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CN104949382A - 太阳辐射能热机 - Google Patents

太阳辐射能热机 Download PDF

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Publication number
CN104949382A
CN104949382A CN201410115030.7A CN201410115030A CN104949382A CN 104949382 A CN104949382 A CN 104949382A CN 201410115030 A CN201410115030 A CN 201410115030A CN 104949382 A CN104949382 A CN 104949382A
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heat engine
working medium
energy
radiant energy
solar radiant
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邱纪林
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Priority to CN201410115030.7A priority Critical patent/CN104949382A/zh
Priority to PCT/CN2014/000798 priority patent/WO2015143590A1/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/02—Devices for producing mechanical power from solar energy using a single state working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Energy (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

太阳辐射能热机以二氧化碳为工质，通过膨胀原理对外做功、制冷，以太阳辐射能(大气、水系、浅地源温度)加热工质，实现热机循环。太阳辐射能热机摆脱了传统热机对化石能源的依赖，是高效、经济利用太阳能的新方法。

Description

太阳辐射能热机
技术领域
本发明涉及一种以二氧化碳为工质，通过膨胀发电制冷，有效利用太阳辐射能的方法。
背景技术
近年来，由于世界人口剧增，工业发展迅速，煤炭、石油、天然气燃烧产生的二氧化碳远超历史水平，严重破坏了地球亿万年来保持的碳平衡。大气中二氧化碳含量每增加1倍，全球气温将升高3℃～5℃，气候变暖导致自然灾害加剧，两极冰川融化，海平面升高，对人类生存和繁衍构成严重的挑战。
1980年全球二氧化碳排放量为50亿吨，2004年超过73亿吨。2008年，中国碳排放超过美国，成为全球排放最大的国家，这与我国以燃煤为主的能源结构有关。我们面临的困境是，到目前为止，所有新能源一直没有革命性的突破；包括光伏和风电技术，效率低，成本远超火电，只能依靠政府补贴生存。
太阳辐射能量巨大，人类目前每年能源消费总和只相当于40分钟内太阳照射到地球的能量。目前利用太阳能的光伏发电效率低，只有12％，每天工作8个小时，晚上无法工作。太阳辐射除大气散射、空中云层吸收等流失外，50％左右是被浅层土壤、水系和大气接收，其蕴藏量巨大。不过太阳辐射能品位低，需要找到一种能够用低品位热做功的热机。
本发明是一种以二氧化碳为工质，通过膨胀对外做功、制冷，利用太阳辐射能(大气、水系、地源温度)加热工质，实现热机循环运行的方法。
发明内容
太阳辐射能热机由膨胀、压缩、热交换三部分组成，其循环运行过程如下：
换热器中的高压液相工质经膨胀机绝热膨胀对外做功，消耗气体工质内能，自身变冷。根据能量转换和守恒定律，气体进行绝热膨张对外作功时，气体能量焓值减少，从而使气体本身强烈冷却，达到制冷目的。膨胀机的制冷量等于气体在膨胀过程减小的焓值。
低温工质经压缩机进入换热器。
在换热器中，工质气液相做相间质量传递并从外界环境温度吸热，工质温度低于临界点。
液相工质再次膨胀，进入下一循环。
太阳辐射能热机的工作原理同火力发电是一致的。火力发电过程，水被加热为蒸汽，气体体积膨胀推动发电机工作。由于工质是水，工作温度必须在100度以上，这就需要外来能源(煤、油、天然气等)加热，热机做功后的乏汽再利用大气环境冷却还原为水。太阳辐射能热机采用二氧化碳为工质，工作温度可以降到大气环境温度以下，可以利用太阳辐射能加热，通过膨胀释放能量来冷却工质。
二氧化碳临界温度低(31.1℃)，临界压力高(7.3Mpa)。从三相点的-56.6℃(0.57兆帕)到临界温度31.1℃(7.3兆帕)，87℃温差下压力提升12.8倍。水的临界温度为374℃，对应7兆帕压力的饱和蒸汽温度约289℃。太阳辐射能热机将低温热源(冷凝)温度设定为20℃，膨胀制冷(蒸发)温度设定为-55℃(略高于CO2的三相点)，两者间温差75℃。根据卡诺热机效率公式，75℃温差热机理论效率为21.56％=1÷COP carnot，实际效率打6折为13％。
二氧化碳和水的性质不同。水从0℃升温到75℃自身压力几乎没有变化，而同样幅度的温升，CO2压力则从0.5兆帕提升至5.7兆帕，有11倍之多。对应5.7兆帕压力，水的饱和蒸汽温度约为274℃。以水来换算，温差75℃的热机(CO2工质)理论效率为50％，实际效率30％，与燃煤火力发电效率相当。
二氧化碳工质通过膨胀机释放热能、对外做功(发电)的同时，产生了与膨胀功等量的冷，所付出的是工质内能的减少，即工质温度从20℃下降到-55℃，压力从5.7兆帕下降到0.5兆帕。而工质从-55℃回升到20℃，压力从0.5兆帕返回到5.7兆帕，其能量来自太阳辐射能。
具体实施方式
换热器中的高压液相工质经膨胀机绝热膨胀对外做功，消耗气体工质内能制冷。低温工质经压缩进入换热器换热，从外界环境温度吸热，液相工质再次膨胀，进入下一循环。太阳辐射能热机二氧化碳循环过程在其两相区间(相当于水在100℃-374℃之间)，为气液两相流。随温度变化，气、液相比随之变化。需要适应两相工质的压缩机和膨胀机，膨胀机替代节流阀以提高效率。

Claims (3)

1.一种以二氧化碳为工质，通过膨胀原理，对外做功、制冷，利用太阳辐射能重新加热工质的热机。
2.根据权利要求1所述，热机的工质为二氧化碳。
3.根据权利要求2所述，二氧化碳工质在其三相点与临界点之间循环运行。
CN201410115030.7A 2014-03-26 2014-03-26 太阳辐射能热机 Pending CN104949382A (zh)

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CN201410115030.7A CN104949382A (zh) 2014-03-26 2014-03-26 太阳辐射能热机
PCT/CN2014/000798 WO2015143590A1 (zh) 2014-03-26 2014-08-26 太阳辐射能热机

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CN110260689A (zh) * 2018-07-23 2019-09-20 郑昊 一种渐进集热逆流水冷却装置

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CN2284937Y (zh) * 1997-03-27 1998-06-24 黄清福 冷冻式压缩空气干燥机之低露点装置
CN1222741C (zh) * 2001-12-06 2005-10-12 天津大学 二氧化碳跨临界制冷循环转子式膨胀机

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