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WO1997001021A1 - Method and apparatus for generating power from low temperature source - Google Patents

Method and apparatus for generating power from low temperature source Download PDF

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Publication number
WO1997001021A1
WO1997001021A1 PCT/CN1995/000075 CN9500075W WO9701021A1 WO 1997001021 A1 WO1997001021 A1 WO 1997001021A1 CN 9500075 W CN9500075 W CN 9500075W WO 9701021 A1 WO9701021 A1 WO 9701021A1
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Prior art keywords
temperature
liquid
working fluid
gas
heat exchanger
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PCT/CN1995/000075
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French (fr)
Chinese (zh)
Inventor
Zhanman Huo
Yeqin Chen
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KONG DEXING
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KONG DEXING
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Priority to AU34694/95A priority Critical patent/AU3469495A/en
Publication of WO1997001021A1 publication Critical patent/WO1997001021A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/10—Closed cycles
    • 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
    • F01K25/04—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the fluid being in different phases, e.g. foamed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/05—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy

Definitions

  • the invention relates to a method and a device for generating power (shaft work and cooling capacity) by utilizing a temperature difference between the cooling capacity of cryogenic liquid nitrogen (or liquid air) and the low-temperature heat in nature.
  • the liquid nitrogen (or liquid air) leaving the liquid turboexpander has a temperature of 77K and a pressure of 0.1-0.12MPa. It enters the liquid storage tank for 1 cycle use.
  • the flash gas that enters the liquid t tank at the same time as the liquid nitrogen (or liquid air) passes through the refrigeration system 1 1, 1 2, 1 3, 1 4 to be liquefied and returns to the liquid storage tank.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

The invention relates to a method and an apparatus for generating power (shaft output and cool energy) from low temperature source. The apparatus has a system including a heater (3), turbines (4, 5, 9), condenser-evaporator (2), a heat exchanger (22), a condenser (8), a trough for storing liquid (1), a high pressure pump (6), centrifugal pumps (7, 10). The system constructs a continual return circuit together with a deep cooling pipeline system and a flash-vaporization cooling system, wherein said deep cooling working fluid is cycling in said circuit. The working fluid is heated in the heater (3) by low temperature energy of atmosphere air, then the air is cooled. The working fluid is expanded in the turbines (4, 5, 9) to generate shaft output. Vaporous working fluid is expanded and then liquefied to be deep cooling working fluid for recycle use.

Description

低温能源产生动力的方法及装置 本发明的领域  Method and device for generating power from low-temperature energy

本发明涉及利用深冷液氮（或液态空气）的冷量与自然界低温热量 之间的温差来产生动力 （轴功和冷量 的方法及装置。  The invention relates to a method and a device for generating power (shaft work and cooling capacity) by utilizing a temperature difference between the cooling capacity of cryogenic liquid nitrogen (or liquid air) and the low-temperature heat in nature.

本发明的背景  Background of the invention

现有产生动力的方法（例如火力发电） ， 是通过燃料的燃烧发出的 热量， 使水变成蒸汽， 推动汽轮机作功， 带动发电机发电。 从而实现热 能转变为机械能（轴功） ， 然后再转变为电能（或其他动力）的实际过 程。  Existing methods of generating power (such as thermal power generation) use the heat generated by the combustion of fuel to turn water into steam, pushing the turbine to perform work, and driving the generator to generate electricity. In this way, the actual process of converting thermal energy into mechanical energy (shaft work) and then into electrical energy (or other power) is realized.

在产生动力 （例如发电）过程中， 7j蒸汽通过汽轮机作功， 温度急 剧下降， 热量大量消耗， 只有依靠不断提供燃料， 使之燃烧来产生热， 才能保证火力发电的正常运行。 同样在获得低温的冷量过程中， 从系统 取出热量， 需要消耗功， 因此， 冷量的获得应视为动力的消耗。 反之， 冷量的产生， 在一定意义上说， 即为动力的获得。  In the process of generating power (such as power generation), 7j steam works through the turbine, the temperature drops sharply, and a large amount of heat is consumed. Only by continuously supplying fuel and burning it to generate heat can the normal operation of thermal power generation be guaranteed. Also in the process of obtaining low-temperature cooling capacity, removing heat from the system requires work to be consumed. Therefore, the acquisition of cooling capacity should be considered as power consumption. Conversely, the generation of cold energy is, in a sense, the acquisition of power.

本发明概述  Summary of the invention

本发明的目的在于提出一种利用自然界存在的低温热量与深冷液氮 (或液态空气）的冷量之间的温差来产生动力 （轴功和冷量）的方法和 装置， 其中， 深冷液氮（或液态空气）在其连续回路中可循环使用， 以 达到利用自然界低温热能来代替燃料燃烧所产生热能。 本发明的目的可以通过以下措施来达到： 空气加热工质 (液氮或液态 空气)，与此同时空气获得冷量； 工质膨胀作功产生动力 （轴功） ； 工质 冷热换位； 工质通过两相透平膨胀机和液体透平膨胀机再次膨胀产生冷 量输出轴功而形成的系统。 该系统包括： The object of the present invention is to propose a method and a device for generating power (shaft work and cooling capacity) by utilizing a temperature difference between the low-temperature heat existing in nature and the cooling capacity of cryogenic liquid nitrogen (or liquid air). Liquid nitrogen (or liquid air) can be recycled in its continuous loop to achieve the use of low-temperature thermal energy in nature to replace the thermal energy generated by fuel combustion. The object of the present invention can be achieved by the following measures: the air heats the working medium (liquid nitrogen or liquid air), and at the same time the air obtains cooling capacity; the working medium expands to generate work (shaft work); the working medium is cold and hot; The working fluid is a system formed by two-phase turboexpander and liquid turboexpander expanding again to generate cold output shaft work. The system includes:

-由加热器、 透平膨胀机、 冷凝-蒸发换热器、 换热器、 冷凝器、 贮液槽、 高压泵、 深冷管路和闪发气制冷系统等构成一个连续回路； -A continuous loop consisting of heaters, turbine expanders, condensation-evaporation heat exchangers, heat exchangers, condensers, liquid storage tanks, high-pressure pumps, cryogenic pipelines and flash gas refrigeration systems;

-深冷液氮（或液态空气）在所述回路中循环； -Cryogenic liquid nitrogen (or liquid air) circulates in the circuit;

-以自然界的空气为热源， 通过加热器对冷氮气（或冷空气）进行 加热， 使之获得能量， 工质通过冷热换位， 气体透平膨胀机， 两相透平 膨胀机， 液体透平膨胀机对外作功产生轴功并获得冷量而液化， 供循环 使用；  -Using natural air as a heat source, cold nitrogen (or cold air) is heated by a heater to obtain energy, and the working fluid is transposed by cold and heat, gas turbine expander, two-phase turbine expander, liquid turbine The flat expander generates external shaft work and obtains cold energy and liquefies it for circulation use;

-进人贮液槽的闪发气通过制冷系统使之液化返回贮液槽。  -Flash gas entering the liquid storage tank is liquefied by the refrigeration system and returned to the liquid storage tank.

附图简述  Brief description of the drawings

图 1是本发明所用的系统原理图。  FIG. 1 is a schematic diagram of a system used in the present invention.

本发明的实施途径  Implementation method of the present invention

以下结合附图详细说明本发明。  The invention is described in detail below with reference to the drawings.

如图 1所述， 经过净化及干燥装置 19的自然界空气用风机 20通过调 节阀 16将其鼓入加热器 3 , 对来自冷凝 -蒸发换热器 2和换热器 2 2的 高压氮气（或高压空气， 压力 6. 45-7. 45MPa， 温度 190 - 195 K )进行加 热至温度为 2 7 0 - 2 8 0 K , 后将高温高压氮气（或空气）引人气体 透平膨胀机 4， 使其在绝热等熵下膨胀做功， 输出轴功。 与此同时， 通 过加热器 3内的自然界空气被冷却而产生冷量， 可作为各种用途的冷源 使用。 As shown in FIG. 1, the air fan 20 for natural air passing through the purification and drying device 19 blows it into the heater 3 through the regulating valve 16, and applies high-pressure nitrogen gas from the condensation-evaporation heat exchanger 2 and the heat exchanger 22 (or High-pressure air, pressure 6. 45-7. 45 MPa, temperature 190-195 K), heated to a temperature of 2 70-2 8 0 K, and then introduce high temperature and high pressure nitrogen (or air) into the gas turbine expander 4, It is expanded to do work under adiabatic isentropic and output shaft work. At the same time, the natural air in the heater 3 is cooled to generate a cooling capacity, which can be used as a cold source for various purposes. Use.

经绝热等熵膨胀后的氮气 (或空气）， 其压力和温度下降（压力 1.8 - 2.2MPa, 温度 185- 195K) , 然后进人冷凝 -蒸发换热器 2， 氮气（或空 气）在来自常压的贮液槽 1且经高压泵 6, 压至 6.5-7.5 MPa的过冷液氮 After the adiabatic isentropic expansion of nitrogen (or air), its pressure and temperature decrease (pressure 1.8-2.2 MPa, temperature 185-195K), and then enter the condensation-evaporation heat exchanger 2, and the nitrogen (or air) Pressured liquid storage tank 1 and high pressure pump 6 to subcooled liquid nitrogen 6.5-7.5 MPa

(或液化空气） 的冷却下（过冷液体被加热后， 送至换热器 2 2和加热 器 3 ) , 部分冷凝成温度为 116K的两相流体， 将其引人两相透平膨胀机(Or liquefied air) under cooling (the supercooled liquid is heated and sent to heat exchanger 2 2 and heater 3), it is partially condensed into a two-phase fluid with a temperature of 116K, which is introduced into a two-phase turboexpander

5 , 工质膨胀输出轴功， 两相流体获得冷量（温度降至 8 4 - 8 6 K, 压力 0.2- G.25MPa) 。 再将上述两相流体引人冷凝器 8, 将其全部冷凝； 其中冷却液系来自贮液槽 1， 经泵 7加压至 0.8- l. OMPa的过冷液氮（或液 态空气） 。 过冷液氮（或液态空气）在冷凝器 8中被加热至 83 - 85 K, 离 幵冷凝器 8后与冷凝液（经泵 1 0和调节阀 2 1 )合并进人液体透平膨 胀机 9 ,.工质在液体透平膨胀机中膨胀输出轴功， 同时获得冷量。 离开 液体透平膨胀机的液氮（或液态空气）温度为 77K, 压力为 0.1 - 0.12MPa, 进入贮液槽 1循环使用。 与液氮（或液态空气） 同时进入液t 槽内的闪发气则通过制冷系统 1 1， 1 2 , 1 3， 1 4使之液化后返回 贮液槽。 5. The working fluid expands the output shaft work, and the two-phase fluid obtains cold capacity (temperature drops to 8 4-86 K, pressure 0.2- G.25MPa). The two-phase fluid is introduced into the condenser 8 to condense all of it; the cooling liquid is from the liquid storage tank 1 and is pressurized to 0.8-l. OMPa of subcooled liquid nitrogen (or liquid air) by the pump 7. Subcooled liquid nitrogen (or liquid air) is heated to 83-85 K in condenser 8, and after leaving condenser 8, it is combined with the condensate (through pump 10 and regulating valve 21) into the liquid turboexpander. 9. The working fluid expands the output shaft work in the liquid turbine expander and obtains the cooling capacity at the same time. The liquid nitrogen (or liquid air) leaving the liquid turboexpander has a temperature of 77K and a pressure of 0.1-0.12MPa. It enters the liquid storage tank for 1 cycle use. The flash gas that enters the liquid t tank at the same time as the liquid nitrogen (or liquid air) passes through the refrigeration system 1 1, 1 2, 1 3, 1 4 to be liquefied and returns to the liquid storage tank.

整个系统都采用较好的低温绝热材料将其与外界环境隔幵， 以保证 系统的良好运行。  The whole system uses better low-temperature insulation materials to isolate it from the external environment to ensure the good operation of the system.

采用本发明的系统流程及装置所表现特征是： 利用自然界空气低温 热量对深冷气氮（或深冷空气）进行加热， 获得能量， 通过透平膨胀机 对外作功产生轴功， 与此同时， 加热空气被冷却而产生冷量。 达到了利 用自然界的低温热量来代替燃料燃烧所获得的热量以产生动力 （轴功和 冷量） 的目的。 工质通过冷热换位， 透平膨胀使之液化， 以达到其循环 使用。 就效果来说， 当气化 IKg/s的液氮时， 扣除系统内部各种功率消 耗， 系统的净输出轴功率约为 2 0 K W, 同时约可产生 IKg/s温度为 2 0 5 K左右的空气冷量， 可作各种用途的冷源。 The characteristics of the system process and the device adopting the invention are: the low-temperature heat of natural air is used to heat the cryogenic gas nitrogen (or cryogenic air) to obtain energy, and the axial work is generated by the turbine expander to perform external work. At the same time, The heated air is cooled to generate cold energy. Achieved the use of low-temperature heat in nature to replace the heat obtained from fuel combustion to generate power (shaft work and The amount of cold). The working fluid is transposed by cold and heat, and the turbine expands to liquefy it to achieve its recycling. In terms of effect, when IKg / s of liquid nitrogen is gasified, after deducting various power consumptions in the system, the net output shaft power of the system is about 20 KW, and at the same time, the temperature of IKg / s is about 20.5 K The amount of air cooling can be used as a cold source for various purposes.

Claims

权利要求 Rights request 1 . 用自然界空气加热深冷工质来产生动力的方法， 该方法包括以 下步骤： 1. A method for generating power by heating a cryogenic working medium with natural air, the method comprising the following steps: a)用自然界低温热源通过加热器加热来自贮液槽经冷凝 -蒸发换热 器、 换热器的深冷工质使之获得高压、 高温气化工质；  a) Use a low-temperature heat source in nature to heat the condensing-evaporating heat exchanger from the liquid storage tank through the heater to obtain a high-pressure, high-temperature gas chemical; b)将高压高温气化工质输人气体透平膨胀机， 使其在绝热等熵下膨 胀做功；  b) Inject high-pressure and high-temperature gas chemicals into a gas turbine expander to expand and perform work under adiabatic isentropic conditions; c)将经透平膨胀后的气态工质输入冷凝 -蒸发换热器与来自贮液槽 并经加压的深冷工质作热交换， 使其部分冷凝而成为两相流体；  c) The gaseous working fluid that has been expanded by the turbine is input to the condensation-evaporation heat exchanger for heat exchange with the pressurized cryogenic working fluid from the liquid storage tank to partially condense it into a two-phase fluid; d)将两相流体引人两相透平膨胀机， 使工质再次膨胀做功， 同时工 质温度下降；  d) introducing the two-phase fluid into the two-phase turboexpander, so that the working fluid expands again to perform work, and the working fluid temperature decreases; e)将膨胀后的两相流体输人冷凝器与来自贮液槽并经加压的深冷液 态工质作热交换， 使气态工质冷凝， 并将冷凝液和加热后的液态工质一 起进人液体透平膨胀机， 工质在膨胀作功的同时， 温度进一步下降； e) The expanded two-phase fluid is conveyed into the condenser for heat exchange with the pressurized cryogenic liquid working medium from the liquid storage tank to condense the gaseous working medium, and the condensed liquid and the heated liquid working medium together When entering the liquid turbine expander, the working fluid expands and works while the temperature further decreases; D膨胀后的液态工质输人贮液槽， 随液态工质一起进人贮液槽的气 态工质在通过一制冷系统而液化后返回贮液槽。 D The expanded liquid working medium is transported to the liquid storage tank, and the gas working liquid that enters the liquid storage tank with the liquid working fluid is returned to the liquid storage tank after being liquefied through a refrigeration system. 2 . 按照权利要求 1的方法， 其特征在于， 在深冷工质进人加热器 之前先通过冷凝-蒸发换热器， 换热器， 使其与膨胀后的气态工质和进 人制冷系统的闪发气作热交换而气化。 2. The method according to claim 1, characterized in that, before the cryogenic working fluid enters the heater, it is passed through a condensing-evaporating heat exchanger, the heat exchanger, and the expanded working fluid and the expanded gaseous working fluid and entering the refrigeration system. The flash gas is vaporized for heat exchange. 3. 按照权利要求 2的方法， 其特征为， 进入冷凝-蒸发换热器的 过冷液体工质， 其压力为 6.5- 7.5MPa, 温度约为 77K; 离开时温度成为 126- 132K的气态工质； 所进人的膨胀后的气态工质， 其压力为 1.8 -3. The method according to claim 2, characterized in that the pressure of the subcooled liquid working fluid entering the condensing-evaporating heat exchanger is 6.5-7.5MPa, and the temperature is about 77K; when leaving, the gaseous working temperature becomes 126-132K The inflated gaseous working medium that enters has a pressure of 1.8- 2.2 Pa, 温度为 185 - 195K， 离开时为约 1 1 6 Κ的两相流体。 2.2 Pa, a two-phase fluid with a temperature of 185-195K and about 1 1 6 K when leaving. 4. 按照权利要求 1的方法， 其特征是， 进人加热器的气态工质压力 为 6.45 - 7.45MPa, 温度为 1 9 0- 1 9 5 K, 离幵时的温度为 2 7 0 - 4. The method according to claim 1, characterized in that the pressure of the gaseous working medium entering the heater is 6.45-7.45 MPa, the temperature is 19 0-1 9 5 K, and the temperature at the time of leaving is 2 7 0- 2 8 0 K;而流人的自然界空气的温度为 2 9 3 - 2 9 8 K, 离幵时的温度 为 2 0 0 - 2 0 5 K。 2 8 0 K; and the temperature of the flowing natural air is 2 9 3-2 9 8 K, and the temperature at the time of leaving is 2 0-2 0 5 K. 5. 按照权利要求 1所述的方法， 其特征在于， 流人冷凝器的液态 工质压力为 0 · 8 - 1. 0 M P a , 温度约为 7 7 K , 离幵时的温度为 83 -85K, 而流人冷凝器的两相流体温度为 8 4 - 8 6 K, 离开时为该温度 下的冷凝液。  5. The method according to claim 1, characterized in that the pressure of the liquid working medium flowing into the condenser is 0. 8-1. 0 MP a, the temperature is about 7 7 K, and the temperature at the time of leaving is 83- 85K, and the temperature of the two-phase fluid flowing into the condenser is 8 4-8 6 K, and it leaves the condensate at this temperature. 6. 用于实施权利要求 1所述方法的装置， 其特征在于， 该装置是 一个由贮液槽（ 1 )加热器（ 3 ) 、 气体透平膨胀机（ 4 ) 、 两相透平 膨胀机（ 5 ) 、 液体透平膨胀机（ 9 ) 、 冷凝一蒸发换热器（ 2 ) 、 换热 器（ 22 ) 、 冷凝器（ 8 ) 、 闪发气制冷系统（ 1 1， 1 2 , 1 3 , 1 4 ) 和泵（ 6 , 7 , 1 0 ) 以及深冷管路构成的循环系统。  6. Device for implementing the method according to claim 1, characterized in that the device is a liquid storage tank (1) heater (3), a gas turbine expander (4), a two-phase turbine expander (5), liquid turbine expander (9), condensation-evaporation heat exchanger (2), heat exchanger (22), condenser (8), flash gas refrigeration system (1 1, 1, 2, 1 3 , 1 4) and pump (6, 7, 10) and the circulation system composed of cryogenic pipelines. 7. 按照权利要求 3所述的装置， 其特征在于， 冷凝 -蒸发换热器 ( 2 )是低温工况下的板翅式换热器， 其有两个人口和两个出口， 一个 人口安来自贮液槽的管路， 另一人口用于进人经气体膨胀机膨胀后的气 态工质； 两个出口中之一是通换热器， 另一是通向两相膨胀机。  The device according to claim 3, characterized in that the condensing-evaporating heat exchanger (2) is a plate-fin heat exchanger under low temperature conditions, which has two populations and two outlets, and one population is safe. From the pipeline of the liquid storage tank, another population is used to enter the gaseous working fluid expanded by the gas expander; one of the two outlets is a heat exchanger, and the other is a two-phase expander. 8. 按照权利要求 4所述的装置， 其特征在于， 加热器是板翅式换 热器。 8. The device according to claim 4, wherein the heater is a plate-fin type Heater. 9. 按照权利要求 5所述的装置， 其特征在于， 冷凝器（ 8 )是低 温工况条件下工作的板翅式换热器， 其有两个人口， 其一通人来自贮流 槽并经离心泵（ 7 )加压的深冷液态工质， 另一人口通人经两相膨胀机 膨胀后的两相流体； 还有两个出口， 其一是输出冷凝液， 另一是输出被 加热的液态工质。  9. The device according to claim 5, characterized in that the condenser (8) is a plate-fin heat exchanger working under low-temperature conditions, and has two populations, one of which comes from a storage tank and passes through it. A centrifugal pump (7) pressurized cryogenic liquid working medium, the other is a two-phase fluid expanded by a two-phase expander; there are two outlets, one of which outputs condensate, and the other is heated. Liquid working fluid. 1 0. 按照权利要求 6所述的装置， 其特征在于， 透平膨胀机是低 温工况条件下的膨胀机， 它们分别是气体透平膨胀机 4 , 两相（气、 液）透平膨胀机 5及液体透平膨胀机 9。 进人气体透平膨胀机的气体工 质压力 6.4- 7.4MPa, 温度为 270 - 280K , 离开时压力 1. 8 - 2. 2 MPa, 温度 185- 195K; 进人两相（气、 液）透平膨胀机的工质压力 1.8 - 2.2MPa, 温度 1 1 6 K的两相流体。 离开时压力 0 · 2 - 0. 2 5 MPa, 温 度 8 4 - 8 6 K的两相流体； 进人液体透平膨胀机的工质为 0.8- 1. 0 MPa, 温度 83-85 K的过冷液氮（或液态空气） ， 离开时压力 0.1-0.12 MPa, 温度 7 7 K的液氮（或液态空气）及闪发气体。  10. The device according to claim 6, characterized in that the turboexpander is an expander under low-temperature operating conditions, and they are respectively a gas turboexpander 4 and a two-phase (gas, liquid) turbine expansion机 5 and Liquid turbine expander 9. The gas working medium pressure entering the gas turbine expander is 6.4-7.4MPa, the temperature is 270-280K, the pressure when leaving is 1.8-2.2 MPa, the temperature is 185-195K; entering the two-phase (gas, liquid) permeability Two-phase fluid with a flat working expander working pressure of 1.8-2.2MPa and a temperature of 1 16 K. Two-phase fluid with a pressure of 0 · 2-0. 2 5 MPa and a temperature of 8 4-8 6 K when leaving; the working fluid entering a liquid turboexpander is 0.8- 1. 0 MPa and a temperature of 83-85 K Cold liquid nitrogen (or liquid air), liquid nitrogen (or liquid air) and flash gas with a pressure of 0.1-0.12 MPa and a temperature of 7 7 K when leaving.
PCT/CN1995/000075 1995-06-23 1995-09-14 Method and apparatus for generating power from low temperature source Ceased WO1997001021A1 (en)

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FR2762873A1 (en) * 1997-05-02 1998-11-06 Andre Charasse Thermal engine utilising latent energy
CN111456823A (en) * 2020-05-19 2020-07-28 宝莲华新能源技术（上海）股份有限公司 Low-temperature cold source expansion power generation device
CN115030792A (en) * 2022-05-10 2022-09-09 昆明理工大学 A medium and low temperature flue gas dewhitening and waste heat ORC power generation and water resource recovery system

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CN1181461A (en) * 1997-10-27 1998-05-13 易元明 Negative temp. differential saturated steam engine
CN1180790A (en) * 1997-10-27 1998-05-06 天然国际新科学技术研究院 Negative temperature difference heat engine
CN101709659A (en) * 2009-09-14 2010-05-19 刘福军 Process for improving efficiency of steam turbine by adopting liquid air as cooling medium

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FR2762873A1 (en) * 1997-05-02 1998-11-06 Andre Charasse Thermal engine utilising latent energy
CN111456823A (en) * 2020-05-19 2020-07-28 宝莲华新能源技术（上海）股份有限公司 Low-temperature cold source expansion power generation device
CN115030792A (en) * 2022-05-10 2022-09-09 昆明理工大学 A medium and low temperature flue gas dewhitening and waste heat ORC power generation and water resource recovery system

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