CN201943904U - Thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation - Google Patents
Thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation Download PDFInfo
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- CN201943904U CN201943904U CN2011200201089U CN201120020108U CN201943904U CN 201943904 U CN201943904 U CN 201943904U CN 2011200201089 U CN2011200201089 U CN 2011200201089U CN 201120020108 U CN201120020108 U CN 201120020108U CN 201943904 U CN201943904 U CN 201943904U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines
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Abstract
The utility model discloses a thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation, and is characterized by comprising a first solar-energy collector, a second solar-energy collector, a first high-temperature heat exchanger, a second high-temperature heat exchanger, a return-heater, an intercooler, a low-temperature heat exchanger, a first low-temperature working-medium gas turbine, a second low-temperature working-medium gas turbine, a generator, a first axial-flow compressor, a second axial-flow compressor and a cooling tower. The thermal power generating system enables refrigerant working medium including ammonia and the like to be changed from the liquid status to the high-temperature and high-pressure gas status after a secondary absorption of solar energy in high-temperature heat exchangers, drives low-temperature working-medium gas turbines to rotate to do work, and the gas turbines drive the generator to generate electricity. With cooled water serving as a low-temperature source, the gas generated during the process that low-temperature working medium expand and do work in the gas turbine is condensed into a gas-liquid mixture through the intercooler and a low-temperature condenser. The gas-liquid mixture is compressed into liquid through axial-flow type two-stage compressors and delivered back to heat exchangers, and the return-heating, reheating and inter-cooling circulation is adopted to complete an operation. The thermal power generating system has the advantages that the thermal power generating system causes no pollution to the environment, and is low-carbon in use.
Description
Technical field:
The utility model relates to a kind of solar energy backheat and pines for the heat power generating system of cold gas turbine cycle again, is used in the occasion of solar electrical energy generation.
Background technique:
At present, oil, coal reserves are limited, and rise in price is the CO that fuel combustion produces with oil coal
2, SO
2Environment is produced very big harm, danger utmost point human existence.Utilize solar electrical energy generation, do not have toxic emission.Combustion turbine power is big, and volume is little, good reliability, and the generating efficiency height has development potentiality and application prospect.
Have based on this, the claimant makes the utility model.
The model utility content:
At above-mentioned technical problem to be solved, main purpose of the present utility model provides a kind of reasonable in design, applied widely, carbon-free a kind of solar energy backheat is pined for the heat power generating system of cold gas turbine cycle again.
The technological scheme that the utility model is taked is as follows:
A kind of solar energy backheat is pined for the heat power generating system of cold gas turbine cycle again, it is characterized in that: comprise first solar collector, second solar collector, first high-temperature heat-exchanging, second high-temperature heat-exchanging, regenerator, intercooler, cryogenic heat exchanger, the first cryogenic fluid gas turbine, the second cryogenic fluid gas turbine, generator, first axial-flow compressor, second axial-flow compressor, cooling tower; Wherein: the corresponding installation of first high-temperature heat-exchanging with first solar collector, be used to absorb the heat energy of first solar collector, the corresponding installation of second high-temperature heat-exchanging with second solar collector, the first cryogenic fluid gas turbine links to each other with first high-temperature heat-exchanging, second high-temperature heat-exchanging links to each other with the first cryogenic fluid gas turbine, the second cryogenic fluid gas turbine links to each other with second high-temperature heat-exchanging, generator links to each other with the second cryogenic fluid gas turbine, regenerator links to each other with the second cryogenic fluid gas turbine, cryogenic heat exchanger links to each other with regenerator, cooling tower links to each other with cryogenic heat exchanger, intercooler links to each other with cooling tower, first axial-flow compressor links to each other with cryogenic heat exchanger, intercooler links to each other with first axial-flow compressor, second axial-flow compressor links to each other with intercooler, and regenerator links to each other with second axial-flow compressor, and cooling tower links to each other with intercooler.
Working principle of the present utility model is as follows:
In the utility model, in heat exchanger, all store refrigeration agent, adopt refrigeration agent working medium such as ammonia, become high temperature and high pressure gas from liquid state during from high-temperature heat-exchanging thermal source absorption heat, promote the work done of cryogenic fluid gas turbine; Cryogenic fluid gas behind the expansion working in gas turbine becomes gas liquid mixture by condenser condenses, is compressed into liquid by axial-flow compressor and sends back to heat exchanger and finish a job.
The utility model compared with prior art has the following advantages:
1, without coal, petroleum fuel, there is not boiler;
2, non-environmental-pollution;
3, can adopt solar energy to drive.
Below in conjunction with the drawings and specific embodiments the utility model is further described in detail, following examples are to explanation of the present utility model but the utility model is not limited to following examples.
Description of drawings:
Fig. 1 is a structural representation of the present utility model;
Fig. 2 is the utility model gas turbine heating power circulation T-S figure.
Embodiment:
As shown in Figure 1, solar energy backheat of the present utility model is pined for the heat power generating system of cold gas turbine cycle again, comprise first solar collector 11, second solar collector, 12, the first high-temperature heat-exchangings 13, second high-temperature heat-exchanging 14, regenerator 15, intercooler 16, cryogenic heat exchanger 17, the first cryogenic fluid gas turbines 18, the second cryogenic fluid gas turbine 19, generator 110, first axial-flow compressor 111, second axial-flow compressor 112, cooling tower 113.Wherein first high-temperature heat-exchanging 13 and the 11 corresponding installations of first solar collector, be used to absorb the heat energy of first solar collector 11, second high-temperature heat-exchanging 14 and the 12 corresponding installations of second solar collector, be used to absorb the heat energy of second solar collector 12, the first cryogenic fluid gas turbine 18 links to each other with first high-temperature heat-exchanging 13, second high-temperature heat-exchanging 14 links to each other with the first cryogenic fluid gas turbine 18, the second cryogenic fluid gas turbine 19 links to each other with second high-temperature heat-exchanging 14, generator 110 links to each other with the second cryogenic fluid gas turbine 19, regenerator 15 links to each other with the second cryogenic fluid gas turbine 19, cryogenic heat exchanger 17 links to each other with regenerator 15, cooling tower 113 links to each other with cryogenic heat exchanger 17, intercooler 16 links to each other with cooling tower 113, first axial-flow compressor 111 links to each other with cryogenic heat exchanger 17, intercooler 16 links to each other with first axial-flow compressor 111, second axial-flow compressor 112 links to each other with intercooler 16, regenerator 15 links to each other with second axial-flow compressor 112, and cooling tower 113 links to each other with intercooler 16.
The utility model working procedure is as follows; Refrigeration agent working medium such as ammonia absorb solar heat and become high temperature and high pressure gas from liquid state in high temperature heat exchange A1, promote cryogenic fluid one-level gas turbine T1 rotation work done, gas heats once more to two-stage solar collector A2 after the work done, promote cryogenic fluid second gas burning turbine T2 rotation work done, the two-stage gas turbine drives generator for electricity generation, cryogenic fluid gas behind the expansion working in gas turbine is condensed into gas liquid mixture to regenerator R3, waste heat is passed to gas through two stage compressor C2, return-air is got back to one-level gas compressor C1 by cryogenic heat exchanger R5 cooling, the gas that comes out from a stage compressor C1 is cooled to two-stage compressor C2 by intercooler R4 once more, being compressed into liquid by axial-flow compressor C2 sends back to, regenerator R3 delivers to and finishes a job in the high temperature heat exchange A1.The cooling water of intercooler R4 and cryogenic heat exchanger R5 is circulated by cooling tower.
Consider cold backheat hot-gas turbine circulation again in the irreversible enclosed that works between constant temperature thermal source Tmax and Tmin shown in Figure 2, promptly irreversible constant temperature source brayton cycle l--2--3--4--5--6--7--8--9-10--l.L-2 is that (pressure ratio is the irreversible adiabatic compression process of gas in low pressure compressor
, the ratio of colding pressing in also claiming); 2-3 is the cooling procedure of gas in intercooler; 3--4 is that (pressure ratio is the irreversible adiabatic compression process of gas in high-pressure compressor
,
Be overall pressure tatio); 4--5 is the warm of gas in regenerator; 5--6 is that working medium is from one-level solar collector endothermic process; 6-7 is the irreversible adiabatic expansion process of working medium in the one-level turbine; 7-8 be working medium from two-stage solar collector endothermic process, 8-9 is the irreversible adiabatic expansion process of working medium in two-stage turbine; 9-10 are the exothermic process of exhaust in regenerator; 10 1 l are the exothermic process of exhaust to low-temperature heat source.1--2 s, 3-4 s and 6-7 s are l one 2,3-4 and 6-7 corresponding reversible adiabatic compression and inflation processes.Gas compressor internal loss internal efficiency
(efficient of establishing high-pressure compressor and low pressure compressor is identical), the internal loss internal efficiency of turbo machine
Represent promptly have:
If working medium is the perfect gas of constant specific heat, its thermal capacity is C
WfHeat exchanger, regenerator and intercooler between working medium and high low-temperature heat source is reverse-flow, and its thermal conductivity (heat-transfer coefficient and heat transfer area are long-pending) is respectively U
H, U
L, U
RAnd U
1By the heat transfer between working medium character, thermal source and working medium and the suction as can be known of heat exchanger theory, rate of heat release, backheat rate of heat flow and in cold heat exchange rate of heat flow be respectively:
Circulation output power and efficient are:
P=Q
H1+Q
H2—Q
L—Q
I?，
=P／QH （7）
The utility model is by utilizing refrigeration agent working medium such as ammonia, becomes gaseous state, the volumetric expansion work done from liquid state when high temperature heat source absorbs heat; When the low-temperature heat source heat release, volume shrinkage becomes liquid state again from gaseous state, the pushing turbine acting.Have alternative oil, coal, advantage free from environmental pollution, carbon-free.
Claims (2)
1. a solar energy backheat is pined for the heat power generating system of cold gas turbine cycle again, it is characterized in that: comprise first solar collector, second solar collector, first high-temperature heat-exchanging, second high-temperature heat-exchanging, regenerator, intercooler, cryogenic heat exchanger, the first cryogenic fluid gas turbine, the second cryogenic fluid gas turbine, generator, first axial-flow compressor, second axial-flow compressor, cooling tower; Wherein: the corresponding installation of first high-temperature heat-exchanging with first solar collector, be used to absorb the heat energy of first solar collector, the corresponding installation of second high-temperature heat-exchanging with second solar collector, the first cryogenic fluid gas turbine links to each other with first high-temperature heat-exchanging, second high-temperature heat-exchanging links to each other with the first cryogenic fluid gas turbine, the second cryogenic fluid gas turbine links to each other with second high-temperature heat-exchanging, generator links to each other with the second cryogenic fluid gas turbine, regenerator links to each other with the second cryogenic fluid gas turbine, cryogenic heat exchanger links to each other with regenerator, cooling tower links to each other with cryogenic heat exchanger, intercooler links to each other with cooling tower, first axial-flow compressor links to each other with cryogenic heat exchanger, intercooler links to each other with first axial-flow compressor, second axial-flow compressor links to each other with intercooler, and regenerator links to each other with second axial-flow compressor, and cooling tower links to each other with intercooler.
2. a kind of solar energy backheat according to claim 1 is pined for the heat power generating system of cold gas turbine cycle again, it is characterized in that: all store refrigeration agent in heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200201089U CN201943904U (en) | 2011-01-21 | 2011-01-21 | Thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200201089U CN201943904U (en) | 2011-01-21 | 2011-01-21 | Thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation |
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| Publication Number | Publication Date |
|---|---|
| CN201943904U true CN201943904U (en) | 2011-08-24 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2011200201089U Expired - Fee Related CN201943904U (en) | 2011-01-21 | 2011-01-21 | Thermal power generating system using solar-energy return-heating, reheating and inter-cooling gas turbine circulation |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102691626A (en) * | 2012-01-15 | 2012-09-26 | 河南科技大学 | Hot wind tower power generation device and method by using industrial waste heat and solar energy |
| CN103775239A (en) * | 2013-01-17 | 2014-05-07 | 摩尔动力(北京)技术股份有限公司 | Constant warm pressing approaching cold source heater |
| CN108643982A (en) * | 2018-07-04 | 2018-10-12 | 西安热工研究院有限公司 | A kind of overcritical Brayton cycle electricity generation system and method that band refrigeration is cooling |
| CN112412555A (en) * | 2020-10-10 | 2021-02-26 | 西安交通大学 | Reheating supercritical carbon dioxide power cycle system with indirect cooling |
-
2011
- 2011-01-21 CN CN2011200201089U patent/CN201943904U/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102691626A (en) * | 2012-01-15 | 2012-09-26 | 河南科技大学 | Hot wind tower power generation device and method by using industrial waste heat and solar energy |
| CN102691626B (en) * | 2012-01-15 | 2014-02-19 | 河南科技大学 | Hot wind tower power generation device and method by using industrial waste heat and solar energy |
| CN103775239A (en) * | 2013-01-17 | 2014-05-07 | 摩尔动力(北京)技术股份有限公司 | Constant warm pressing approaching cold source heater |
| CN108643982A (en) * | 2018-07-04 | 2018-10-12 | 西安热工研究院有限公司 | A kind of overcritical Brayton cycle electricity generation system and method that band refrigeration is cooling |
| CN112412555A (en) * | 2020-10-10 | 2021-02-26 | 西安交通大学 | Reheating supercritical carbon dioxide power cycle system with indirect cooling |
| CN112412555B (en) * | 2020-10-10 | 2022-06-21 | 西安交通大学 | Reheating supercritical carbon dioxide power cycle system with indirect cooling |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110824 Termination date: 20140121 |