WO1997013961A1 - Systeme generateur d'energie utilisant un fluide - Google Patents

Systeme generateur d'energie utilisant un fluide Download PDF

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Publication number
WO1997013961A1
WO1997013961A1 PCT/KR1996/000171 KR9600171W WO9713961A1 WO 1997013961 A1 WO1997013961 A1 WO 1997013961A1 KR 9600171 W KR9600171 W KR 9600171W WO 9713961 A1 WO9713961 A1 WO 9713961A1
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WO
WIPO (PCT)
Prior art keywords
working fluid
heat
turbine
temperature
fluid
Prior art date
Application number
PCT/KR1996/000171
Other languages
English (en)
Inventor
Jae Hwan Kim
Original Assignee
Jae Hwan Kim
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1019960001844A external-priority patent/KR970021723A/ko
Application filed by Jae Hwan Kim filed Critical Jae Hwan Kim
Priority to EP96935550A priority Critical patent/EP0858552A1/fr
Priority to AU73404/96A priority patent/AU7340496A/en
Priority to JP9514929A priority patent/JP2000509122A/ja
Publication of WO1997013961A1 publication Critical patent/WO1997013961A1/fr

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Classifications

    • 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
    • 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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant circuit

Definitions

  • This invention relates to a power generating system comprising a turbine system and a refrigerating system, wherein the power is obtained by use of the heat from an external fluid in the normal temperature.
  • Conventional power generating systems are directed to obtain motive power or electric power from the heat generated in the course of combustion of fuel, so that the conventional systems have disadvantages that the fuel expense is high and they cause air pollution due to the combustion of fuel.
  • Fig. 1 is a schematic view showing the construction of a power generating system according to the present invention
  • Fig. 2 is a schematic view showing the power generating system according to an embodiment of the present invention
  • Fig. 3 is a schematic view showing the power generating system according to another embodiment of the present invention.
  • Fig. 4 is a schematic view showing the power generating system according to a third embodiment of the present invention.
  • Fig. 5 is a schematic view showing an antifreezing solution evaporation means.
  • Fig. 6 is a schematic view showing another antifreezing solution evaporation means.
  • Fig. 7 is a cross sectional view showing the construction of an evaporation means in Figs. 4 and 5.
  • the power generating system by use of fluid includes an electric motor 1 rotatable by an external electric power supply.
  • the rotational force of the electric motor 8 drives a compression means 30 installed in a coolant circulating circuit of a first refrigerating system 30 to 36 filled with coolant.
  • working fluid in a heat exchanger 12 is cooled and liquefied by an endothermic part 36 of the coolant circulating circuit and the pressure of the working fluid decreases inside the heat exchanger 12 and a flowing tube 10 at the outlet of a turbine 1.
  • the working fluid in closed flowing tubes 10 to 20 moves from a higher pressured part 20 to a lower pressured part 10, and the removing force of the working fluid drives the turbine 1.
  • the rotational force of a rotational axis 7 connecting the electric motor 8 and the turbine 1 drives a compression means
  • the first refrigerating system 30 to 36 which constitutes a separate coolant circulating circuit
  • second and third refrigerating systems 40 to 45 and 50 to 55 and a heat exchanger 60 which absorbs heat from the external fluid.
  • the liquefied working fluid is removed to flowing tubes
  • Heat exchangers 11 and 15 and valves 73 and 76 which stand in a line in Fig.l are used in another embodiment.
  • the flowing tubes 177, 179, 182, 183, 185, 187 and 188, and the valves 178, 180, 181, 184 and 186 which stand in a line are used in other conditions.
  • Flowing tubes in a dotted area of Fig.l may be neglected in this embodiment.
  • the working fluid is heated in an exothermic part 34 of the first refrigerating system 30 to 36 and an exothermic part 45 of the second refrigerating system 45.
  • the fluid is further heated by the external fluid in the heat exchanger 60 through which the external fluid, e.g., air passes. Then, the working fluid is finally heated in an exothermic part 53 of the third refrigerating system 50 to 55 and enters the turbine 1.
  • the third refrigerating system is to absorb heat from the external fluid in the normal temperature and to heat the working fluid in the boiler 19.
  • Heat media like Freon R14, R13, carbon dioxide, ethane and ethylene which are in a gaseous state over a critical temperature in the normal temperature, or substances and their mixtures which have similar properties to the heat media may be used as the working fluid. Further, synthesized substances suitable for the system can be utilized. The temperature of the working fluid becomes higher than the critical temperature while flowing through the turbine 1, and at the outlet of the turbine the working fluid is discharged at the critical temperature or the temperatures a little below or above the critical temperature.
  • the working fluid should have lower temperature than the critical one and higher pressure than the saturated one to be liquefied. Accordingly, the working fluid at the outlet of the turbine 1 is liquefied in a condenser 12 as its temperature decreases by the endothermic part 36 of the first refrigerating system. However, since the latent heat, i.e., the heat of liquefaction is not large at temperatures below the critical temperature, the amount of heat absorbed by the endothermic part 36 of the first refrigerating system 30 to 36 is not large.
  • the working fluid is heated in turn by the exothermic part 34 of the first refrigerating system, the exothermic part 45 of the second refrigerating system, and then a flowing tube
  • the working fluid is further heated in the heat exchanger 19 including the flowing tube of the exothermic part 53 of the third refrigerating system, and the temperature of the fluid increases.
  • the power generated in the turbine 1 is larger than the power which drives the compression means 13 of the working fluid, the first to third refrigerating systems and a fluid transporter 61 of the heat exchanger. Therefore, after the first drive of an electric motor 8 by external electric power supply, self-generated power drives the system spontaneously, though the external electric power supply has been suspended when a stationery state is established, and extra self-generated power keeps a generator 9 driving, thus giving electric power.
  • the work in Carnot cycle may comprise four steps, and the work obtained through isothermal expansion and adiabatic expansion may be the work done by the turbine. In this procedure, a heat source in high temperature is necessary to converse the thermal energy of gas into power as much as possible.
  • the pressure in the boiler can be freely controlled regardless of the temperature.
  • the high pressure of the boiler can be achieved though the temperature in the boiler is not high, since the working fluid is not liquefied even when the pressures is high at temperatures above the critical temperature.
  • a difference in pressure between the boiler and the condenser can be large though a difference in temperature between them is not large.
  • a difference of saturated vapor pressure is larger than the temperature difference.
  • the working fluid in a lower-pressured part(condenser) has large difference in density during the liquefaction, so that the power consumed by the compression means or pump is very little compared to the power obtained by the turbine, though the pressure difference between the lower-pressured and higher-pressured parts is large.
  • the work done by the turbine is the work done in the adiabatic procedure and the efficiency increases according the pressure ratio
  • the work done by the refrigerator reduces the amount of heat which is transferred by the power according to the temperature difference (reversed Carnot cycle). Accordingly, in the condition of the present invention, that is, in the condition that the pressure difference is much smaller than the temperature difference, the power that the turbine obtains can be larger than the power from the refrigerator.
  • the power the turbine obtains and its efficiency are low when the temperature difference between the higher temperature part (the boiler) and the lower temperature part (the condenser) is too small.
  • a temperature difference larger than a certain degree has to be guaranteed to drive the system of the present invention, since the temperature difference is required for the exchange of heat in the heat exchanger and since it is difficult to liquefy the fluid when the difference between the critical temperature and the liquefaction temperature (the temperature of the working fluid in the condenser) is too small, and accordingly the temperature for liquefaction should be lowered below some limit point.
  • the work done by the refrigerator to increase the temperature is proportional to the temperature difference, so that the power obtained by the turbine can be larger than the work done by the refrigerator. Therefore, the heat of liquefaction is eliminated by the refrigerating system, and also the external fluid like air to be supplied to the boiler has the temperature raised by the third refrigerating system 50 to 55.
  • the system of the present invention can be preferably utilized in various transportation means.
  • the third refrigerating system is driven.
  • the power transferring/discontinuing means 6a and 6b which are installed on a rotational axis 7 together with the coolant compression means 50 can be driven to discontinue the power so that the system may be driven without the operation of the third refrigerating system.
  • a flowing tube 172 and a valve 171 are therefore installed to be used as needed so that the working fluid may not pass through the heat exchanger 19.
  • the flowing tubes 177 and 179 and the valves 178 and 180 can be installed in a line with the exothermic parts 33 and 34 to be alternatively used according to the properties of the working fluid and the temperature of the external fluid.
  • the flowing tubes 182 and 183 and the valve 181 can be arranged in a line, and a heat exchanger (not shown) can be installed to be connected with the flowing tubes 182 and 183.
  • the unshown heat exchanger can have the same structure as the heat exchanger 60 without the antifreezing solution circulating circuit, or can be installed additionally to the heat exchanger 60.
  • the temperature of the working fluid decreases in the heat exchanger 11 and the fluid is condensed in the condenser 12. Then, the temperature of the fluid increases again in the heat exchanger. Accordingly, since the temperature difference of the working fluid from the critical temperature is small, it is more preferable that the exothermic part discharges heat to the external fluid rather than that the working fluid exchanges heat with the external fluid, when the external temperature is lower than the critical temperature.
  • the flowing tubes 182 and 183 standing in a line are connected with the heat exchanger through which the external fluid passes to discharge heat to the external fluid. Also, when the external fluid has substantially the same temperature as the critical one, it is preferable that the working fluid exchanges heat with the external fluid in the heat exchanger.
  • the second refrigerating system 40 to 45 does not have to be worked.
  • the temperature at the exothermic part of the first refrigerating system may be lower than the critical one. Then, the heat exchanger 43 is operated to exchange heat with the second refrigerating system, and the heat exchanger 16 and the flowing tubes 182 and 183 through which the working fluid exchanges heat with the extemal fluid are closed.
  • the flowing tubes 187 and 188 which stand in a line are connected to a heat exchanger (having the same structure as the heat exchanger 60) and include the valve 186 to discharge heat of the working fluid to the external fluid.
  • a valve and a flowing tube are arranged in a line with only one flowing tube of a heat exchanger, and another valve and another tube can be arranged in a line with the other flowing tube, so that the loss due to the abrasion may not be caused by the flow of the fluid through a non-operating heat exchanger (see 173 to 176 in Fig.l).
  • the above alternative operation can be applied in the second to
  • the system where the working fluid is heated by steps in the exothermic parts 34 and 45 of the first and second refrigerating systems, the heat exchanger 60 absorbing heat from the extemal fluid and the third refrigerating system reduces the power consumed by the refrigerating systems, thus increasing the efficiency of the system.
  • the working fluid is heated by the exchange of heat with the fluid at the outlet 10 of the turbine in the heat exchanger
  • the first refrigerating system eliminates the heat of liquefaction of the working fluid in the condenser 12, to heat the endothermic part 43 of the second refrigerating system and then to heat the working fluid in the exothermic part 34.
  • the second refrigerating system 40 to 45 obtains the heat from the first refrigerating system to heat the working fluid.
  • the working fluid absorbs heat only from the third refrigerating system rather than from the heat exchanger 60 and the exothermic part 53 of the third refrigerating system, the total amount of heat absorbed by step by the heat
  • the procedure of thermal transmission between the first and second refrigerating systems is as follows.
  • the exothermic part 33 of the first refrigerating system heats the endothermic part 43 of the second refrigerating system with the half amount of heat and then heats the working fluid at the exothermic part 34. Only half amount of the heat is transmitted to the second refrigerating system, which transmits only the half amount of heat to the working fluid, thus reducing the power consumption.
  • a heat exchanger 11 where the fluids flowing in opposite directions exchange heat is installed in the flowing tube at the outlet 10 of the turbine.
  • the pressure at the outlet 10 of the turbine is much lower than the critical one and the temperature is as high as the critical temperature
  • the working fluid from the outlet of the compression pump 13 exchanges heat with the working fluid at the outlet 10 of the turbine.
  • the working fluid at the outlet 10 of the turbine is cooled while the working fluid from the compression pump 13 is heated to increase the temperature. Therefore, the turbine can obtain large amount of power due to its large pressure ratio, and the turbine works at temperatures above the critical temperature, thus obtaining the higher efficiency than that of the working fluid in a vapor state.
  • the power consumption can be reduced since the working fluid in a high temperature but in a low pressure is discharged from the outlet 10 of the turbine and the working fluids flowing in opposite directions exchange heat mutually.
  • the mutual exchange of heat reduces the power to decrease the temperature by the endothermic part 35 of the refrigerating system.
  • thermoelectric heat exchanger where the fluids having a little difference in temperature exchange heat efficiently, e.g., the heat exchanger having high heat conductivity, high purity, large surface area and thin thickness. High efficiency can be obtained when using a heat exchanger manufactured of superconductor.
  • an automatic voltage controller can be installed at the output of the generator 9 to maintain the output voltage constant.
  • the heat exchanger 60 through which the extemal fluid passes can be used as a refrigerator or an air conditioner.
  • heat exchanger 60 is used as the air conditioner
  • indirect heating method wherein a heat medium absorbs heat from the extemal fluid in the heat exchanger 60 to heat the working fluid may be adopted.
  • the flowing tube of the endothermic part 110 at one part of the heat exchanger 60 is connected to an antifreezing solution evaporation means 300 as shown in Fig.5 and flowing tubes 111 and 112 to heat the antifreezing solution in operation.
  • an antifreezing solution flows down from a nozzle 62 at the upper part of the heat exchanger, and is diluted with the moisture in the air, to prevent freezing.
  • the moisture in the air may be frozen, thereby reducing the efficiency of the heat exchanger and causing suspension of operation.
  • the antifreezing solution is evaporated and concentrated while flowing through an evaporation means 310 in a low pressure, and the evaporated antifreezing solution is removed to the upper part 62 of the heat exchanger 60.
  • the antifreezing solution at the lower part 63 of the heat exchanger 60 is removed to the evaporation means 310 to be concentrated and then retumed to the upper part 62.
  • the flowing tube 110 of the heat exchanger 60 is an endothermic part of the refrigerating system constituting a separate coolant circulating circuit.
  • the coolant is removed to the evaporation means 310 by a compression means 312 and heats the antifreezing solution while flowing through a flowing tube 320 installed in a path 370 inside the evaporation means. That is, the coolant supplements the heat of evaporation.
  • the refrigerating systems 312, 320, 316 and 250 absorb heat from the extemal fluid and heat the antifreezing solution when the extemal temperature is very low.
  • the compression means 312 works only as a fluid transporter and a separate flowing tube 318 and valves 380 and 381 are arranged in a line with the flowing tube passing the expansion valve 316, so that the fluid may flow into the flowing tube 318 to supply the heat absorbed from the external fluid to the antifreezing solution without the increase of the temperature.
  • the evaporation means 310 includes a vacuum pump 313 to evacuate the gas at the upper space.
  • the antifreezing solutions to be discharged from and to enter the evaporation means 310 flow in opposite directions in a heat exchanger 314 and exchange heat each other. That is, the antifreezing solution which has been heated in the evaporation means heat the solution toward the evaporation means. Further, the antifreezing solution which has been heated in the above heat exchanger 314 exchange heat with the vapor discharged from the vacuum pump 313 in a heat exchanger 315 to be further heated, thus entering the evaporation means 310.
  • the heat exchanger 314 can be excluded.
  • the antifreezing solution is removed to the flowing tube 62 at the upper part of the heat exchanger 60 by means of a circulation pump 311, and the antifreezing solution which stagnates in the lower part 63 is absorbed by the absorption force since the intemal pressure of the evaporation means 310 is low. Therefore, a flux control valve 360 is installed to control the flux, and a water level sensor 330 is installed inside the evaporation means. The flux is automatically controlled through the valve 360 according to signals of the water level sensor 330 to maintain the level inside the evaporation means constant.
  • Fig. 7 is a sectional view showing the intemal paths of the evaporation means, wherein a flowing tube 320 of the refrigerating system is installed in a curved path 370, and the coolant and the antifreezing solution exchange heat mutually while flowing in opposite directions through the flowing tube
  • the intemal path 370 of the evaporation means 310 is filled with sand, primarily heated earth and rocks, soil, fibers and so on, and the lower part of the path 370 is filled with relatively larger particles and the upper part is filled with relatively smaller particles, so that the antifreezing solution may flow through the larger particles in the lower part to be effectively evaporated.
  • Fig. 6 shows another embodiment of the antifreezing solution evaporation means wherein the external fluid passes rapidly by means of a blower 350 and the internal pressure of the evaporation means 310 is reduced by the vacuum pump.
  • FIG. 2 shows a third embodiment of the present invention wherein turbines 1 to 5 has multiple- stepped reheating and regenerating turbine systems.
  • the refrigerating systems 30 to 35 and 40 to 45 are installed in a two- stepped structure to liquefy the working fluid in a lower-pressured part at the outlet 82 of the turbine 5.
  • the third refrigerating system are arranged in a line to heat the working fluid flowing into the respective reheating turbines.
  • the working fluid at the outlet 82 of the turbine is cooled and liquefied by the exothermic part 35 of the first refrigerating system 30 to 35, and then removed to the higher-pressured part by means of the compression pump 13.
  • the exothermic part 33 of the first refrigerating system heats the endothermic part 43 of the second refrigerating system 40 to 45.
  • the working fluid in the second refrigerating system 40 to 45 absorbs heat from the exothermic part 33 of the first refrigerating system to be evaporated, and then heats the working fluid 105 in the exothermic part 45 to be liquefied.
  • the third refrigerating system 50to55 are arranged to heat the working fluid in the boiler in the same way as in the first and second embodiments, but further includes reheating and regenerating turbines which are provided with additional heat exchanger and regenerating pump.
  • Exothermic parts 53, 54 and 55 of the third refrigerating system are in a line to reheat the working fluid which is heated first by the external fluid in the heat exchanger 60 before entering the respective turbines of the reheating turbine system 1 to 3.
  • part of the working fluid is derived from the respective turbines to be removed to the heat exchangers 76 and 81, where the working fluid exchanges heat with the working fluid in a liquid state which has been removed by the compression pump 13 to be liquefied and joined together.
  • the working fluid at the outlet of a last- step turbine 82 is removed to an outlet 14 after being liquefied in the condenser 87 and compressed with high pressure by means of the compression pump 13. Then the fluid is liquefied while exchanging heat with the working fluid discharged from the outlet 80 of the second- step turbine 4 of the regenerating turbine system.
  • the liquefied working fluid joins the working fluid removed by a pump 101 and liquefied again while exchanging heat with the working fluid discharged from the outlet 75 of the turbine 3, so as to join together by the pump 102 in the same manner.
  • the working fluid is heated in the exothermic part
  • the temperature of the working fluid is preferable to be higher than the critical temperature so as to gasify the working fluid after being heated in the boiler 67 and the boilers 71 and 86 of the reheating turbine system (at least 30
  • C or higher than the critical temperature the temperature of the working fluid lower than the critical temperature from the outlet 75 of the first- step turbine 3 of the regenerating turbine system and to maintain the difference between the temperature at the outlet 75 and the saturation temperature small.
  • the temperature and the pressure of the working fluid at the outlet of the turbine 82 is preferably lowered. If the pressure difference between the inlet of the turbine 68 and the condenser (lower-pressured part) is very large and, particularly, the pressure ratio is large, more power may be obtained by the turbine.
  • the temperature and the pressure of the working fluid at the outlet of the turbine 82 are to be lowered but not to be saturated, and the temperature at the condenser 87 is lowered slightly more so as to cool and liquefy the working fluid.
  • the heat of liquefaction is high since the temperature is low, and the heat more than the heat of liquefaction may be eliminated since the temperature is lowered by the condenser.
  • the pressure ratio between the higher-pressured part and the lower-pressured part is very large, since the pressure difference between the boiler and the condenser is large and the absolute pressure at the outlet of the turbine 82 is very low.
  • the ratio of the saturated pressure to the temperature ratio becomes larger. For example, comparing a saturated pressure Al at a temperature A with a saturated pressure Bl at a temperature B which is lower than the temperature A, the ratio of the saturated pressure (Al-Bl) is larger than the temperature ratio (A-B) and this difference becomes even larger under the boiling point, so that the efficiency of the turbines greatly increases.
  • the pressure of the working fluid at the inlet 74 is to be kept low since the efficiency at the reheating turbine system decreases if the pressure of the working fluid at the inlet 74 of the turbines in the regenerating turbine system 3 to 5 increases.
  • the pressure at the outlet of the turbine 82 is lower than that of the inlet 74 and the pressure ratio between these two points 74 and 82 is large, so that the pressure difference in the reheating turbine system is also large to have enough efficiency.
  • the efficiency of the turbines in the regenerating turbine system 3 to 5 is not so low, since the pressure difference is larger than the temperature difference in the regenerating turbine system. Therefore, it is preferable to use substances having a low critical temperature and a high liquefaction point (boiling point) as the working fluid to obtain high efficiency.
  • Fig. 3 is a view showing a fourth embodiment of this invention wherein the power generating system by use of fluid comprises a reheating turbine system without the regenerating system.
  • the working fluid at the outlet of the last- step turbine 90 exchanges heat with the working fluid in a liquid state which is removed from the compression pump 13 in the heat exchangers 91 and 94, to be supplied to the condenser 92 after being cooled.
  • a flowing tube 173 and an opening valve 176 arranged in a line with the heat exchanger 91 are adopted not to operate the heat exchanger 91 in the fifth embodiment.
  • the heat exchanger 91 replaces the turbines in the regenerating turbine system and the heat exchanger.
  • the pressure of the working fluid may be greatly lowered and the temperature may be maintained substantially same as the critical temperature. Then the working fluid is cooled in the heat exchanger 91 and further cooled in the condenser 92 to be liquefied. Therefore, the pressure ratio between the higher- pressured part (the boiler) and the lower-pressured part (the condenser) is very large and the temperature at the turbines 1 to 3 is maintained higher than the critical temperature, so that the efficiency of the turbine is improved.
  • the working fluids exchange heat each other to be cooled by the mutual heat exchanger 91 without the interaction between the turbines of the regenerating turbine system and the heat exchangers of the regenerating turbine system, thereby simplifying the structure.
  • the flowing tube 173 and the valve 176 are installed in a line with the heat exchanger 91 to prevent the working fluid from entering the heat exchanger 91 and to make the temperature and the pressure of the working fluid at the outlet of the turbine 90 substantially the same as the critical temperature and the critical pressure, so as to liquefy the working fluid at temperatures slightly below the critical temperature in the condenser 92. Therefore, the liquefaction heat to be eliminated by the refrigerating systems 130 to 136 and 40 to 45 is reduced as in the first embodiment.
  • Fig. 4 is a view showing the sixth embodiment of this invention, wherein the turbines 1 and 2 constitute a two-stepped reheating turbine system.
  • the refrigerating systems 190 to 198 and 140 to 146 to heat the working fluid in the boiler comprise two steps rather than one step system to cool the working fluid in the condenser 157.
  • the 155 is cooled while exchanging heat with the working fluid in a liquid state which has been removed by the compression pump 13 and is liquefied by the endothermic part 236 of the first refrigerating system 230 to 236.
  • the working fluid increases in temperature while exchanging heat mutually in the heat exchanger 156 and is heated by the exothermic part 233 of the first refrigerating system and then by the extemal fluid in the heat exchanger 60.
  • the working fluid After being heated by the exothermic part 194 of the second refrigerating system 190 to 198 and the exothermic part 143 of the third refrigerating system 140 to 146 by step, the working fluid enters the turbine 1.
  • the fluid obtains power from the first- step turbine and is discharged at the outlet 151.
  • the working fluid is reheated by the exothermic parts 154 and 144 of the second and third refrigerating systems and enters the second-step turbine 2.
  • the exothermic parts 143, 194, 143, 195 and 144 are connected in serial or in parallel with each other to heat the working fluid sequentially, wherein the first exothermic part 193 of the second refrigerating system 190 to 198 heats the endothermic part 146 of the third refrigerating system firstly and then heats the working fluid secondly and thirdly.
  • the third refrigerating system 140 to 146 absorbs only half of the amount of the heat from the second refrigerating system and after raising its temperature provides the working fluid with the heat, so that the power consumption by the third refrigerating system decreases by half comparing with the conditions that the second refrigerating system transmits all the heat to the third refrigerating system and the third refrigerating system transmits all the heat to the working fluid.
  • the power consumption of the refrigerating system decreases as much as the extemal fluid can supply the heat to the working fluid in the heat exchanger 60, and the power consumption of the exothermic part 233 of the first refrigerating system may also decrease in the same way. Therefore, even though the refrigerating systems 190 to
  • the refrigerating systems to heat the boiler in the first to fifth embodiments may also be formed in the two- stepped structure as in the sixth embodiment.
  • the refrigerating system 230 to 236 to cool the working fluid of the condenser may also have the two-stepped structure and can be manufactured simply depending on various uses. In other words, it is possible to vary the stmcture of the refrigerating system according to the appliance and operation conditions, for example, the refrigerating system may have only one- stepped structure and the refrigerating system for heating the working fluid in the boiler may be omitted if the working fluid enters the turbine directly after absorbing heat from the extemal fluid in the heat exchanger 60.

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  • General Engineering & Computer Science (AREA)
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Abstract

Cette invention concerne un système générateur d'énergie et utilisant un fluide, lequel système comprend un système de turbine et un système de réfrigération permettant de générer de l'énergie au moyen de celle du fluide à température ambiante et sans quelque carburant que ce soit, ce qui permet de réduire la pollution de l'air résultant de la combustion de ces derniers. La réfrigération et la liquéfaction dans le condensateur (12) d'un système de turbine à étages multiples, se font à l'aide d'un échangeur de chaleur situé dans une partie endothermique d'un système de réfrigération, ce dernier constituant un circuit de circulation d'agent de refroidissement. Un dispositif d'actionnement du système de réfrigération est installé de manière à fournir de l'énergie en commun avec l'axe rotatif du système de turbine. Cet axe rotatif (7) comporte un moteur électrique (8) actionné par une source d'alimentation électrique externe. Le fluide de travail situé dans une chaudière du système de turbine, échange de la chaleur avec le fluide externe à température ambiante et avec la partie exothermique du système de réfrigération devant être chauffée, ceci jusqu'à ce que le fluide de travail de la chaudière se trouve en phase gazeuse au dessus de la température critique. La pression de la chaudière est augmentée de sorte qu'une petite quantité de chaleur de liquéfaction soit produite et que le fluide de travail dans le condensateur puisse être liquéfié à des températures situées légèrement en-dessous de la température critique, la chaleur produite par la liquéfaction du fluide de travail dans le condensateur restant ainsi à un faible niveau.
PCT/KR1996/000171 1995-10-07 1996-10-07 Systeme generateur d'energie utilisant un fluide WO1997013961A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96935550A EP0858552A1 (fr) 1995-10-07 1996-10-07 Systeme generateur d'energie utilisant un fluide
AU73404/96A AU7340496A (en) 1995-10-07 1996-10-07 Power generating system by use of fluid
JP9514929A JP2000509122A (ja) 1995-10-07 1996-10-07 流体を利用した動力発生システム

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR19950034407 1995-10-07
KR1995/34407 1995-10-07
KR1019960001844A KR970021723A (ko) 1995-10-07 1996-01-29 유체를 이용한 동력발생장치
KR1996/01844 1996-01-29

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000029737A1 (fr) * 1998-11-12 2000-05-25 Yuanming Yi Moteur aeronautique thermique a difference negative de temperature
WO2000071944A1 (fr) * 1999-05-20 2000-11-30 Thermal Energy Accumulator Products Pty Ltd Moteur thermo-volumetrique semi-autonome
GB2447448A (en) * 2007-03-12 2008-09-17 Raymond Trefor William Lloyd Hydro-electric and hydro-thermal system
WO2008124868A1 (fr) * 2007-04-13 2008-10-23 Renewable Energy Systems Limited Procédés et systèmes de production d'énergie et de récupération d'énergie
GR20080100635A (el) * 2008-10-01 2010-05-13 Παυλος Μανωλουδης Μεθοδος και συσκευη "θερμικης μετατροπης ψυχρης δεξαμενης κλειστου ενεργειακου κυκλου"
CN102162397A (zh) * 2011-01-13 2011-08-24 绍兴文理学院 压水堆核动力燃汽轮机循环发电系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103696818B (zh) * 2012-12-31 2017-01-25 摩尔动力(北京)技术股份有限公司 一种高充压热力学循环系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2101690A (en) * 1981-07-10 1983-01-19 John Daniel Lynch Cooling spent vapour from the turbines of a power station installation
GB2102889A (en) * 1981-08-07 1983-02-09 Ormat Turbines Power plant utilizing multi-stage turbines
US5014518A (en) * 1989-06-23 1991-05-14 Allied-Signal Inc. ECS with advanced air cycle machine
US5431016A (en) * 1993-08-16 1995-07-11 Loral Vought Systems Corp. High efficiency power generation

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2101690A (en) * 1981-07-10 1983-01-19 John Daniel Lynch Cooling spent vapour from the turbines of a power station installation
GB2102889A (en) * 1981-08-07 1983-02-09 Ormat Turbines Power plant utilizing multi-stage turbines
US5014518A (en) * 1989-06-23 1991-05-14 Allied-Signal Inc. ECS with advanced air cycle machine
US5431016A (en) * 1993-08-16 1995-07-11 Loral Vought Systems Corp. High efficiency power generation

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000029737A1 (fr) * 1998-11-12 2000-05-25 Yuanming Yi Moteur aeronautique thermique a difference negative de temperature
WO2000071944A1 (fr) * 1999-05-20 2000-11-30 Thermal Energy Accumulator Products Pty Ltd Moteur thermo-volumetrique semi-autonome
GB2447448A (en) * 2007-03-12 2008-09-17 Raymond Trefor William Lloyd Hydro-electric and hydro-thermal system
WO2008124868A1 (fr) * 2007-04-13 2008-10-23 Renewable Energy Systems Limited Procédés et systèmes de production d'énergie et de récupération d'énergie
GR20080100635A (el) * 2008-10-01 2010-05-13 Παυλος Μανωλουδης Μεθοδος και συσκευη "θερμικης μετατροπης ψυχρης δεξαμενης κλειστου ενεργειακου κυκλου"
CN102162397A (zh) * 2011-01-13 2011-08-24 绍兴文理学院 压水堆核动力燃汽轮机循环发电系统

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AU7340496A (en) 1997-04-30
JP2000509122A (ja) 2000-07-18
EP0858552A1 (fr) 1998-08-19

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