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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- Prior art keywords
- gas turbine
- temperature
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- heat exchanger
- temperature heat
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- 238000003303 reheating Methods 0.000 title claims abstract 6
- 238000010438 heat treatment Methods 0.000 title description 2
- 239000000112 cooling gas Substances 0.000 title 1
- 238000001816 cooling Methods 0.000 claims abstract description 16
- 238000010248 power generation Methods 0.000 claims abstract 3
- 238000011084 recovery Methods 0.000 claims abstract 3
- 239000003507 refrigerant Substances 0.000 claims abstract 2
- 239000007788 liquid Substances 0.000 abstract description 11
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 abstract description 8
- 229910021529 ammonia Inorganic materials 0.000 abstract description 4
- 239000000203 mixture Substances 0.000 abstract description 3
- 239000000498 cooling water Substances 0.000 abstract description 2
- 230000005611 electricity Effects 0.000 abstract description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 abstract 1
- 229910052799 carbon Inorganic materials 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 43
- 239000012530 fluid Substances 0.000 description 19
- 238000000034 method Methods 0.000 description 10
- 230000002427 irreversible effect Effects 0.000 description 6
- 239000003795 chemical substances by application Substances 0.000 description 4
- 239000003245 coal Substances 0.000 description 4
- 238000009434 installation Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000007906 compression Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000003912 environmental pollution Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 235000008331 Pinus X rigitaeda Nutrition 0.000 description 1
- 235000011613 Pinus brutia Nutrition 0.000 description 1
- 241000018646 Pinus brutia Species 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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Classifications
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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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- Engine Equipment That Uses Special Cycles (AREA)
Abstract
本实用新型公开了一种太阳能回热再热中冷燃气轮机循环的热力发电系统，其特征在于：包括第一太阳能聚集器、第二太阳能聚集器，第一高温换热器、第二高温换热器，回热器，中冷器，低温换热器,第一低温工质燃气轮机、第二低温工质燃气轮机，发电机，第一轴流式压气机、第二轴流式压气机，冷却塔；本实用新型通过用氨等制冷剂工质，在高温换热器内二次吸收太阳能热量从液态变成高温高压气体，推动低温工质燃气轮机旋转作功，燃气轮机拖动发电机发电，以冷却水为低温源，低温工质在燃气轮机内膨胀作功后的气体由中冷冷凝器和低温冷凝器冷凝成气液混合体，由轴流式二级压气机压缩成液体送回到换热器，采用回热再热中冷循环，完成一个工作。有不污染环境，低碳的优点。
The utility model discloses a thermal power generation system for solar heat recovery and reheating and intercooling gas turbine cycle, which is characterized in that it comprises a first solar concentrator, a second solar concentrator, a first high-temperature heat exchanger, and a second high-temperature heat exchanger Regenerator, regenerator, intercooler, low-temperature heat exchanger, first low-temperature gas turbine, second low-temperature gas turbine, generator, first axial compressor, second axial compressor, cooling tower ; The utility model uses ammonia and other refrigerants to absorb solar heat twice in the high-temperature heat exchanger from liquid to high-temperature and high-pressure gas, and promotes the rotation of the low-temperature gas turbine to perform work. The gas turbine drives the generator to generate electricity for cooling Water is a low-temperature source, and the gas after the low-temperature working medium expands and works in the gas turbine is condensed into a gas-liquid mixture by the intercooler condenser and the low-temperature condenser, and is compressed into a liquid by the axial-flow two-stage compressor and sent back to the heat exchanger , using reheating, reheating and intercooling cycles to complete a job. It has the advantages of not polluting the environment and low carbon.
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)
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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ID=44471250
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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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|---|---|
| CN (1) | CN201943904U (en) |
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 | A hot wind tower power generation device and method 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 |