US3795103A - Dual fluid cycle - Google Patents

Dual fluid cycle Download PDF

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US3795103A
US3795103A US00185243A US3795103DA US3795103A US 3795103 A US3795103 A US 3795103A US 00185243 A US00185243 A US 00185243A US 3795103D A US3795103D A US 3795103DA US 3795103 A US3795103 A US 3795103A
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fluid
power
isobutane
water
hot
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J Anderson
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/185Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using waste heat from outside the plant

Abstract

Power is extracted from a stream of hot fluid, such as geothermal water, by passing the stream in heat exchange relationship with a working fluid to vaporize the latter, expanding the vapor through a turbine, and condensing the vapor in a conventional Rankine cycle. Additional power is obtained in a second Rankine cycle by employing a portion of the hot fluid after heat exchange with the working fluid to vaporize a second working fluid having a lower boiling point and higher vapor density than the first fluid. Isobutane and R-22 (CH C1 F2) may be employed as the first and second working fluids, respectively.

Description

United States Patent 1191 Anderson 1 1 DUAL FLUID CYCLE [76] Inventor: James Hilbert Anderson, 1615 Hillock Ln'., York, Pa. 17403 [22] Filed: Sept. 30, 1971 [21] Appl. No.: 185,243

521 vs. c1. 60/651, 60/655, 671

[ Mar.5,1974

Primary Examiner-Edgar W. Geoghegan Assistant Examiner-Allen M. Ostrager Power is extracted from a stream of hot fluid, such as 32 3/ REE/6 7' geothermal water, by passing the stream in heat ex- [51] Int. Cl F01k 25/06 change relationship with a working fluid to vaporize [58] Fleld f Search 60/38, 95 the latter, expanding the vapor gh a turbine, and v condensing the vapor in a conventional Rankine cycle. [56] References Clted Additional power is obtained in'a second Rankine UNITED STATES PATENTS cycle by employing a portion of the hot fluid after 2,120,909 6/1938 Schmer 60/95 h a ex hange with the working fluid to vaporize '6 1,465,095 7/1923 Richardson 60/95 R X second working fluid having a lower boiling point and 2, 4/1952 gg 60/3 higher vapor density than the first fluid. lsobutane and FOREIGN PATENTS 0R APPLICATIONS R42 m be m i as the first d 514,551 10/1952 Belgium Secon wor mg respecuv'e 551,671 10/1956 Belgium 60/95 7 Claims, 2 Drawing Figures n 44 ,zon CO/VDf/KS'I'R -a 60/1/05/116276 COOL //VG- PO/VO.

3| 5 I v I 1 SOURCE DUAL FLUID CYCLE BACKGROUND OF THE INVENTION The same elements are referred to by the same reference numerals in both Figures.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT FIG. 1 shows a conventional Rankine cycle system for producing power from a source of hot fluid which may be, for instance, a geothermal water source 10.

, Water from source 10 passes through a conduit 12 to It is well known to produce power from a source of hot fluid by passing that fluid in heat exchanging with a second fluid so that the second fluid is vaporized and then expanding the second fluid through a turbine to produce power.

One of the largest factors in-the initial cost of such power plants is the cost of the heat exchangers in which the hot fluid is passed in heat exchanging relation to the second fluid. The size of the heat exchangers is controlled by the equation Q UATA in which Q is the heat per unit time passed by the heat exchanger, A is the heat exchange area of the exchanger which, .of course is determined by the size of the exchanger, and the numbers of tubes used therein, AT is the log mean temperature difference between the fluid being heated and the fluid being cooled and U isa constant. The quantity Q is generally fixed by the requirements of the power system so the only way of reducing A, and thus the sizeof-the heat exchanger is by increasing AT.

One way to increase AT is to increase the relative flow rate of the hot fluid to the cold fluid. In this way less heat is taken from each pound of hot fluid and thus the exit temperature of the hot fluid is higher. and the log mean temperature difference AT is greater. However, the increase in flow rate for the hot ,fluid would require an increase in operational costs inthe power plant unless the hot fluid exiting from the heat exchanger can be further utilized, i,.e., unless a means is used for producing additional power from the hot fluid.

SUMMARY OF THE INVENTION his the object of this invention to provide a power plant for utilizing the heat from a hot fluid in which the constructional costs are low compared to the power output because the total area of the heat exchangers is small and yet the operationalcosts are low because a great amount of the heat in the hot fluid is used to produce power.

Basically, the invention comprises the addition to the power plant of a second power cycle using a second power fluid which has a lower boiling temperature as well as a higher vapor density than the first power fluid. A portion of the hot fluid is diverted from the first power cycle to heat and vaporize the second power fluid which is then expanded through a second turbine to produce power. Since the second power fluid hasa higher vapor density than the first powerfluid it requires a smaller turbine than would the first power fluid for an equival'ent power output.

BRIEF DESCRIPTION OF THE'DRAWINGS FIG. 1 shows a prior art system for producing power from a hot fluid, and

FIG. 2 shows a system in accord with the invention for producing power from a'hot'fluid.

a boiler 13 in which the first power fluid, which may be isobutane, is vaporized. The water exits from the boiler at a lower temperature since a portion of its heat has been used to vaporize the isobutane and the water then passesby conduit 14 to the isobutane heater-l where it also runs in counter-heat exchanging relation to the isobutane to heat the isobutane prior to the power fluid flow through conduit 16 to the boiler 13. From the heater the water is exhausted to a waste water reservoir (not shown).

The isobutane vapor issuing from the boiler 13 passes through conduit 17 to a conventional turbine 18 and ,is exhausted therethrough to low pressure vapor output 19 which is connected to a condenser 20 wherein the low pressure power fluid vapor is condensed by passing it in heat exchange relation to the cooling water from source 21. The power produced by turbine 18 may, for instance, be transformed to electrical power by use of a generator 28.

From the condenser 20, the isobutane,:which is now in the liquid state, passes through a conduit 22, is pressurized by feed pump 23 and passes through conduit 24 back to the isobutane inlet of the heater 15.

The feed pump 23 is operated by a small turbine 25 which is powered by a portion of the isobutane vapor which is removed from turbine 18 at a position intermediate the high pressure and low pressure ends thereof. The vapor passes'by conduit 26 to the turbine 25, is expanded through this turbine and is exhausted from the low pressure end thereof by a conduit 27 which communicates with conduit 19 and thus the condenser 20'. i

In order to decrease the size of boiler 13 and heater 15 it is desirable to increase the flow rate of the hot water passing therethrough. However, in this case, it is also desirable to utilize the'heat remaining in the hot water exiting from exchanger 15 or boiler 13 in a subsequent system for producing power. Thus, in FIG. 2 a portion of the hot water flowing through conduit l4 is removed via conduit 29 and passesthrough a boiler 30 in a second power fluid for instance, the refrigerant, R-22, CH Cl F chlorodifluoromethane, having a lower boiling temperature than isobutane, is vaporized by the hot water. The water then passes via conduit 31 to a heatexchanger 32 in which the R-22 is heated prior to its vaporization. 7

Finally, the water, having been relieved of much of its heat content, is rejected from heater 32 to'a waste water reservoir. Meanwhile, in the second power cycle, the R-22 which is heated in heater 32 passes by a conduit 33 to the boiler 30 and it vaporized therein. The R-22 which is now in the vapor state then'passes through a conduit 34, to turbine 35 and is expanded therethrough. The R-22 vapor then. exits from the low pressureend thereof through a low pressure exhaust conduit 36 to the R-22 condenser 37 where the R-22 changes back to the liquid state.

In the liquid state, the second power fluid passes through conduit 38, a pressurizing pump 39 and conduit 40 to the second power fluid input to heater 32. It

is noted that both the pumps 23 and 39 shown in FIG. 2 may be powered, as is the pump in FIG. I, by a turbine run by the power fluids or they may be powered,

as is shown, by motors 41 and 42, respectively.

It is further noted that the cooling water which passes from the cooling pond, through conduit 43 and into the condenser 37 for condensing the R-22 then passes through conduit 44 to the condenser 20 for condensing the isobutane. Since the condensing temperature as well as the boiling temperature of R-22' is lower than that of isobutane, the cooling water is still cool enough after passing through the R-22 condenser fluid 37 to condense the isobutane in condenser 20 and since the isobutane is condensed at a higher'temperature, the specific volume at the exhaust of turbine 18 is reduced and thus the size of the turbine '18 is reduced. Furthermore, since R-22 notonly has a lower boiling temperature at a given pressure than isobutane, but also has a higher vapor density, the R-ZZ turbine can be smaller for the same power output than the isobutane turbine. Thus, in FIGv 2 a systemis shown which produces a greater power output for a given turbine size, i.e., size of turbine 18 plus turbine 35 and a smaller heat exchanger area, i.e., the total area of the exchangers l3, 15, 30 and 32 than would be required by a single Rankine cyele'using the same amount of hot water and a single power fluid, or by two Rankine cycles using a single power fluid.

An example of the efficieneies possible utilizing the system shown in FIG. 2 is described in thefollowing example in which the first power fluid is isobutane, the second power fluid is R-2 2, and the hot fluid is water. In this-example it is assumed that the water issuing from source through conduit 12 has a temperature of approximately 325F. andthe isobutane is heated to a superheat temperature of 300F. at'a pressure of 500 psi in heat exchanger and boiler 13 and that the temperature of the water exiting from boiler 13 into conduit I4 is 277F. Given these factors, it can be shown through standard calculations that 1.385 pounds of water per. pound of isobutane must flow through the boiler 13. If it is further assumed that the isobutane is condensed at a temperature of approximately 72F. and is vaporized at a temperature of approximately 269F. then 0.830 pounds of water per pound of isobutane will be needed to raise the isobutane from its condensate temperature of approximately 72F. to itsboiling temperature of approximately 269F. In other words, 1.385 minus 0.830 or 0.555 pounds of water per pound of isobutane which is needed in the boiler 13 is not needed in the heat exchanger 15 and thus may be split off at conduit 14 for the purpose of heating and boiling R-22.

lf'it is also assumed that boiler 30 and heater 32 are so designed that the water temperature leaving the boiler 30 is 178F. and the temperature of water leaving the heater 32 is 121 .5F., it can be determined through well-known'calculations that the gross generator output from generator 45 which is attached to turbine 35 is 16.04 Btu per pound of water flowing through the R-22 cycle. It can also be determined from the same type of calculations that for the isobutane cycle described above the gross generator output and Btu per pound of water would be 2l.4 Btu'per pound of water entering the isobutane cycle. Thus, for each point of water which enters the isobutane cycle 21.4 Btu of power would be produced from the system and since 0.555/l.385 of each initial pound of water is shunted through the R-22 system an additional 0555/1385 (16.04) of 6.4 Btu per pound of water entering the isobutane cycle would be produced by the R-22 system.

This represents a 30 percent increase in the gross generator output per pound of water entering the isobutane cycle over a system such as shown in FIG. I and this increase is not accompanied by a great increase in equipment cost. The heat exchangers 32 and 15 and the boilers 30 and 13 may be made much smaller due to the increased water flow therethrough and the additional turbine 35 is smaller than an addition to turbine 18 which would produce equivalent power due to the higher vapor density of R-22.

tion, it should be obvious to one skilled in the art that many modifications are possible within the scope of this invention. Thus, for example, other fluid combinations couldbe used besides isobutane and R22. The important factor in selecting the appropriate fluids is that the higher boiling temperature fluid must'be at the hotter end of the cycle. In addition, it is obvious that these principles could be extended to appiy to a plurality of fluid cycles and need not be limited to two fluid cycles.

Also, both of the turbines in FIG. 2 could be connected to a single generator instead of being as shown connected to separate generators.

What is claimed is:

I. In the method of producing power by vaporizing a first power fluid with a stream of hot fluid passed in heat exchange relationship in a first region with said first power fluid, expanding the vaporized first power fluid to produce power, condensing the first power fluid vapor and passing the condensed power fluid in heat exchange relationship in a second region with said hot fluid, the improvement comprising: passing the hot fluid sequentially through said first and second regions while passing said first power fluid sequentially through said regions in the opposite direction tothereby heat said first power fluid in said second region and to vaporize said first power fluid in said first region, passing a portion of the hot fluid from between said first and second regions into heat exchange relationship with a second power fluid having a lower boiling temperature than said first power fluid to vaporize said second power fluid, expanding said second power fluid to produce power, condensing said second power fluid by passing it in heat exchange relationship with a cooling fluid, then passing the cooling fluidin heat exchange relationship with said vaporized first power fluid to condense the latter.

2. The method of claim 1 wherein said second power fluid has a higher vapor density than said first power fluid.

3. The method of claim 1 wherein said hot fluid is water.

6. heat exchange relationship with said second power fluid to produce power in a vaporization and expansion cycle.

7. The method of claim 1 wherein said cooling fluid is a stream of recycled cooling water.

Claims (6)

  1. 2. The method of claim 1 wherein said second power fluid has a higher vapor density than said first power fluid.
  2. 3. The method of claim 1 wherein said hot fluid is water.
  3. 4. The method of claim 2 wherein said first power fluid is isobutane.
  4. 5. The method of claim 4 wherein said second power fluid is R-22.
  5. 6. The method of claim 1 wherein said hot fluid is passed in heat exchange relationship with at least a third power fluid after said hot fluid has been passed in heat exchange relationship with said second power fluid to produce power in a vaporization and expansion cycle.
  6. 7. The method of claim 1 wherein said cooling fluid is a stream of recycled cooling water.
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Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4102133A (en) * 1977-04-21 1978-07-25 James Hilbert Anderson Multiple well dual fluid geothermal power cycle
US4104535A (en) * 1976-04-23 1978-08-01 Ormat Turbines (1965) Ltd. Hybrid electric power generating system
FR2410742A1 (en) * 1977-12-05 1979-06-29 Fiat Spa engine fueling facility from heat sources at various temperatures
EP0003264A1 (en) * 1977-12-29 1979-08-08 Reikichi Nozawa Method and plant for generating power
EP0007850A1 (en) * 1978-07-13 1980-02-06 Creusot-Loire Plant for recovering energy
US4192145A (en) * 1977-10-25 1980-03-11 Nihon Sekiyu Hanbai Kabushiki Kaisha Process for utilizing energy produced by the phase change of liquid
US4503682A (en) * 1982-07-21 1985-03-12 Synthetic Sink Low temperature engine system
US4622472A (en) * 1984-07-16 1986-11-11 Ormat Turbines Ltd. Hybrid electric power generating system
US4700543A (en) * 1984-07-16 1987-10-20 Ormat Turbines (1965) Ltd. Cascaded power plant using low and medium temperature source fluid
US4738111A (en) * 1985-12-04 1988-04-19 Edwards Thomas C Power unit for converting heat to power
US6035643A (en) * 1998-12-03 2000-03-14 Rosenblatt; Joel H. Ambient temperature sensitive heat engine cycle
WO2000073631A1 (en) * 1999-06-02 2000-12-07 Valentin Vasilievich Korneev Thermal powerplant
WO2007148076A1 (en) * 2006-06-20 2007-12-27 Peter John Bayram Renewable gravity power via refrigerated liquid refrigerant turbine-generators
GB2451961A (en) * 2006-06-20 2009-02-18 Peter John Bayram Renewable gravity power via refrigerated liquid refrigerant turbine-generators
US20100327605A1 (en) * 2009-06-26 2010-12-30 Larry Andrews Power Generation Systems, Processes for Generating Energy at an Industrial Mine Site, Water Heating Systems, and Processes of Heating Water
US20110173978A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Cold Water Pipe
US20110173979A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Plant
US20120192563A1 (en) * 2011-01-28 2012-08-02 Johnson Controls Technology Company Heat Recovery System Series Arrangements
CN102877903A (en) * 2012-10-22 2013-01-16 哈尔滨工业大学 Heat supply and power generation system of low-temperature heat source without direct working capability
US20130042612A1 (en) * 2011-08-15 2013-02-21 Laurence Jay Shapiro Ocean thermal energy conversion power plant
US20130091841A1 (en) * 2010-01-19 2013-04-18 Celine Mahieux Multi cycle geothermal power plant
US20130104546A1 (en) * 2011-10-31 2013-05-02 Dharendra Yogi Goswami Integrated Cascading Cycle Solar Thermal Plants
JP2013531178A (en) * 2010-07-14 2013-08-01 ジ アベル ファウンデーション, インコーポレイテッド Industrial ocean thermal energy conversion process
US20130263599A1 (en) * 2012-04-09 2013-10-10 Delta Electronics, Inc. Thermal magnetic engine and thermal magnetic engine system
US20130328322A1 (en) * 2012-06-07 2013-12-12 Marvin Duane Julian Non-to-minimally fractionalized biomass-fueled renewable energy
US8820080B2 (en) * 2010-06-28 2014-09-02 Marvin Duane Julian Nonfractionalized biomass-fueled refrigerant-based cogeneration
US20140245737A1 (en) * 2011-09-09 2014-09-04 Saga University Steam power cycle system
US20150135709A1 (en) * 2011-07-25 2015-05-21 Ormat Technologies, Inc. Cascaded power plant using low and medium temperature source fluid
US9151279B2 (en) 2011-08-15 2015-10-06 The Abell Foundation, Inc. Ocean thermal energy conversion power plant cold water pipe connection
US9797386B2 (en) 2010-01-21 2017-10-24 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
WO2018068430A1 (en) * 2016-10-12 2018-04-19 李华玉 Steam combined cycle having single working fluid, and combined-cycle steam power device

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BE514551A (en) * 1951-10-01
BE551671A (en) * 1955-10-22
US1465095A (en) * 1920-09-23 1923-08-14 Gen Electric Heating system
US2120909A (en) * 1936-07-04 1938-06-14 Gen Electric Elastic fluid condenser arrangement
US2593963A (en) * 1950-01-11 1952-04-22 Gen Electric Binary cycle power plant having a high melting point tertiary fluid for indirect heating

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
US1465095A (en) * 1920-09-23 1923-08-14 Gen Electric Heating system
US2120909A (en) * 1936-07-04 1938-06-14 Gen Electric Elastic fluid condenser arrangement
US2593963A (en) * 1950-01-11 1952-04-22 Gen Electric Binary cycle power plant having a high melting point tertiary fluid for indirect heating
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Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4104535A (en) * 1976-04-23 1978-08-01 Ormat Turbines (1965) Ltd. Hybrid electric power generating system
US4102133A (en) * 1977-04-21 1978-07-25 James Hilbert Anderson Multiple well dual fluid geothermal power cycle
US4192145A (en) * 1977-10-25 1980-03-11 Nihon Sekiyu Hanbai Kabushiki Kaisha Process for utilizing energy produced by the phase change of liquid
FR2410742A1 (en) * 1977-12-05 1979-06-29 Fiat Spa engine fueling facility from heat sources at various temperatures
EP0003264A1 (en) * 1977-12-29 1979-08-08 Reikichi Nozawa Method and plant for generating power
EP0007850A1 (en) * 1978-07-13 1980-02-06 Creusot-Loire Plant for recovering energy
FR2431025A1 (en) * 1978-07-13 1980-02-08 Creusot Loire Installation for recovering energy
US4503682A (en) * 1982-07-21 1985-03-12 Synthetic Sink Low temperature engine system
US4700543A (en) * 1984-07-16 1987-10-20 Ormat Turbines (1965) Ltd. Cascaded power plant using low and medium temperature source fluid
US4622472A (en) * 1984-07-16 1986-11-11 Ormat Turbines Ltd. Hybrid electric power generating system
US4738111A (en) * 1985-12-04 1988-04-19 Edwards Thomas C Power unit for converting heat to power
US6035643A (en) * 1998-12-03 2000-03-14 Rosenblatt; Joel H. Ambient temperature sensitive heat engine cycle
WO2000073631A1 (en) * 1999-06-02 2000-12-07 Valentin Vasilievich Korneev Thermal powerplant
WO2007148076A1 (en) * 2006-06-20 2007-12-27 Peter John Bayram Renewable gravity power via refrigerated liquid refrigerant turbine-generators
GB2451961A (en) * 2006-06-20 2009-02-18 Peter John Bayram Renewable gravity power via refrigerated liquid refrigerant turbine-generators
US20100327605A1 (en) * 2009-06-26 2010-12-30 Larry Andrews Power Generation Systems, Processes for Generating Energy at an Industrial Mine Site, Water Heating Systems, and Processes of Heating Water
US8237299B2 (en) * 2009-06-26 2012-08-07 Larry Andrews Power generation systems, processes for generating energy at an industrial mine site, water heating systems, and processes of heating water
US20130091841A1 (en) * 2010-01-19 2013-04-18 Celine Mahieux Multi cycle geothermal power plant
US9797386B2 (en) 2010-01-21 2017-10-24 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
US20110173979A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Plant
US9086057B2 (en) 2010-01-21 2015-07-21 The Abell Foundation, Inc. Ocean thermal energy conversion cold water pipe
US20110173978A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Cold Water Pipe
US8899043B2 (en) 2010-01-21 2014-12-02 The Abell Foundation, Inc. Ocean thermal energy conversion plant
US10184457B2 (en) 2010-01-21 2019-01-22 The Abell Foundation, Inc. Ocean thermal energy conversion plant
US8820080B2 (en) * 2010-06-28 2014-09-02 Marvin Duane Julian Nonfractionalized biomass-fueled refrigerant-based cogeneration
JP2013531178A (en) * 2010-07-14 2013-08-01 ジ アベル ファウンデーション, インコーポレイテッド Industrial ocean thermal energy conversion process
US9816402B2 (en) * 2011-01-28 2017-11-14 Johnson Controls Technology Company Heat recovery system series arrangements
US20120192563A1 (en) * 2011-01-28 2012-08-02 Johnson Controls Technology Company Heat Recovery System Series Arrangements
US9784248B2 (en) * 2011-07-25 2017-10-10 Ormat Technologies, Inc. Cascaded power plant using low and medium temperature source fluid
US20150135709A1 (en) * 2011-07-25 2015-05-21 Ormat Technologies, Inc. Cascaded power plant using low and medium temperature source fluid
US9909571B2 (en) 2011-08-15 2018-03-06 The Abell Foundation, Inc. Ocean thermal energy conversion power plant cold water pipe connection
CN107036463A (en) * 2011-08-15 2017-08-11 阿贝尔基金会 Ocean Thermal Energy Conversion Power Plant
US9151279B2 (en) 2011-08-15 2015-10-06 The Abell Foundation, Inc. Ocean thermal energy conversion power plant cold water pipe connection
US20130042612A1 (en) * 2011-08-15 2013-02-21 Laurence Jay Shapiro Ocean thermal energy conversion power plant
US9945263B2 (en) * 2011-09-09 2018-04-17 Saga University Steam power cycle system
US20140245737A1 (en) * 2011-09-09 2014-09-04 Saga University Steam power cycle system
US20130104546A1 (en) * 2011-10-31 2013-05-02 Dharendra Yogi Goswami Integrated Cascading Cycle Solar Thermal Plants
US20130263599A1 (en) * 2012-04-09 2013-10-10 Delta Electronics, Inc. Thermal magnetic engine and thermal magnetic engine system
US8984885B2 (en) * 2012-04-09 2015-03-24 Delta Electronics, Inc. Thermal magnetic engine and thermal magnetic engine system
US8887504B2 (en) * 2012-06-07 2014-11-18 Marvin Duane Julian Non-to-minimally fractionalized biomass-fueled renewable energy
US20130328322A1 (en) * 2012-06-07 2013-12-12 Marvin Duane Julian Non-to-minimally fractionalized biomass-fueled renewable energy
CN102877903A (en) * 2012-10-22 2013-01-16 哈尔滨工业大学 Heat supply and power generation system of low-temperature heat source without direct working capability
WO2018068430A1 (en) * 2016-10-12 2018-04-19 李华玉 Steam combined cycle having single working fluid, and combined-cycle steam power device

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