CN112814755A - High-efficiency supercritical CO2Closed cycle power system - Google Patents
High-efficiency supercritical CO2Closed cycle power system Download PDFInfo
- Publication number
- CN112814755A CN112814755A CN202011609289.9A CN202011609289A CN112814755A CN 112814755 A CN112814755 A CN 112814755A CN 202011609289 A CN202011609289 A CN 202011609289A CN 112814755 A CN112814755 A CN 112814755A
- Authority
- CN
- China
- Prior art keywords
- compressor
- regenerator
- communicated
- pipeline
- point
- 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
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims abstract description 12
- 230000005540 biological transmission Effects 0.000 claims abstract description 12
- 229910002092 carbon dioxide Inorganic materials 0.000 claims abstract description 12
- 239000001569 carbon dioxide Substances 0.000 claims abstract description 5
- 239000000463 material Substances 0.000 abstract description 4
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 238000012423 maintenance Methods 0.000 abstract description 2
- 238000013461 design Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000005381 potential energy Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/08—Adaptations for driving, or combinations with, pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses efficient supercritical CO2The closed cycle power system comprises an A compressor, a B regenerator, a C regenerator, a heater and a driving turbine which are sequentially communicated, wherein the output end of the driving turbine, a C regenerator heat exchange pipeline and a B regenerator heat exchange pipeline are sequentially communicated, the heat exchange pipeline of the B regenerator is communicated with the input port of the A compressor through a precooler, the A compressor is in transmission connection with the C compressor which is in transmission connection with the driving turbine, the input end of the C compressor is communicated with a pipeline between the B regenerator and a precooler, and the output end of the C compressor is communicated with a flow dividing point B between the B regenerator and the C regenerator. The invention has the beneficial effects that: this scheme adopts supercritical carbon dioxide circulation as the medium that provides power, can reduce the operating temperature of equipment to reduce high temperature resistant material's use, reduce equipment cost, this scheme can adopt turbomachinery as core machine, thereby reduce the maintenance cost in later stage, and improve annAnd (4) full performance.
Description
Technical Field
The invention relates to the technical field of power equipment, in particular to efficient supercritical CO2Closed cycle power systems.
Background
The power equipment is equipment for converting, transmitting and adjusting various potential energy sources in nature. In the production process of enterprises, the energy-saving machine system can convert the potential energy of nature into mechanical energy, then convert the mechanical energy into electric energy and convert the electric energy into the mechanical energy.
A power plant commonly used under the prior art conditions is a gas turbine, but the gas turbine needs to combust fuel to generate heat energy, so that the inside of the system is in a high-temperature environment, and in order to meet the performance requirements and safety requirements of the plant, a hardware system needs to be prepared by adopting a high-temperature-resistant material, so that the cost of the system is overhigh.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide high-efficiency supercritical CO2Compared with a gas turbine, the closed cycle power system has lower operating temperature, can reduce the use of high-temperature resistant materials, and reduces the use cost of equipment.
The invention is realized by the following technical scheme: high-efficiency supercritical CO2The closed cycle power system comprises an A compressor, a B heat regenerator, a C heat regenerator, a heater and a driving turbine which are sequentially communicated through pipelines according to the flowing direction of carbon dioxide, wherein the output end of the driving turbine, a C heat regenerator heat exchange pipeline and a B heat regenerator heat exchange pipeline are sequentially communicated, the heat exchange pipeline of the B heat regenerator is communicated with the input port of the A compressor through a precooler, the A compressor is in transmission connection with the C compressor which is in transmission connection with the driving turbine, the input end of the C compressor is communicated with the pipeline between the B heat regenerator and the precooler, and the output end of the C compressor is communicated with the pipeline between the BAnd a diversion point e is arranged between the heater and the driving turbine at a diversion point B between the heat regenerator B and the heat regenerator C, and the diversion point e is communicated with the power turbine.
Furthermore, in order to better realize the invention, a driving turbine air inlet valve is communicated between the heater and the driving turbine.
Further, in order to better realize the invention, a power turbine air inlet valve 13 is arranged between the diversion point e and the power turbine 5, the power turbine is communicated with a diversion point f positioned between the power turbine and a heat exchange pipeline of the heat regenerator B, and the power turbine is in transmission connection with a power output structure.
Furthermore, in order to better realize the invention, a pipeline between the diversion point e and the power turbine air inlet valve is provided with a diversion point c, the diversion point c is sequentially communicated with a bypass valve and a pressure reducing valve according to the gas flow direction, and the pressure reducing valve is communicated with a diversion point d between the diversion point f and the power turbine.
Furthermore, in order to better realize the invention, an intercooler and a compressor B are sequentially arranged on a pipeline between the compressor A and the heat regenerator B, the compressor B is in transmission connection between the compressor A and the compressor C, a shunting point a is arranged on a pipeline between the compressor A and the intercooler, and the pipeline between the inlet end of the compressor C and the heat regenerator B is disconnected and communicated with the shunting point a.
Furthermore, in order to better realize the invention, the pipeline between the B heat regenerator and the precooler is provided with the A heat regenerator, and the pipelines between the flow dividing point a and the C compressor are respectively communicated with two ends of the A heat regenerator heat exchange tube in the A heat regenerator.
Furthermore, in order to better realize the invention, a pipeline between the power turbine and the diversion point d is sequentially communicated with a heater B, a low-pressure power turbine air inlet valve and a low-pressure power turbine in the gas flow direction.
The beneficial effect that this scheme obtained is: this scheme adopts supercritical carbon dioxide circulation as the medium that provides power, can reduce the operating temperature of equipment to reduce high temperature resistant material's use, reduce equipment cost, this scheme can adopt turbomachinery to be the core machine, thereby reduce the maintenance cost in later stage, and improve the security performance.
Drawings
FIG. 1 is a schematic structural diagram of the present embodiment;
FIG. 2 is a schematic structural view of embodiment 3;
FIG. 3 is a schematic structural view of example 4;
FIG. 4 is a schematic structural view of example 5;
the system comprises a 1-A compressor, a 2-B compressor, a 3-C compressor, a 4-drive turbine, a 5-power turbine, a 6-precooler, a 7-intercooler, an 8-A regenerator, an 81-A regenerator heat exchange pipeline, a 9-B regenerator, a 91-B regenerator heat exchange pipeline, a 10-C regenerator, a 101-C regenerator heat exchange pipeline, an 11-heater, a 12-drive turbine air inlet valve, a 13-power turbine air inlet valve, a 14-bypass valve, a 15-pressure reducing valve, a 16-power output, a 17-low-pressure power turbine, an 18-low-pressure power turbine air inlet valve and a 19-B heater.
Detailed Description
The present invention will be described in further detail with reference to examples, but the embodiments of the present invention are not limited thereto.
Example 1:
as shown in FIG. 1, in this embodiment, a high efficiency supercritical CO2The closed cycle power system comprises an A compressor 1, a B regenerator 9, a C regenerator 10, a heater 11 and a drive turbine 4 which are sequentially communicated through pipelines according to the flowing direction of carbon dioxide, wherein the output end of the drive turbine 4, a B regenerator heat exchange pipeline 91 and a C regenerator heat exchange pipeline 101 are sequentially communicated, the heat exchange pipeline of the B regenerator 9 is communicated with the input port of the A compressor 1 through a precooler 6, the A compressor 1 is in transmission connection with the C compressor 3 in transmission connection with the drive turbine 4, the input end of the C compressor 3 is communicated with the pipeline between the B regenerator 9 and the precooler 6, the output end of the C compressor 3 is communicated with a shunting point B between the B regenerator 9 and the C regenerator 10, a shunting point e is arranged between the heater 11 and the drive turbine 4, and the shunting point e is communicated with the power turbine 5.
When the system works, the working medium is cooled to the design temperature by the precooler 6 and then enters the compressor A1. After being compressed by the compressor A1, the pressure reaches above the supercritical pressure, and then enters the heat regenerator B9 for heat exchange so as to improve the temperature of the working medium. Then enters a heat regenerator 10C to exchange heat with the exhaust gas of the power turbine 5, and the temperature of the working medium is continuously increased. And then the gas enters a heater 11 to be heated to a design temperature, and is divided into two parts at a splitting point e, wherein one part enters a driving turbine 4 to do work, so that the driving turbine 4 outputs power to drive an A gas compressor 1 and a C gas compressor 3 to rotate. The other part enters a power turbine 5 to push the power turbine to do work outwards to output power.
The working medium which does work in the drive turbine 4 enters the heat regenerator heat exchange pipeline 101 of the C heat regenerator 10 to exchange heat with the working medium before doing work. The working medium after heat exchange enters the heat exchanger heat exchange pipeline 91 of the heat exchanger B of the heat exchanger C10 to exchange heat with the working medium before doing work, and finally returns to the precooler 6 to perform precooling and cooling so as to participate in the next cycle.
The scheme does not need to burn fuel to generate heat energy, so that the temperature in the system can be reduced, the requirement of equipment on temperature resistance is lowered, and the equipment cost can be effectively lowered.
Through setting up B regenerator 9 and C regenerator 10, can reduce the temperature of backward flow working medium when heating working medium for the effect of backward flow working medium cooling in precooler 6 can improve, reduces the heat transfer of precooler 6 and environment, has improved energy utilization and system efficiency.
Example 2:
in addition to the above embodiment, in the present embodiment, the drive turbine intake valve 12 is communicated between the heater 11 and the drive turbine 4. The split ratio of the working medium at the e split point can be controlled by adjusting the opening of the drive turbine air inlet valve 12, so that the power of the drive turbine 4 and the power turbine 5 is controlled to adapt to various different working conditions, and the advantage of flexible adjustment is achieved.
On the basis of the above embodiment, in this embodiment, a power turbine intake valve 13 is disposed between the diversion point e and the power turbine 5, the power turbine 5 is communicated with the diversion point f between the power turbine 4 and the regenerator heat exchange pipeline 101, and the power turbine 5 is in transmission connection with a power output structure 16. The efficiency of the power turbine 5 can be controlled by adjusting the opening and closing degree of the power turbine intake valve 13. The working medium which does work in the power turbine 5 is discharged and then mixed with the working medium which is discharged after doing work in the drive turbine 4 at the split point f, and then enters the heat exchange pipeline 101 of the heat regenerator C.
In addition to the above-described embodiments, in the present embodiment, a branch point c is provided in the pipeline between the branch point e and the power turbine intake valve 13, a bypass valve 14 and a pressure reducing valve 15 are sequentially communicated with the branch point c in the gas flow direction, and the pressure reducing valve 15 is communicated with a branch point d between the branch point f and the power turbine 5. When the opening degree of the power turbine air inlet valve 13 is adjusted, the opening degree of the bypass valve 14 and the pressure reducing valve 15 is correspondingly adjusted, so that redundant working media can be discharged through the bypass valve 14 and the pressure reducing valve 15, and the overlarge pressure of a pipeline in front of the power turbine air inlet valve 13 is avoided.
Example 3:
as shown in fig. 2, on the basis of the above embodiment, in this embodiment, an intercooler 7 and a B compressor 2 are sequentially disposed on a pipeline between the a compressor 1 and the B regenerator 9, the B compressor 2 is drivingly connected between the a compressor 1 and the C compressor 3, a diversion point a is disposed on a pipeline between the a compressor 1 and the intercooler 7, and a pipeline between an inlet end of the C compressor 3 and the B regenerator 9 is disconnected and communicated with the diversion point a.
The working medium from the compressor A1 is divided into two paths at a shunting point a, one path enters the intercooler 7 to exchange heat with the environment, the temperature and the pressure of the cooled working medium are slightly higher than the critical point of the working medium, the working medium continuously flows into the compressor B2, and the working medium flows into the heat regenerator B9 after being compressed. And the other part of the working medium enters the C compressor 3 to be compressed. Two parts of working media are mixed after the heat regenerator 9B; the mixed working medium flows into the C heat regenerator 10 to exchange heat with the exhaust gas of the power turbine 5, the temperature of the working medium is continuously increased, and then the working medium enters the heater 11, so that the heating efficiency of the working medium flowing into the C heat regenerator 10 is improved, the heat exchange between the flowing C heat regenerator 10 and the environment is reduced, and the energy utilization rate and the system efficiency can be improved.
Example 4:
as shown in fig. 3, on the basis of the above embodiment, in this embodiment, the pipe between the B regenerator 9 and the precooler 6 is provided with the a regenerator 8, and the pipe between the diversion point a and the C compressor 3 is respectively communicated with two ends of the a regenerator heat exchange pipe 81 in the a regenerator 8.
The working medium is cooled to the design temperature by the precooler 6 and then flows into the compressor A1, and after being compressed by the compressor A, the temperature and the pressure of the working medium are all higher than the critical point. The exhaust gas is divided into two parts at a shunting point a, wherein one part of working medium flows into the intercooler 7, the temperature and the pressure of the cooled working medium are slightly higher than the critical point of the working medium, the working medium continuously flows into the B gas compressor 2, and the working medium flows into the B heat regenerator 9 after being compressed. And another part of the working medium flows into the heat exchange pipeline 81 of the heat regenerator A and exchanges heat with the working medium flowing out of the heat regenerator B9, so that the temperature of the part of the working medium is increased, the temperature of the returned working medium is further reduced, and then the part of the working medium enters the compressor C3 and is compressed to mix the two parts of the working medium after entering the heat regenerator B9. The mixed working medium flows into a C heat regenerator 10 to exchange heat with the exhaust of the power turbine 5, the temperature of the working medium is continuously increased, the working medium enters a heater 11 and is heated to the design temperature and then is divided into two parts at a splitting point e, one part of the two parts enters a driving turbine 4 to push the driving turbine 4 to do work and provide power for a gas compressor, and the other part of the two parts enters the power turbine 5 to push the power turbine to do work and output power. The temperature of the backflow working medium is further reduced, and the precooling efficiency of the backflow working medium in the precooler 6 can be further improved.
Therefore, the heat exchange efficiency between the working media in the system can be further improved, the heat exchange between the system and the external environment is reduced, the utilization rate of the energy in the system is improved, and the system efficiency can be further improved.
Example 5:
as shown in fig. 4, a B heater 19, a low-pressure power turbine intake valve 18, and a low-pressure power turbine 17 are connected to the pipe between the power turbine 5 and the split point d in this order in the gas flow direction.
By arranging the low-pressure power turbine 17, part of the high-pressure exhaust of the power turbine 5 can directly enter the B heater 19 for heating and then enter the low-pressure power turbine 17 for work. Thereby providing two power sources for outputting power. Thereby further improving the efficiency of the system.
In this embodiment, other undescribed contents are the same as those in the above embodiment, and thus are not described again.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications and equivalent variations of the above embodiments according to the technical spirit of the present invention are included in the scope of the present invention.
Claims (7)
1. High-efficiency supercritical CO2Closed cycle driving system, its characterized in that: the system comprises an A air compressor (1), a B heat regenerator (9), a C heat regenerator (10), a heater (11) and a driving turbine (4) which are sequentially communicated through pipelines according to the flowing direction of carbon dioxide, wherein the output end of the driving turbine (4), the C heat regenerator heat exchange pipeline (91) and the B heat regenerator heat exchange pipeline (101) are sequentially communicated, the heat exchange pipeline of the B heat regenerator (9) is communicated with the input port of the A air compressor (1) through a precooler (6), the A air compressor (1) is connected with the C air compressor (3) in a transmission way, the input end of the C air compressor (3) is communicated with the pipeline between the B heat regenerator (9) and the precooler (6), the output end of the C air compressor (3) is communicated with a shunting point B between the B heat regenerator (9) and the C heat regenerator (10), and a shunting point e is arranged between the heater (11) and the driving turbine (4), the flow dividing point e is communicated with a power turbine (5).
2. The high efficiency supercritical CO according to claim 12Closed cycle driving system, its characterized in that: and a driving turbine air inlet valve (12) is communicated between the heater (11) and the driving turbine (4).
3. The high efficiency supercritical CO2 closed cycle power system of claim 2, wherein: and a power turbine air inlet valve (13) is arranged between the diversion point e and the power turbine (5), the power turbine (5) is communicated with a diversion point f between the power turbine (4) and the heat exchanger pipeline (101) of the heat regenerator B, and the power turbine (5) is in transmission connection with a power output structure (16).
4. A high efficiency supercritical CO according to claim 32Closed cycle driving system, its characterized in that: the flow dividing point e and the power turbine air inlet valve(13) The pipeline between the two is provided with a diversion point c, a bypass valve (14) and a pressure reducing valve (15) are sequentially communicated with the diversion point c in the gas flowing direction, and the pressure reducing valve (15) is communicated with a diversion point d between a diversion point f and the power turbine (5).
5. A high efficiency supercritical CO according to any one of claims 1, 2, 3, 42Closed cycle driving system, its characterized in that: an intercooler (7) and a B compressor (2) are sequentially arranged on a pipeline between the A compressor (1) and the B regenerator (9), the B compressor (2) is connected between the A compressor (1) and the C compressor (3) in a transmission mode, a shunting point a is arranged on a pipeline between the A compressor (1) and the intercooler (7), and a pipeline between the inlet end of the C compressor (3) and the B regenerator (9) is disconnected and communicated with the shunting point a.
6. A highly efficient supercritical CO according to claim 52Closed cycle driving system, its characterized in that: a heat regenerator (8) is arranged on a pipeline between the heat regenerator (9) B and the precooler (6), and pipelines between the flow dividing point a and the compressor (3) C are respectively communicated with two ends of a heat regenerator heat exchange pipe (81) in the heat regenerator (8) A.
7. The high efficiency supercritical CO according to claim 42Closed cycle driving system, its characterized in that: and a pipeline between the power turbine (5) and the flow splitting point d is sequentially communicated with a B heater (19), a low-pressure power turbine air inlet valve (18) and a low-pressure power turbine (17) according to the gas flow direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011609289.9A CN112814755A (en) | 2020-12-30 | 2020-12-30 | High-efficiency supercritical CO2Closed cycle power system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011609289.9A CN112814755A (en) | 2020-12-30 | 2020-12-30 | High-efficiency supercritical CO2Closed cycle power system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112814755A true CN112814755A (en) | 2021-05-18 |
Family
ID=75856223
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011609289.9A Pending CN112814755A (en) | 2020-12-30 | 2020-12-30 | High-efficiency supercritical CO2Closed cycle power system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112814755A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014159587A1 (en) * | 2013-03-14 | 2014-10-02 | Echogen Power Systems, L.L.C. | Mass management system for a supercritical working fluid circuit |
| US20160326916A1 (en) * | 2015-05-04 | 2016-11-10 | Doosan Heavy Industries & Construction Co., Ltd. | Supercritical co2 generation system |
| CN108252758A (en) * | 2018-02-09 | 2018-07-06 | 安徽工业大学 | A kind of electricity generation system recycled using steel billet radiation energy and supercritical carbon dioxide |
| CN109340066A (en) * | 2018-10-16 | 2019-02-15 | 中国科学院工程热物理研究所 | A kind of supercritical carbon dioxide solar power generation energy storage integrated system |
| CN208650933U (en) * | 2018-08-17 | 2019-03-26 | 西安热工研究院有限公司 | The working medium displacement apparatus of the non-rotating environment division of supercritical carbon dioxide system |
| US20200131920A1 (en) * | 2018-10-30 | 2020-04-30 | Korea Institute Of Energy Research | Supercritical carbon dioxide power generation system including dry gas seal and method of operating the same |
| CN111951993A (en) * | 2020-07-23 | 2020-11-17 | 东南大学 | Lead-cooled fast reactor supercritical carbon dioxide circulation switchable type vessel power system |
-
2020
- 2020-12-30 CN CN202011609289.9A patent/CN112814755A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014159587A1 (en) * | 2013-03-14 | 2014-10-02 | Echogen Power Systems, L.L.C. | Mass management system for a supercritical working fluid circuit |
| US20160326916A1 (en) * | 2015-05-04 | 2016-11-10 | Doosan Heavy Industries & Construction Co., Ltd. | Supercritical co2 generation system |
| CN108252758A (en) * | 2018-02-09 | 2018-07-06 | 安徽工业大学 | A kind of electricity generation system recycled using steel billet radiation energy and supercritical carbon dioxide |
| CN208650933U (en) * | 2018-08-17 | 2019-03-26 | 西安热工研究院有限公司 | The working medium displacement apparatus of the non-rotating environment division of supercritical carbon dioxide system |
| CN109340066A (en) * | 2018-10-16 | 2019-02-15 | 中国科学院工程热物理研究所 | A kind of supercritical carbon dioxide solar power generation energy storage integrated system |
| US20200131920A1 (en) * | 2018-10-30 | 2020-04-30 | Korea Institute Of Energy Research | Supercritical carbon dioxide power generation system including dry gas seal and method of operating the same |
| CN111951993A (en) * | 2020-07-23 | 2020-11-17 | 东南大学 | Lead-cooled fast reactor supercritical carbon dioxide circulation switchable type vessel power system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN211474436U (en) | Variable-pressure-ratio isothermal compressed air energy storage system | |
| CN109944698B (en) | Method and system for improving flexibility of combined cooling, heating and power supply of gas turbine | |
| WO2023193486A1 (en) | Normal-temperature liquid compressed carbon dioxide mixed working fluid energy storage system and method | |
| CN110887270B (en) | Multistage utilization system and method for waste heat of air compressor | |
| CN115263476A (en) | Control method of supercritical carbon dioxide series double-turbine power generation system | |
| CN107288758B (en) | A kind of the combination gas jet power unit and conversion method of split axle | |
| CN113090506B (en) | Combined cooling, heating and power system and method using compressed air as energy source | |
| CN110793801B (en) | Hybrid indirect cooling compressor experiment system | |
| CN211573739U (en) | Compressed air energy storage system | |
| CN112814755A (en) | High-efficiency supercritical CO2Closed cycle power system | |
| CN217899550U (en) | Gas excess pressure energy recovery device | |
| CN113309612B (en) | Combined cooling, heating and power system for coupling pressure energy, compressed air energy storage and solar energy | |
| CN214221330U (en) | Biogas generator set | |
| CN214741487U (en) | Natural gas turbine decompression power generation system | |
| CN210829422U (en) | Turbine driving gas compression system | |
| CN202228175U (en) | Low-temperature air inlet engine | |
| CN201991617U (en) | Circulating power generation system of pressurized water reactor nuclear power gas turbine | |
| CN207246047U (en) | generating set | |
| CN211976980U (en) | Electric compression heat pump combined step heat exchange large temperature difference pressure isolation machine set | |
| CN116412030B (en) | Multifunctional gas turbine power generation system | |
| CN214145678U (en) | Gas turbine plant | |
| CN113700631B (en) | Low-temperature waste heat multistage coupling utilization system and process for large-sized gas compressor | |
| CN110905611B (en) | Combined supply system based on organic Rankine cycle and supercritical carbon dioxide cycle | |
| CN220728574U (en) | Compressor heat energy comprehensive utilization system | |
| CN217178283U (en) | Coke oven gas compressor nitrogen gas circulation pipeline that can be reserved |
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 |
Application publication date: 20210518 |
|
| RJ01 | Rejection of invention patent application after publication |