Claims (9)
1. A supercritical carbon dioxide circulation system is characterized by comprising a heat source (1), a high-pressure turbine (2), a low-pressure turbine (3), a first regenerator (4), a second regenerator (5), a precompressor (6), a cooler (7) and a main compressor (8), wherein the heat source (1) is provided with a first air inlet (1a) and a first air outlet (1b) which are communicated; a first air outlet (1b) of the heat source (1) is connected with an air inlet (2a) of the high-pressure turbine (2), an air outlet (2b) of the high-pressure turbine (2) is connected with an air inlet (3a) of the low-pressure turbine (3), an air outlet (3b) of the low-pressure turbine (3) is connected with a hot end inlet (4a) of the first heat regenerator (4), a hot end outlet (4b) of the first heat regenerator (4) is connected with a hot end inlet (5a) of the second heat regenerator (5), a hot end outlet (5b) of the second heat regenerator (5) is connected with an inlet (6a) of the pre-compressor (6), an outlet (6b) of the pre-compressor (6) is connected with an inlet (7a) of the cooler (7), and an outlet (7b) of the cooler (7) is connected with an inlet (8a) of the main compressor (8), an outlet (8b) of the primary compressor (8) is connected with a cold end inlet (5c) of the second heat regenerator (5), a cold end outlet (5d) of the second heat regenerator (5) is connected with a cold end inlet (4c) of the first heat regenerator (4), and a cold end outlet (4d) of the first heat regenerator (4) is connected with a first air inlet (1a) of the heat source (1).
2. Supercritical carbon dioxide cycle system according to claim 1, characterized in that the hot end outlet (5b) of the second regenerator (5) is connected to the inlet (6a) of the precompressor (6) by means of a precooler (9), the hot end outlet (5b) of the second regenerator (5) is connected to the inlet (9a) of the precooler (9), and the outlet (9b) of the precooler (9) is connected to the inlet (6a) of the precompressor (6).
3. Supercritical carbon dioxide cycle system according to claim 1, characterized in that the outlet (6b) of the precompressor (6) is connected to the inlet (7a) of the cooler (7) by a third regenerator (10), the outlet (6b) of the precompressor (6) is connected to the hot side inlet (10a) of the third regenerator (10), the hot side outlet (10b) of the third regenerator (10) is connected to the inlet (7a) of the cooler (7), the outlet (8b) of the main compressor (8) is further connected to the cold side inlet (10c) of the third regenerator (10), and the cold side outlet (10d) of the third regenerator (10) is connected to the cold side inlet (4c) of the first regenerator (4).
4. Supercritical carbon dioxide cycle system according to claim 3, characterized in that the outlet (8b) of the primary compressor (8) connects the cold end inlet (5c) of the second regenerator (5) and the cold end inlet (10c) of the third regenerator (10) simultaneously through a first flow splitter (11).
5. Supercritical carbon dioxide circulation system according to claim 1, characterized by further comprising a re-compressor (12), the outlet (6b) of the pre-compressor (6) being further connected to the inlet (12a) of the re-compressor (12), the outlet (12b) of the re-compressor (12) being connected to the cold end inlet (4c) of the first recuperator (4).
6. Supercritical carbon dioxide circulation system according to claim 5, characterized in that the outlet (6b) of the pre-compressor (6) is connected simultaneously to the inlet (7a) of the cooler (7) and to the inlet (12a) of the re-compressor (12) by a second flow divider (13).
7. Supercritical carbon dioxide cycle system according to claim 5, characterized in that the re-compressor (12) is connected to the rotor of the high pressure turbine (2).
8. Supercritical carbon dioxide cycle system according to claim 1, characterized in that the exhaust (2b) of the high pressure turbine (2) is connected to the inlet (3a) of the low pressure turbine (3) via the heat source (1).
9. Supercritical carbon dioxide cycle system according to claim 1, characterized in that the main compressor (8) and the pre-compressor (6) are both connected to the rotor of the high pressure turbine (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911395091.2A CN113123839A (en) | 2019-12-30 | 2019-12-30 | Supercritical carbon dioxide circulation system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911395091.2A CN113123839A (en) | 2019-12-30 | 2019-12-30 | Supercritical carbon dioxide circulation system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113123839A true CN113123839A (en) | 2021-07-16 |
Family
ID=76767667
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911395091.2A Pending CN113123839A (en) | 2019-12-30 | 2019-12-30 | Supercritical carbon dioxide circulation system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113123839A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107355269A (en) * | 2017-07-13 | 2017-11-17 | 上海发电设备成套设计研究院有限责任公司 | A kind of supercritical carbon dioxide and helium combined cycle system |
| US20180156075A1 (en) * | 2016-12-06 | 2018-06-07 | Doosan Heavy Industries & Construction Co., Ltd | Supercritical co2 generation system for series recuperative type |
| CN108612573A (en) * | 2018-07-05 | 2018-10-02 | 华北电力大学 | A kind of supercritical carbon dioxide Brayton cycle electricity generation system |
| CN208138011U (en) * | 2018-02-28 | 2018-11-23 | 上海发电设备成套设计研究院有限责任公司 | A kind of supercritical carbon dioxide circulating solar energy heat generating system with cold-storage |
| CN109826685A (en) * | 2019-03-12 | 2019-05-31 | 上海发电设备成套设计研究院有限责任公司 | A supercritical carbon dioxide cycle coal-fired power generation system and method |
| CN110030048A (en) * | 2019-04-28 | 2019-07-19 | 三峡大学 | A kind of S-CO2Recycle the nuclear power generating system combined with ORC circulation and heat circulation method |
-
2019
- 2019-12-30 CN CN201911395091.2A patent/CN113123839A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20180156075A1 (en) * | 2016-12-06 | 2018-06-07 | Doosan Heavy Industries & Construction Co., Ltd | Supercritical co2 generation system for series recuperative type |
| CN107355269A (en) * | 2017-07-13 | 2017-11-17 | 上海发电设备成套设计研究院有限责任公司 | A kind of supercritical carbon dioxide and helium combined cycle system |
| CN208138011U (en) * | 2018-02-28 | 2018-11-23 | 上海发电设备成套设计研究院有限责任公司 | A kind of supercritical carbon dioxide circulating solar energy heat generating system with cold-storage |
| CN108612573A (en) * | 2018-07-05 | 2018-10-02 | 华北电力大学 | A kind of supercritical carbon dioxide Brayton cycle electricity generation system |
| CN109826685A (en) * | 2019-03-12 | 2019-05-31 | 上海发电设备成套设计研究院有限责任公司 | A supercritical carbon dioxide cycle coal-fired power generation system and method |
| CN110030048A (en) * | 2019-04-28 | 2019-07-19 | 三峡大学 | A kind of S-CO2Recycle the nuclear power generating system combined with ORC circulation and heat circulation method |
Non-Patent Citations (1)
| Title |
|---|
| 庞麓鸣等, 人民教育出版社 * |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US11614003B2 (en) | Combined cooling, heating and power system | |
| CN109736909B (en) | Compressed air energy storage system for multi-energy supply | |
| JP3230516U (en) | Supercritical carbon dioxide Brayton cycle power generation system for waste heat recovery | |
| KR101984122B1 (en) | Complex generation system with multi-supercritical carbon dioxide generationand and fuel cell | |
| CN102449271B (en) | Steam power cycle device | |
| CN205779057U (en) | Closed combined cooling and power energy storage system | |
| CN107355269B (en) | Supercritical carbon dioxide and helium combined cycle system | |
| CN105863753A (en) | Closed combined cooling and power energy storage system | |
| CN111365131B (en) | Power-cooling combined supply system driven by exhaust smoke waste heat of gas turbine and method thereof | |
| CN114198173B (en) | Electric cooling combined supply system integrating full-regenerative brayton cycle and absorption refrigeration | |
| CN101344075A (en) | Self-cascading solar low temperature Rankine cycle system | |
| CN114704456A (en) | A multi-source heat storage compressed air energy storage system coupled with electric heat storage | |
| CN112943385A (en) | Liquid compressed air energy storage system and method coupled with photo-thermal power generation | |
| CN114370391B (en) | A supercritical compressed air energy storage system | |
| CN110486968A (en) | One kind being based on CO2The combined cooling and power system of working medium | |
| CN111365130B (en) | A gas turbine waste heat utilization system and method using LNG cold energy | |
| CN216342359U (en) | A combined heat and power device combining carbon dioxide power generation and geothermal energy | |
| CN108771950A (en) | A kind of carbon dioxide recycle electricity generation system and method being pressurized using chemical absorbing | |
| CN116025440A (en) | A high-efficiency supercritical carbon dioxide high-temperature gas-cooled reactor system and its operation method | |
| CN208073574U (en) | A kind of three regenerator supercritical carbon dioxide cycle generating system of three turbine | |
| KR101812919B1 (en) | Complex supercritical CO2 generation system | |
| CN207647560U (en) | Supercritical carbon dioxide and helium combined cycle system | |
| CN114893298B (en) | A closed refrigeration energy storage power generation system | |
| CN113123839A (en) | Supercritical carbon dioxide circulation system | |
| CN113123840A (en) | Supercritical carbon dioxide circulation system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20210716 |