CN110836131B - Supercritical carbon dioxide recompression circulating turbine mechanical system - Google Patents
Supercritical carbon dioxide recompression circulating turbine mechanical system Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
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- 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
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K21/00—Steam engine plants not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
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Abstract
The invention discloses a supercritical carbon dioxide recompression cycle turbine mechanical system, wherein a high-temperature and high-pressure supercritical carbon dioxide working medium heated by a heat source rotates in a turbine to do work to drive a generator to generate electricity, a main compressor and a recompressor are driven by a gearbox to rotate to compress the working medium, and the working medium flows through a high-temperature heat regenerator and a low-temperature heat regenerator and then is shunted to enter a main compressor and a recompressor. When the system is started, the starting motor is started and the heat source is closed, and a cold supercritical carbon dioxide cycle is formed in the system. After the compressor gradually reaches the pressure ratio, the heat source and the generator are started, and the supercritical carbon dioxide working medium in the turbine gradually rises in temperature to reach the rated operation state. The arrangement mode of the turbine machinery in the supercritical carbon dioxide recompression cycle is improved through the gearbox, and a safe starting method is considered, so that the component efficiency is improved, and the system complexity and the manufacturing cost are reduced.
Description
Technical Field
The invention belongs to the field of impeller machinery, and particularly relates to a supercritical carbon dioxide recompression cycle turbine mechanical system.
Background
In recent years, the research on the application of the carbon dioxide working medium to the Brayton cycle is widely concerned, the critical pressure of the carbon dioxide is 7.38MPa, the critical temperature is 31.1 ℃, the carbon dioxide has excellent physical properties of large density and small viscosity under the conditions that the pressure is higher than the critical pressure and the temperature is higher than the critical temperature, and the carbon dioxide Brayton cycle core component, namely a turbine and a compressor, can be compact in structure and high in efficiency, so that the carbon dioxide working medium has good engineering application prospects when being applied to power cycle.
The system flow is distributed to the main compressor and the recompressor, the mass flow passing through the cooler is reduced, and the recompression circulation is applied to the supercritical carbon dioxide Brayton system, so that the system efficiency can be improved, the pinch point problem of the heat exchanger design can be improved, and the method is an economic and reliable circulation mode. However, the application of the conventional supercritical carbon dioxide recompression Brayton cycle has many problems, if the main compressor, the recompressor and the turbine adopt a coaxial structure, the physical property change near the critical point of the supercritical carbon dioxide working medium is too large, the recompressor with higher inlet temperature is difficult to design into the same rotating speed with the main compressor, and the turbine operates in a high-temperature environment, so that the difference between the physical property of the working medium and the working condition of the compressor is larger; if the three key components are designed at different rotating speeds, the system is complex, the cost is too high, and the advantage of compact supercritical carbon dioxide Brayton cycle is difficult to highlight.
Disclosure of Invention
The invention aims to provide a supercritical carbon dioxide recompression cycle turbine mechanical system and a starting method aiming at the limitations of the prior art, solves the design difficulties of a supercritical carbon dioxide turbine and a compressor, improves the component efficiency, reduces the complexity and the manufacturing cost of a supercritical carbon dioxide recompression Brayton cycle system, and has wide application prospect.
The invention is realized by adopting the following technical scheme:
a supercritical carbon dioxide recompression cycle turbomachinery system comprises a heat source, a generator, a supercritical carbon dioxide turbine, a gearbox, a main compressor, a secondary compressor, a cooler, a low-temperature heat regenerator and a high-temperature heat regenerator; wherein the content of the first and second substances,
when the system operates, the supercritical carbon dioxide working medium heated by the heat source enters a supercritical carbon dioxide turbine, the supercritical carbon dioxide turbine rotates to do work to drive a generator to generate electricity, and a main compressor and a recompressor are driven to rotate to compress the working medium through a gearbox; the working medium at the outlet of the supercritical carbon dioxide turbine enters a high-temperature heat regenerator to exchange heat with the mixed working medium at the outlet of a low-temperature heat regenerator and the outlet of a recompressor, and then enters a low-temperature heat regenerator to exchange heat with the working medium at the outlet of a main compressor; and part of the working medium after the heat recovery enters a cooler for cooling and enters a main compressor for compression according to the flow dividing coefficient, and the rest part of the working medium directly enters a recompressor for compression, so that circulation is formed.
A further improvement of the invention is that when the system is rated in kW, the supercritical carbon dioxide turbine is of the single-stage centripetal type.
The invention is further improved in that when the power of the system is MW level, the turbine type is 2-4 level axial flow turbine.
The invention has the further improvement that under any power of the system, the main compressor and the recompressor are single-stage centrifugal compressors, the inlet pressure of the main compressor and the inlet pressure of the recompressor are both 7.5-7.8MPa, the pressure ratio is 1.8-2.4, the inlet temperature of the main compressor is 32-35 ℃, and the inlet temperature of the recompressor is 60-65 ℃.
A further development of the invention is that the transmission ratio of the main compressor to the supercritical carbon dioxide turbine is n1The transmission ratio of the recompression machine to the supercritical carbon dioxide turbine is n2Then n is1And n2Rounding after calculation as follows:
wherein a is a flow dividing coefficient, namely the flow of the main compressor is divided by the total flow of the system; no subscript indicates the parameter in the turbine, subscript 1 indicates the parameter in the main compressor, and subscript 2 indicates the parameter in the recompressor; rho is the working medium density at the inlet of the turbine impeller and the outlet of the compressor impeller;
the speed ratio when the turbine and the compressor run; alpha is the airflow angle of the outlet of the turbine nozzle and the inlet of the compressor diffuser; beta is the airflow angle of the inlet of the turbine impeller and the outlet of the compressor impeller; Δ h represents the isentropic enthalpy drop or enthalpy rise of the turbine and compressor flow sections.
The further improvement of the invention is that when the system is started, firstly, a starting motor is started, a main shaft of the starting motor drives a main compressor and a recompressor to start through a gearbox, supercritical carbon dioxide working media with rated temperature and pressure are respectively introduced into inlets of the main compressor and the recompressor, a heat source is closed, and cold supercritical carbon dioxide circulation is formed in the system; and after the compressor gradually reaches the pressure ratio, starting the heat source and the generator, gradually raising the temperature of the supercritical carbon dioxide working medium in the supercritical carbon dioxide turbine to reach the rated operation state of the system, and enabling the generator to form rated power output.
The invention provides a supercritical carbon dioxide recompression cycle turbine mechanical system by successfully integrating the advantages of various prior arts and improving and innovating a supercritical carbon dioxide recompression cycle power generation system, and has the following beneficial technical effects:
the invention improves the system efficiency by adopting the recompression cycle, and for the arrangement of three key components, the gearbox is adopted to connect the supercritical carbon dioxide turbine, the main compressor and the recompressor, so that the system has compact structure, and the cycle complexity and the manufacturing cost are reduced.
Further, when the system power is in a kW level, the turbine type is a single-stage centripetal turbine, and when the system power is in a MW level, the turbine type is a 2-4 stage axial flow turbine, so that the part of the turbine can operate at the optimal speed ratio, and the optimal pneumatic efficiency is realized.
Further, under any power of the system, the main compressor and the recompressor are single-stage centrifugal compressors, enough single-stage pressure ratio can be realized, the inlet pressure of the compressors is 7.5-7.8MPa, the pressure ratio is 1.8-2.4, the inlet temperature of the main compressor is 32-35 ℃, and the inlet temperature of the recompressor is 60-65 ℃. The variable working condition research shows that the pressure ratio is continuously increased along with the decrease of the inlet temperature of the compressor, the compression factor is indicated from the perspective of the compression factor, namely the smaller the compression factor of the same working medium is, the easier the same working medium is to be compressed, the lower the working medium inlet temperatures of the main compressor and the recompressor in the system are both selected, the inlet temperature of the main compressor is close to the critical point of the carbon dioxide working medium, the compression power consumption is small, and the pneumatic efficiency is high.
Further, the transmission ratio n of the main compressor, the recompressor and the turbine1、n2The three key components of the turbine, the main compressor and the recompressor can meet the through-flow size requirement and the processing and manufacturing requirements of pneumatic design and improve the pneumatic efficiency of each component. In a kW-level system, the temperature of a turbine inlet is 500 ℃, and the inlet of a main compressor is connected with the inlet of the main compressorThe temperature is 35 ℃, the inlet temperature of the recompressor is 65 ℃ for example, and the density of the supercritical carbon dioxide working medium at the inlet of the turbine impeller in the system is about 77kg/m3The density of the working medium at the outlet of the impeller of the main compressor is about 502kg/m3The density of the recompression machine impeller outlet working medium is about 257kg/m3. If a split-shaft structure is adopted, in order to meet the rotor dynamics requirement, balancing weights with the axial length of 300mm need to be added into all the turbine parts, and the system volume is greatly increased; if the turbine, the main compressor and the recompressor adopt coaxial structures, the rotating speed of the turbine meeting the optimal speed ratio is about 40000rpm, at the moment, the heights of the nozzle blades and the inlet blades of the impeller movable blades in the turbine are 3mm, the heights of the corresponding outlet blades of the diffuser of the main compressor and the impeller movable blades are 0.5mm, and the heights of the outlet blades of the diffuser of the recompressor and the impeller movable blades are 1 mm. Thus, the blade heights of the two compressor parts are difficult to meet manufacturing requirements, and the smaller through-flow size further amplifies the proportion of boundary layer flow losses. By means of a transmission ratio n1、n2The rotating speed of the main compressor and the secondary compressor can be increased, the diameter of the impeller is reduced, the blade heights of the impeller outlets of the main compressor and the secondary compressor and the diffuser are increased to be more than 2mm, the precision required by machining and manufacturing is achieved, the flow loss caused by a boundary layer is reduced, and the efficiency of the two compressor parts can be improved to 80% from 70% in CFD calculation. Further, when the system is started, the starting motor is started to drive the main compressor and the recompressor to start, the heat source is closed, and cold supercritical carbon dioxide circulation is formed in the system. After the compressor gradually reaches the pressure ratio, the heat source and the generator are started, and the supercritical carbon dioxide working medium in the turbine is gradually heated to form rated power output. By the starting method, the running safety of the system is guaranteed, and the reliability of the turbine part is improved.
In conclusion, the supercritical carbon dioxide recompression cycle turbomachinery system provided by the invention has the advantages that the arrangement modes of three key components, namely the turbine, the main compressor and the recompressor are improved, the starting method of the system is improved, the design of the three key components, namely the turbine, the main compressor and the recompressor is ensured to meet the requirements, the component efficiency is improved, the cycle complexity and the manufacturing cost are reduced, and the supercritical carbon dioxide recompression cycle turbomachinery system has a wide engineering application prospect.
Drawings
FIG. 1 is a schematic diagram of a supercritical carbon dioxide recompression cycle turbomachinery system of the present invention.
Description of reference numerals:
the method comprises the following steps of 1-heat source, 2-generator, 3-supercritical carbon dioxide turbine, 4-starting motor, 5-gearbox, 6-main compressor, 7-recompressor, 8-cooler, 9-low temperature regenerator and 10-high temperature regenerator.
Detailed Description
The invention will be further explained with reference to the drawings.
Referring to fig. 1, the supercritical carbon dioxide recompression cycle turbine mechanical system provided by the invention comprises a heat source 1, a generator 2, a supercritical carbon dioxide turbine 3, a starting motor 4, a gearbox 5, a main compressor 6, a recompressor 7, a cooler 8, a low-temperature heat regenerator 9 and a high-temperature heat regenerator 10; when the system operates, the supercritical carbon dioxide working medium heated by the heat source 1 enters the supercritical carbon dioxide turbine 3, the supercritical carbon dioxide turbine 3 rotates to do work to drive the generator 2 to generate electricity, and the main compressor 6 and the recompressor 7 are driven to rotate to compress the working medium through the gearbox 5. The working medium at the outlet of the supercritical carbon dioxide turbine 3 enters the high-temperature heat regenerator 10 to exchange heat with the mixed working medium at the outlet of the low-temperature heat regenerator 9 and the outlet of the recompressor 7, and then enters the low-temperature heat regenerator 9 to exchange heat with the working medium at the outlet of the main compressor 6. And part of the working medium after the heat recovery enters the cooler 8 to be cooled and enters the main compressor 6 to be compressed according to the flow dividing coefficient, and the rest part of the working medium directly enters the secondary compressor 7 to be compressed, so that circulation is formed.
When the system power is in a kW level, the supercritical carbon dioxide turbine is in a single-stage centripetal turbine type; when the system power is MW level, the turbine type is 2-4 level axial flow turbine. Under any power of the system, the main compressor and the recompressor are single-stage centrifugal compressors, the inlet pressure of the main compressor and the inlet pressure of the recompressor are both 7.5-7.8MPa, the pressure ratio is 1.8-2.4, the inlet temperature of the main compressor is 32-35 ℃, and the inlet temperature of the recompressor is 60-65 ℃.
Main compressor and supercritical carbon dioxide turbineHas a transmission ratio of n1The transmission ratio of the recompression machine to the supercritical carbon dioxide turbine is n2Then n is1And n2Rounding after calculation as follows:
wherein a is a flow dividing coefficient, namely the flow of the main compressor is divided by the total flow of the system; no subscript indicates the parameter in the turbine, subscript 1 indicates the parameter in the main compressor, and subscript 2 indicates the parameter in the recompressor; rho is the working medium density at the inlet of the turbine impeller and the outlet of the compressor impeller;
the speed ratio when the turbine and the compressor run; alpha is the airflow angle of the outlet of the turbine nozzle and the inlet of the compressor diffuser; beta is the airflow angle of the inlet of the turbine impeller and the outlet of the compressor impeller; Δ h represents the isentropic enthalpy drop or enthalpy rise of the turbine and compressor flow sections.
When the system is started, the starting motor 4 is started, the main shaft drives the main compressor 6 and the recompressor 7 to start through the gearbox 5, supercritical carbon dioxide working media with rated temperature and pressure are respectively introduced into inlets of the main compressor 6 and the recompressor 7, the heat source 1 is closed, and cold supercritical carbon dioxide circulation is formed in the system. After the compressor gradually reaches the pressure ratio, the heat source 1 and the generator 2 are started, the supercritical carbon dioxide working medium in the supercritical carbon dioxide turbine 3 gradually rises in temperature to reach the rated operation state of the system, and the generator 2 forms rated power output.
The supercritical carbon dioxide recompression cycle turbine mechanical system provided by the invention solves the design difficulties of a supercritical carbon dioxide turbine and a compressor, meets the through-flow size requirement and the processing and manufacturing requirements of pneumatic design, improves the component efficiency, and reduces the complexity and the manufacturing cost of a supercritical carbon dioxide recompression Brayton cycle system.
Claims (6)
1. A supercritical carbon dioxide recompression cycle turbomachinery system is characterized by comprising a heat source (1), a generator (2), a supercritical carbon dioxide turbine (3), a gearbox (5), a main compressor (6), a recompressor (7), a cooler (8), a low-temperature regenerator (9) and a high-temperature regenerator (10); wherein the content of the first and second substances,
when the system operates, the supercritical carbon dioxide working medium heated by the heat source (1) enters the supercritical carbon dioxide turbine (3), the supercritical carbon dioxide turbine (3) rotates to do work to drive the generator (2) to generate electricity, and the main compressor (6) and the recompressor (7) are driven to rotate to compress the working medium through the gearbox (5); the working medium at the outlet of the supercritical carbon dioxide turbine (3) enters a high-temperature regenerator (10), exchanges heat with the mixed working medium at the outlet of a low-temperature regenerator (9) and the outlet of a recompressor (7), and then enters the low-temperature regenerator (9) to exchange heat with the working medium at the outlet of a main compressor (6); and part of the working medium after the heat recovery enters a cooler (8) for cooling and enters a main compressor (6) for compression according to the flow dividing coefficient, and the rest part of the working medium directly enters a secondary compressor (7) for compression, so that circulation is formed.
2. The system of claim 1, wherein the supercritical carbon dioxide turbine is of the single-stage centripetal type when the system is rated in kW.
3. The supercritical carbon dioxide recompression cycle turbomachinery system of claim 1, wherein the turbine is a 2-4 stage axial flow turbine when the system is in MW stage power.
4. The supercritical carbon dioxide recompression cycle turbomachinery system as recited in claim 1, wherein the main compressor and the recompressor are single-stage centrifugal compressors at any power, the inlet pressure of the main compressor and the recompressor is 7.5-7.8MPa, the pressure ratio is 1.8-2.4, the inlet temperature of the main compressor is 32-35 ℃, and the inlet temperature of the recompressor is 60-65 ℃.
5. The supercritical carbon dioxide recompression cycle turbomachinery system of claim 1, wherein the transmission ratio of the main compressor to the supercritical carbon dioxide turbine is n1The transmission ratio of the recompression machine to the supercritical carbon dioxide turbine is n2Then n is1And n2Rounding after calculation as follows:
wherein a is a flow dividing coefficient, namely the flow of the main compressor is divided by the total flow of the system; no subscript indicates the parameter in the turbine, subscript 1 indicates the parameter in the main compressor, and subscript 2 indicates the parameter in the recompressor; rho is the working medium density at the inlet of the turbine impeller and the outlet of the compressor impeller;
the empirical coefficients selected during the design calculation for the turbine and the compressor are called speed ratios; alpha is the airflow angle of the outlet of the turbine nozzle and the inlet of the compressor diffuser; beta is the airflow angle of the inlet of the turbine impeller and the outlet of the compressor impeller; Δ h represents the isentropic enthalpy drop or enthalpy rise of the turbine and compressor flow sections.
6. The supercritical carbon dioxide recompression cycle turbomachinery system as recited in claim 5, wherein when the system is started, the starting motor (4) is firstly started, the main shaft thereof drives the main compressor (6) and the recompressor (7) to start through the gearbox (5), supercritical carbon dioxide working media with rated temperature and pressure are respectively introduced into inlets of the main compressor (6) and the recompressor (7), the heat source (1) is closed, and a cold supercritical carbon dioxide cycle is formed in the system; after the compressor gradually reaches the pressure ratio, the heat source (1) and the generator (2) are started, the supercritical carbon dioxide working medium in the supercritical carbon dioxide turbine (3) is gradually heated to reach the rated operation state of the system, and the generator (2) forms rated power output.
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| CN112880222B (en) * | 2021-01-27 | 2022-12-20 | 郑州大学 | Carbon dioxide transcritical air supplementing and enthalpy increasing system with power generation function |
| CN115013103B (en) * | 2022-07-04 | 2024-05-07 | 西安热工研究院有限公司 | Supercritical carbon dioxide split-flow recompression circulating power generation system and adjusting method |
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| CN106285805B (en) * | 2016-08-10 | 2018-07-10 | 西安热工研究院有限公司 | A kind of coal base supercritical carbon dioxide Brayton cycle electricity generation system of intermediate preheating |
| WO2018131760A1 (en) * | 2017-01-16 | 2018-07-19 | 두산중공업 주식회사 | Complex supercritical carbon dioxide power generation system |
| CN107131017A (en) * | 2017-04-27 | 2017-09-05 | 西安交通大学 | Circulation therrmodynamic system and control method based on supercritical carbon dioxide axial flow compressor Yu axial-flow turbine coaxial configuration |
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| CN108412613A (en) * | 2018-01-24 | 2018-08-17 | 西安热工研究院有限公司 | A kind of biogas-supercritical carbon dioxide recompression cycle generating system |
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