CN111677571A - Double-shaft compact supercritical carbon dioxide turbine - Google Patents

Double-shaft compact supercritical carbon dioxide turbine Download PDF

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Publication number
CN111677571A
CN111677571A CN202010519711.5A CN202010519711A CN111677571A CN 111677571 A CN111677571 A CN 111677571A CN 202010519711 A CN202010519711 A CN 202010519711A CN 111677571 A CN111677571 A CN 111677571A
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China
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pressure
low
axial flow
shaft
pressure axial
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CN202010519711.5A
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张钰浩
陆道纲
袁永龙
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North China Electric Power University
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North China Electric Power University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • 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
    • F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • F04D25/045—Units comprising pumps and their driving means the pump being fluid-driven the pump wheel carrying the fluid driving means, e.g. turbine blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows

Abstract

The invention discloses a double-shaft compact supercritical carbon dioxide turbine, which belongs to the field of engines; the device comprises a high-pressure shaft and a low-pressure shaft which are arranged in parallel and are provided with independent shaft structures; the high-pressure shaft is a common shaft of the high-pressure axial flow turbine, the high-pressure axial flow compressor and the high-pressure side starting motor; the low-pressure shaft is a common shaft of the low-pressure axial flow turbine, the low-pressure axial flow compressor and the low-pressure side starting motor; the generator is connected with the high-pressure shaft through the speed changing device, the outlet of the gas storage tank, the inlet of the low-pressure axial-flow compressor, the outlet of the low-pressure axial-flow compressor, the inlet of the high-pressure axial-flow compressor, the outlet of the high-pressure axial-flow compressor, the inlet of the heating device, the outlet of the heating device, the inlet of the high-pressure axial-flow turbine, the outlet of the high-pressure axial-flow turbine and the inlet of the gas storage tank are sequentially. The invention adopts a compact turbine device with a parallel double-shaft structure to replace the existing steam Rankine power cycle turbine, thereby effectively improving the thermal cycle efficiency and reducing the volume and the mass of turbine equipment.

Description

Double-shaft compact supercritical carbon dioxide turbine
Technical Field
The invention belongs to the technical field of engines, and particularly relates to a double-shaft compact supercritical carbon dioxide turbine.
Background
CO2The energy-saving device is colorless, tasteless and nontoxic, has better chemical stability and nuclear physical property, is widely existed in the atmosphere, has rich reserves, is cheap and easy to obtain, and is considered to be one of energy transmission and energy conversion working mediums with the most application prospect. The supercritical carbon dioxide is in a state that the temperature reaches 31.1 ℃ and the pressure reaches 7.38MPa, and the carbon dioxide is not ideal gas any more and is changed into very dense fluid, and the fluid has high density similar to liquid and low viscosity similar to gas, and has good fluidity, high heat transfer efficiency and strong work-doing capability. And the critical temperature and pressure of the carbon dioxide are far lower than the critical point of water, so that the supercritical state is easily achieved, and engineering application is facilitated.
At present, most power plants and power plants adopt steam power Rankine cycle, and a common turbine device generally adopts superheated steam heated by a boiler as a working medium to push blades to rotate to do work, so that internal energy of steam is converted into mechanical energy. However, with the increase of rated power, the requirements on high temperature resistance, high pressure resistance and corrosion resistance of turbine materials are higher and higher, and due to the inherent property of water vapor, the overall size of the turbine is obviously increased, the limitation on arrangement space is large, and the investment cost is increased.
Therefore, a novel compact turbine device using supercritical carbon dioxide as a working medium is urgently needed, a parallel double-shaft structure is adopted, and the special advantages of the carbon dioxide in a supercritical state are fully utilized. The turbine needs few stages, the axial size is shortened, the diameter of the impeller is very small, the structure is more compact, the size of the pipeline accessory is small, the size and the weight of equipment are greatly reduced, the structure is simple, the number of accessory equipment is few, the installation is convenient, and the manufacturing and running cost is greatly reduced.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a double-shaft compact supercritical carbon dioxide turbine based on a supercritical carbon dioxide Brayton cycle and integrating the advantages of the prior art, which is characterized by comprising the following steps: the high-pressure shaft and the low-pressure shaft are arranged in parallel and have independent shaft structures; the high-pressure shaft is a common shaft of the high-pressure axial flow turbine, the high-pressure axial flow compressor and the high-pressure side starting motor, and the high-pressure axial flow turbine, the high-pressure axial flow compressor and the high-pressure side starting motor have the same rotating speed; the low-pressure shaft is a common shaft of the low-pressure axial flow turbine, the low-pressure axial flow compressor and the low-pressure side starting motor, and the low-pressure axial flow turbine, the low-pressure axial flow compressor and the low-pressure side starting motor have the same rotating speed;
the generator is connected with the high-pressure shaft through the speed changing device, so that the high-pressure shaft drives a load; the outlet of the gas storage tank, the inlet of the low-pressure axial flow compressor, the outlet of the low-pressure axial flow compressor, the inlet of the high-pressure axial flow compressor, the outlet of the high-pressure axial flow compressor, the inlet of the heating device, the outlet of the heating device, the inlet of the high-pressure axial flow turbine, the outlet of the high-pressure axial flow turbine and the inlet of the gas storage tank are sequentially connected to form a loop.
The high-pressure shaft is sequentially provided with a high-pressure side starting motor, a left radial bearing, a high-pressure axial flow compressor, a dynamic seal, a thrust bearing, a dynamic seal, a high-pressure axial flow turbine, a right radial bearing and a speed change device from left to right.
And a low-pressure side starting motor, a left radial bearing, a low-pressure axial flow compressor, a dynamic seal, a thrust bearing, a dynamic seal, a low-pressure axial flow turbine and a right radial bearing are sequentially arranged on the low-pressure shaft from left to right.
And a diffuser is arranged at the outlet of the low-pressure axial flow turbine.
The high-pressure axial flow turbine and the low-pressure axial flow compressor both adopt a multistage axial flow structural stage for a turbine.
The stage number of the high-pressure axial flow turbine and the stage number of the low-pressure axial flow turbine are four stages.
The stage pressure ratio of the low-pressure axial flow compressor to the high-pressure axial flow compressor is 1.6, and the working medium pressure at the outlet of the low-pressure axial flow compressor is reduced to 7.7 MPa.
A rotatable guide vane is arranged in front of the first stage of the low-pressure axial flow compressor, and a pinion for adjusting the angle of the guide vane is arranged at the root of the guide vane.
The invention has the beneficial effects that:
1. the compact turbine device with the parallel double-shaft structure is adopted to replace the existing steam Rankine power cycle turbine, so that the thermal cycle efficiency is effectively improved, the volume and the mass of turbine equipment are reduced, and the operation and maintenance cost is reduced.
2. In order to adapt to the development of high-temperature, high-pressure ratio and high-efficiency gas turbines, the gas compressor is divided into a high-pressure rotor and a low-pressure rotor which are respectively driven by two turbines.
3. Compared with steam Rankine cycle, the supercritical carbon dioxide cycle has less corrosivity to metals, low noise in the operation process of a turbine, less required cycle compression work, high thermal cycle efficiency and greatly improved safety, and has wide application prospect.
Drawings
FIG. 1 is a schematic block diagram of an embodiment of a two-shaft compact supercritical carbon dioxide turbine according to the present invention;
FIG. 2 is a view of a high pressure shaft support seal according to an embodiment of the present invention;
FIG. 3 is a schematic structural view of an axial turbine blade according to an embodiment of the present invention;
FIG. 4 is a graph of cycle efficiency in an embodiment of the invention.
Wherein:
2-low pressure shaft, 3-high pressure shaft, 4-heating device, 7-speed changing device, 8-generator, 9-gas storage tank, 21-low pressure side starting motor, 22-low pressure axial flow compressor, 23-low pressure axial flow turbine, 31-high pressure side starting motor, 32-high pressure axial flow compressor and 33-high pressure axial flow turbine.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings.
The embodiment of the present invention shown in fig. 1 includes: a high pressure shaft 3 and a low pressure shaft 2 which are arranged in parallel and have independent shaft structures; the high-pressure shaft 3 is a common shaft of the high-pressure axial flow turbine 33, the high-pressure axial flow compressor 32 and the high-pressure side starting motor 31, and the high-pressure axial flow turbine 33, the high-pressure axial flow compressor 32 (high-pressure compressor) and the high-pressure side starting motor 31 are sequentially arranged on the high-pressure shaft 3, so that the high-pressure axial flow turbine 33, the high-pressure axial flow compressor 32 and the high-pressure side starting motor 31 have the same rotating speed; the low-pressure shaft 2 is a common shaft of a low-pressure axial flow turbine 23, a low-pressure axial flow compressor 22 (low-pressure compressor) and a low-pressure side starting motor 21, and the low-pressure axial flow turbine 23, the low-pressure axial flow compressor 22 and the low-pressure side starting motor 21 are sequentially arranged on the low-pressure shaft 2;
the generator 8 is connected with the high-pressure shaft 3 through the speed changing device 7, so that the high-pressure shaft 3 drives the load, and the efficiency under partial load is superior to that of a gas turbine driven by a single shaft;
the outlet of the gas storage tank 9, the inlet of the low-pressure axial flow compressor 22, the outlet of the low-pressure axial flow compressor 22, the inlet of the high-pressure axial flow compressor 32, the outlet of the high-pressure axial flow compressor 32, the inlet of the heating device 4, the outlet of the heating device 4, the inlet of the high-pressure axial flow turbine 33, the outlet of the high-pressure axial flow turbine 33 and the inlet of the gas storage tank 9 are sequentially connected to form a loop. In the operation process, the high-pressure axial flow turbine 33 drives the impeller of the high-pressure axial flow compressor 32 to rotate to compress the working medium, and the working medium and the impeller have the same rotating speed, so that the operation cost is effectively reduced.
The low-pressure axial flow turbine 23 and the high-pressure axial flow turbine 33 have independent shaft structures, and the exhaust from the high-pressure axial flow turbine 33 pushes the impeller of the low-pressure axial flow turbine 23 to rotate, and the low-pressure axial flow turbine 23 drives the impeller of the low-pressure axial flow compressor 22 to rotate through the low-pressure shaft 2. Meanwhile, as the high-pressure axial flow turbine 33 is coaxially connected with the high-pressure axial flow compressor 32, the high-temperature high-pressure carbon dioxide working medium from the heating device 4 pushes the impeller of the high-pressure axial flow turbine 33 to rotate and do work. And a diffuser is installed at the outlet of the low-pressure axial flow turbine 23 to reduce the efficiency decrease.
As shown in the sealing and bearing arrangement mode of FIG. 2, a high-pressure side starting motor 31, a left radial bearing 10, a high-pressure axial flow compressor 32, a dynamic seal A-A, a dynamic seal B-B, a thrust bearing 11, a dynamic seal A-A, a dynamic seal B-B, a high-pressure axial flow turbine 33, a right radial bearing 12 and a speed change device 7 are sequentially arranged on the high-pressure shaft 3 from left to right.
The support bearings including the left radial bearing 10 and the right radial bearing 12 are any one of an air foil bearing, an electromagnetic bearing, and an oil-lubricated bearing.
2 paths of dynamic seals are arranged at the shaft end of the outlet side of the high-pressure axial flow compressor 32 and the shaft end of the inlet side of the high-pressure axial flow turbine 33, a first path of dynamic seal A-A is arranged in a mode of clinging to the outlet of the compressor and the inlet of the turbine, a non-contact dry gas sealing mode is adopted, and friction loss does not exist in the sealing; the second dynamic seal B-B adopts a contact type mechanical dynamic seal structure. Zero leakage of the supercritical carbon dioxide working medium in the compressor and the turbine chamber can be basically realized by adopting 2 paths of dynamic seals.
In the present embodiment, the low pressure shaft 2 uses the same sealing arrangement as the high pressure shaft 3.
The working flow of this embodiment is:
when the device is started: the high-pressure side starting motor 31 and the low-pressure side starting motor 21 respectively drive impellers of the high-pressure axial flow compressor 32 and the low-pressure axial flow compressor 22 to rotate, and after working media enter a turbine through heating of a heat source and start to drive the impellers to rotate, the high-pressure side starting motor 31 and the low-pressure side starting motor 21 are closed.
When in work: CO in the gas tank 92The working medium enters the low-pressure axial flow compressor 22 and the high-pressure axial flow compressor 32 in sequence for compression, wherein CO at the inlet of the low-pressure axial flow compressor 222The pressure of the working medium is 7.7MPa, the temperature is 32.8 ℃, and the pressure of the working medium at the outlet of the high-pressure axial flow compressor 32 can reach 20 MPa. The outlet of the high-pressure axial flow compressor 32 is connected with the inlet of the heating device 4, and the high-temperature and high-pressure supercritical CO at the outlet of the heating device 42The working medium then enters the high-pressure axial flow turbine 33 from the inlet of the high-pressure axial flow turbine 33 and pushes the impeller to do work, so that the working medium is filled inHigh pressure axial flow turbine 33 (supercritical CO) capable of converting into mechanical energy2Turbine) to drive the generator 8 by the high-pressure shaft 3 and the speed-changing device 7 to generate electricity. The pressure of the carbon dioxide working medium at the inlet of the high-pressure axial flow turbine 33 reaches 20MPa, the temperature is up to 600 ℃, and the high-temperature high-pressure working medium pushes the impeller of the high-pressure axial flow turbine 33 to rotate and do work. The low-pressure axial flow turbine 23 is used for reducing the pressure of the working medium before reaching the high-pressure axial flow turbine 33, and the low-pressure axial flow turbine 23 reduces the pressure of the flowing working medium to 7.7MPa while driving the low-pressure axial flow compressor 22 to rotate; if only the high-pressure axial flow turbine is used, the number of stages of the turbine must be increased to meet the requirement of outlet pressure. Carbon dioxide after work is cooled and returns to CO2And a high-pressure air storage tank 9 forms closed circulation.
In this embodiment, the high-pressure axial flow turbine 33(HT) and the low-pressure axial flow turbine 23(LT) both adopt a multistage axial flow structure, the stages of the stages 23 of the high-pressure axial flow turbine 33 and the low-pressure axial flow turbine are all four stages, and as shown in fig. 4, the blades are all in a symmetrical uniform cross-section structure form, and a subsonic oblique nozzle local air intake mode is adopted.
In the present embodiment, the stage pressure ratio of the low-pressure axial compressor 22 and the high-pressure axial compressor 32 is 1.6. A rotatable guide vane is arranged in front of the first stage of the low-pressure axial flow compressor 22, a pinion is arranged at the root of the guide vane, the angle of the guide vane can be adjusted, surging is prevented, and the compressor can keep stable operation. CO at the inlet of the low pressure axial compressor 222The pressure of the working medium is 7.7MPa, the temperature is 32.8 ℃, and the pressure of the working medium at the outlet of the high-pressure axial flow compressor 32 can reach 19.8 MPa.
In this example, the inlet pressure of the high pressure axial flow turbine 33 was 19.8MPa at 550 ℃ and the outlet pressure of the low pressure axial flow compressor 22(LT) was 7.7MPa at 479.4 ℃.
In this embodiment, the heating device 4 adopts a sodium-cooled fast reactor with a mature technology, and the primary sodium loop is used as a heat source, the temperature of the coolant at the core outlet can reach 500-. At this time, S-CO is shown in FIG. 32The thermal efficiency of the brayton cycle is over 45%. Carbon dioxide working medium axial flow pressure at high pressureThe pressure in the compressor 32 is increased, the supercritical carbon dioxide with the pressure of 19.8MPa and the temperature of 550 ℃ is formed by heating through a heat source, then the supercritical carbon dioxide enters the high-pressure axial flow turbine 33 from the inlet of the high-pressure axial flow turbine 33 and expands in the high-pressure axial flow turbine 33(HT) to do work, and the high-pressure axial flow turbine 33 drives the high-pressure shaft 3 and the high-pressure axial flow compressor 32 to work.
In this embodiment, the pressure of the carbon dioxide in the gas holder 9 is maintained at 7.7 MPa.
The thermal power of this embodiment is 5MW, and the generating power is 2.2MW, belongs to small-size power output device, can be used to ocean nuclear power platform and space flight field.

Claims (8)

1. A dual-shaft compact supercritical carbon dioxide turbine, comprising: a high pressure shaft (3) and a low pressure shaft (2) which are arranged in parallel and have independent shaft structures; the high-pressure shaft (3) is a common shaft of the high-pressure axial flow turbine (33), the high-pressure axial flow compressor (32) and the high-pressure side starting motor (31), and the high-pressure axial flow turbine (33), the high-pressure axial flow compressor (32) and the high-pressure side starting motor (31) have the same rotating speed; the low-pressure shaft (2) is a common shaft of the low-pressure axial flow turbine (23), the low-pressure axial flow compressor (22) and the low-pressure side starting motor (21), and the low-pressure axial flow turbine (23), the low-pressure axial flow compressor (22) and the low-pressure side starting motor (21) have the same rotating speed;
the generator (8) is connected with the high-pressure shaft (3) through the speed changing device (7), so that the load is driven by the high-pressure shaft (3); the outlet of the gas storage tank (9), the inlet of the low-pressure axial flow compressor (22), the outlet of the low-pressure axial flow compressor (22), the inlet of the high-pressure axial flow compressor (32), the outlet of the high-pressure axial flow compressor (32), the inlet of the heating device (4), the outlet of the heating device (4), the inlet of the high-pressure axial flow turbine (33), the outlet of the high-pressure axial flow turbine (33) and the inlet of the gas storage tank (9) are sequentially connected to form a loop.
2. The dual-shaft compact supercritical carbon dioxide turbine according to claim 1, characterized in that a high-pressure side starting motor (31), a left side radial bearing (10), a high-pressure axial compressor (32), a dynamic seal (a-a), a dynamic seal (B-B), a thrust bearing (11), a dynamic seal (a-a), a dynamic seal (B-B), a high-pressure axial turbine (33), a right side radial bearing (12) and a speed change device (7) are arranged on the high-pressure shaft (3) from left to right in this order.
3. The dual-shaft compact supercritical carbon dioxide turbine according to claim 1 is characterized in that a low-pressure side starting motor (21), a left radial bearing (10), a low-pressure axial compressor (22), a dynamic seal (a-a), a dynamic seal (B-B), a thrust bearing (11), a dynamic seal (a-a), a dynamic seal (B-B), a low-pressure axial turbine (23) and a right radial bearing (12) are arranged on the low-pressure shaft (2) from left to right in sequence.
4. The two-shaft compact supercritical carbon dioxide turbine according to claim 1, characterized in that a diffuser is installed at the outlet of the low-pressure axial flow turbine (23).
5. The twin-shaft compact supercritical carbon dioxide turbine according to claim 1, characterized in that the high-pressure axial flow turbine (33) and the low-pressure axial flow compressor (22) each employ a multistage axial flow type structural stage.
6. The twin-shaft compact supercritical carbon dioxide turbine according to claim 5, characterized in that the number of stages of the high-pressure axial flow turbine (33) and the number of stages (23) of the low-pressure axial flow turbine are four stages.
7. The dual-shaft compact supercritical carbon dioxide turbine according to claim 1, characterized in that the stage pressure ratio of the low-pressure axial compressor (22) and the high-pressure axial compressor (32) is 1.6, and the working medium pressure at the outlet of the low-pressure axial compressor (22) is reduced to 7.7 MPa.
8. The twin-shaft compact supercritical carbon dioxide turbine according to claim 7, characterized in that a rotatable vane is installed in front of the first stage of the low-pressure axial compressor (22), and a pinion for adjusting the angle of the vane is installed at the root of the vane.
CN202010519711.5A 2020-06-09 2020-06-09 Double-shaft compact supercritical carbon dioxide turbine Pending CN111677571A (en)

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CN112343680A (en) * 2020-11-03 2021-02-09 上海齐耀动力技术有限公司 Supercritical carbon dioxide power generation system and operation control method thereof
CN114251136A (en) * 2021-12-20 2022-03-29 中国科学院工程热物理研究所 Compression expansion type energy storage system and energy storage control method

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CN114251136A (en) * 2021-12-20 2022-03-29 中国科学院工程热物理研究所 Compression expansion type energy storage system and energy storage control method

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