EP3227533A1 - A system for high efficiency energy conversion cycle by recycling latent heat of vaporization - Google Patents
A system for high efficiency energy conversion cycle by recycling latent heat of vaporizationInfo
- Publication number
- EP3227533A1 EP3227533A1 EP15890168.6A EP15890168A EP3227533A1 EP 3227533 A1 EP3227533 A1 EP 3227533A1 EP 15890168 A EP15890168 A EP 15890168A EP 3227533 A1 EP3227533 A1 EP 3227533A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- working fluid
- stage
- pressure
- vapour
- heat
- Prior art date
- Legal status (The legal status 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 status listed.)
- Pending
Links
- 238000009834 vaporization Methods 0.000 title claims abstract description 53
- 230000008016 vaporization Effects 0.000 title claims abstract description 53
- 238000006243 chemical reaction Methods 0.000 title abstract description 12
- 238000004064 recycling Methods 0.000 title abstract description 8
- 239000002918 waste heat Substances 0.000 claims abstract description 47
- 238000000034 method Methods 0.000 claims abstract description 45
- 238000010248 power generation Methods 0.000 claims abstract description 26
- 239000012530 fluid Substances 0.000 claims description 126
- 239000007788 liquid Substances 0.000 claims description 28
- 230000007246 mechanism Effects 0.000 claims description 27
- 238000009833 condensation Methods 0.000 claims description 23
- 230000005494 condensation Effects 0.000 claims description 23
- 230000008859 change Effects 0.000 claims description 16
- 238000012546 transfer Methods 0.000 claims description 16
- 230000008569 process Effects 0.000 claims description 11
- 230000000704 physical effect Effects 0.000 claims description 4
- 238000010438 heat treatment Methods 0.000 claims 2
- 238000003303 reheating Methods 0.000 claims 1
- 238000013461 design Methods 0.000 abstract description 14
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 39
- 229910021529 ammonia Inorganic materials 0.000 description 19
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 18
- 230000005611 electricity Effects 0.000 description 12
- 239000012071 phase Substances 0.000 description 12
- 238000000605 extraction Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 239000007791 liquid phase Substances 0.000 description 4
- 239000002826 coolant Substances 0.000 description 3
- 230000003467 diminishing effect Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 229920006395 saturated elastomer Polymers 0.000 description 3
- 239000002699 waste material Substances 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 239000003245 coal Substances 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- -1 solar Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000004557 technical material Substances 0.000 description 1
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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/04—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled condensation heat from one cycle heating the fluid in another cycle
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
-
- 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
- F01K25/10—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 the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/106—Ammonia
Definitions
- the present subject matter described herein in general, relates to electric power generation, and more particularly, towards a multi-stage system for efficiently driving electric power generating turbines.
- TECHNICAL PROBLEM The condenser has to remove the latent heat of vaporization to convert steam back to liquid so that the pumps can pump the fluid back to the start of the cycle with minimum energy requirement. This energy (latent heat) is then discarded to the surroundings as waste heat. Therefore, even the best power plants rarely achieve an efficiency of even 40%.
- TECHNICAL SOLUTION provides a mechanism to efficiently and economically solve the above mention technical problem by transferring the latent heat of vaporization of any stage into the input stage of the next stage instead of rejecting it into the atmosphere, and thereby greatly increasing the efficiency of any power cycle.
- a basic objective of the present invention is to overcome the disadvantages/drawbacks of the known art by increasing the conversion efficiency of heat into electricity of all existing and future power plants.
- the present invention provides the conversion of thermal energy into electrical energy in a power plant with higher efficiency then is possible with current technology.
- the improved efficiency by the use of present invention is achieved by reducing the amount of waste heat that is rejected into the atmosphere in existing plant cycle designs.
- the present invention provides a mechanism by creating multiple turbine cycles where the latent heat of vaporization of the first cycle is injected into the input stage of the second cycle and the waste heat (latent heat of vaporization) of the second cycle into the input stage of the third cycle and so on. Only the waste heat of the final cycle is rejected into the atmosphere.
- the present invention enables the utilization of waste latent heat and converts the same into electricity, and thereby achieving a significant improvement in the efficiency of a power plant.
- the waste heat exchange mechanism can also be used with all heat based power systems even if the final output is some form of non electrical output.
- the present invention increases the efficiency of any power cycle.
- the present invention enables the transfer of all the latent heat of vaporization into the next stage thereby greatly reducing the amount of energy required to heat the working fluid of that stage to the desired temperature. This results in an extremely high efficiency for all stages after the first stage resulting in a very high overall efficiency.
- embodiments of the present invention provide a plurality of aspects of the present application. The plurality of aspects provides a system/apparatus and method for high efficiency energy conversion cycle by recycling latent heat of vaporization. The technical solutions are as follows:
- a multi stage electric power generation apparatus with at least two stage system.
- the electric power generation apparatus comprises a first stage power cycle comprising a first working fluid, boiler, turbine, heat exchanger, pumps etc., and configured for electric power generation;
- a second stage power cycle comprising a second working fluid, boiler, turbine, heat exchanger, pumps, etc., and configured for electric power generation; wherein the second working fluid absorbs the waste heat (latent heat of vaporization and/or condensation) generated from first stage cycle for electric power generation.
- a method for generating electrical power using an electric power generation apparatus with at least two stage power cycle comprises: • generating electricity, using a first stage power cycle comprising a first working fluid, boiler, turbine, heat exchanger, pumps, etc;
- ⁇ generating electricity, using a second stage latent heat exchange mechanism and turbine cycle comprising a second working fluid, the electrical power generation; WHEREIN • the second working fluid absorbs the waste heat (latent heat of vaporization and/or condensation) generated from first stage in the latent heat exchange mechanism for generating electrical power.
- the low quality waste heat of the first stage is transferred to the input stage of the second cycle, the waste heat of the second cycle transferred to the input stage of the third cycle and so on.
- Figure 1 illustrates a simplified schematic of existing power plant cycles (Prior-art).
- Figure 2 illustrates a simplified schematic of a multistage cycle that will achieve very high efficiencies, in accordance with an embodiment of the present subject matter.
- Figure 3 illustrates an example of what a 2 stage system could look like if water and ammonia are used as working fluids, in accordance with an embodiment of the present subject matter.
- Figure 4 illustrates a method for generating an electrical power using an electric power generation apparatus with at least two stage latent heat exchange mechanism, in accordance with an embodiment of the present subject matter.
- Figure 5 illustrates a method performed during the first stage latent heat exchange mechanism 1000, in accordance with an embodiment of the present subject matter.
- Figure 6 illustrates a method performed during the second stage latent heat exchange mechanism 2000, in accordance with an embodiment of the present subject matter.
- FIG 1 illustrates basic layout of existing plant cycles as a prior- art.
- FIG 2 illustrates a simplified schematic of a multistage cycle that will achieve very high efficiencies, in accordance with an embodiment of the present subject matter.
- the low quality waste heat of the first stage is transferred to the input stage of the second cycle, the waste heat of the second cycle transferred to the input stage of the third cycle and so on.
- stage A 1000 a high pressure and low pressure turbine
- stage B 2000 a single stage turbine
- all existing techniques such as regenerative heat, open feed water heater and other minor modifications already in existence to improve cycle efficiencies and performance have been intentionally left out.
- thermo physical properties mentioned in this entire document have been taken from the National Institute of Standards and Technology (NIST) website at www.nist.com or more specifically from webbook.nist.gov/chemistry/fluid/.
- NIST National Institute of Standards and Technology
- boiler 2 it is heated to a high temperature of say 600°C (or any other desired temperature) and exits from boiler A 2 at point 10 as a supercritical or heated fluid.
- This high temperature and pressure supercritical fluid is then expanded in a high pressure turbine 3 and after a significant temperature and pressure drop is sent back to the boiler A 2 to be reheated back to 600°C at 50 bar (or any other desired temperature and pressure) and sent to a low pressure turbine 4 for final energy extraction to produce electricity.
- the steam exits the low pressure turbine A 4 at point 11 at sufficiently high pressure and temperature so as to allow for its latent heat energy transfer to the second working fluid which in the example used is ammonia, this is where the first major deviation from prior-art is made.
- the second working fluid which in the example used is ammonia
- the latent heat of vaporization of stage A 1000 will be transferred to the working fluid of stage B 2000 in heat exchanger A100 instead of being wasted into the atmosphere as is the case with existing prior-art.
- stage B 2000 In this process of transferring the latent heat energy to stage B 2000, the steam/vapour of stage A 1000 is converted back into a liquid at point 12 so that it may be pumped back into the input stage 13 at high pressure by condensate pump A 1.
- stage B 2000 has already absorbed the large amount of latent heat energy of stage A 1000, much less additional energy needs to be added in stage B 2000 to achieve the desired temperature.
- the ammonia By absorbing the latent heat energy of the steam in stage A 1000 in heat exchanger A 100 the ammonia has already been converted to a high temperature and pressure vapour at point 14. It may be understood by a person skilled in the art that, in this example, with the pressures and temperatures chosen, the ammonia is a vapour at point 14.
- the working fluid B in this case ammonia can exit heat exchanger A 100 as a liquid, vapour, or super critical liquid or super critical vapour at point 14 depending on the operating pressures desired for stage B. It then enters boiler B 5 where it is heated to the desired temperature before entering turbine B 6 at point 15. On exiting turbine B 6 at low pressure at point 16 the ammonia enters heat exchanger B 100 where it is cooled until it becomes liquid at point 17. Pump B 7 then pumps the liquid ammonia to the high pressure (that may be sub critical, critical or super critical pressure) point 18.
- the high pressure that may be sub critical, critical or super critical pressure
- stage B 2000 As a significant amount of the total amount of energy added in stage B 2000 was obtained from the transfer of the latent heat of vaporization of stage A 1000 to stage B 2000, much less additional energy is required in stage B 2000 to get the ammonia to the desired temperature. Therefore, all stages after the first stage will operate at very high efficiencies which will more than compensate for the slight efficiency drop in stage A 1000.
- each stage may be isolated from the other stages and none of the different stage fluids mix.
- the present invention enables to use any of existing techniques such as regenerative heat, open feed water heater, a multi stage turbines, and the like can continue to be used in each individual stage.
- the present invention may be used with any heat source that may include but not limited to coal, solar, nuclear, and the like.
- the latent heat of vaporization of any stage may be transferred into the input of the next stage at a temperature and pressure sufficiently high so as to cause a complete or partial phase change from liquid to vapour or super critical vapour and in the process the vapour of the first stage may be converted into liquid.
- the turbine exit pressure in all but the last stage may be above atmospheric temperature and pressure.
- any number of stages and choice of working fluids may be chosen depending individual requirements.
- the first stage efficiency of heat to electricity conversion may be slightly reduced with respect to what is possible in current designs.
- the subsequent stages may have a "virtual" efficiency that may even exceed 100%, and is explained in below sections.
- the working fluid of stage A 1000 may have the highest critical point temperature.
- Each subsequent stage e.g., 2000 may have a working fluid with a lower critical point temperature then the previous stage. Therefore, water would generally be the choice of fluid for the first stage.
- the present invention may be used as the lower stage of a gas fired plant.
- a heat pump in addition to a heat exchanger 100, can also be used to transfer heat from one stage to the next.
- the heat pump would consume energy and reduce the efficiency, it would also allow for removal of the temperature drop that may have to be maintained in some cases in the heat exchanger in order to transfer energy. The absence of a temperature drop in the heat exchanger would give a better efficiency and this would help in negating the energy consumed by the heat pump.
- a heat exchanger could be used to transfer the bulk of the energy while maintaining a temperature difference, and the final amount of energy could be transferred using a heat pump so that no temperature difference exists. This may be useful in the end stages.
- a multi stage electric power generation apparatus with at least two stage system.
- the electric power generation apparatus comprises of: a first stage power cycle 1000 comprising a first working fluid (not shown), and configured for electric power generation, and thereby generating waste heat(latent heat of vaporization and/or condensation); a second stage power cycle 2000 comprising a second working fluid (not shown), and configured for electric power generation, and thereby generating waste heat(latent heat of vaporization and/or condensation); WHEREIN the second working fluid absorbs all the waste heat(latent heat of vaporization and/or condensation) generated from first stage power cycle for the purpose of electric power generation.
- the first power generating stage comprises: a first means 1 configured to pass the first working fluid at a high pressure, a second means 2 configured to receive the first working fluid at the high pressure; heat the first working fluid to a high temperature to generate a heated or superheated fluid or vapour; a third means 3 and fourth means 4 configured to receive the heated fluid/vapour, and expand it till it drops to a certain temperature and pressure, andthe working fluid exits the power extraction stage at low pressure and temperature with its waste heat (latent heat of vaporization and/or condensation).
- the present invention comprises a heat exchanger mechanism 100, wherein the heat exchanger mechanism 100 is configured to transfer the waste heat (latent heat of vaporization and/or condensation) generated from the first stage 1000 to the second working fluid in the second stage 2000, and converts the second working fluid into a high temperature and pressure fluid or vapour.
- the waste heat latent heat of vaporization and/or condensation
- the heat exchanger mechanism 100 is configured to receive, during the first stage power cycle 1000, the first working fluid vapours from the fourth means 4, and cool it till it is converted to liquid form, and pass it to the first means 1; or receive, during the second stage power cycle 2000, the second working fluid vapours from the seventh means 7, and heat it with the waste energy of stage A 1000.
- the second stage power cycle comprises a fifth means 5 configured to: receive the second working fluid in liquid or vapour form at a high temperature and pressure,; and heat the second working fluid in liquid or vapour form to high temperature and pressure vapour; a sixth means 6 configured to receive the heated vapour at the high temperature and pressure, and generate electric power from the vapours, and exit the power extraction stage at low pressure and temperature with its latent heat of vaporization and/or condensation to enter a heat exchanger 200 where its waste heat (latent heat) is either transferred to the next stage or rejected to the atmosphere; a seventh means 7 configured to pass the second working fluid in liquid form at a high pressure.
- a fifth means 5 configured to: receive the second working fluid in liquid or vapour form at a high temperature and pressure,; and heat the second working fluid in liquid or vapour form to high temperature and pressure vapour
- a sixth means 6 configured to receive the heated vapour at the high temperature and pressure, and generate electric power from the vapours, and exit the power extraction stage at low pressure and temperature with its latent heat
- FIG 4 illustrates a method for generating an electrical power using an electric power generation apparatus with at least two stage latent heat exchange mechanism, in accordance with an embodiment of the present subject matter.
- the second working fluid after absorbing all the waste heat of the first stage may be further heated to obtain the desired temperature for the purpose of generating useable power.
- the method of generation is explained in description of figure 6.
- the remaining energy of the second working fluid (waste heat) may be transferred to a third working fluid or to the surrounding as waste heat.
- FIG 5 illustrates a method performed during the first stage power cycle 1000, in accordance with an embodiment of the present subject matter.
- the first working fluid at a high pressure is passed using a first means 1.
- the first working fluid at the high pressure is received by a second means 2.
- the second means 2 heats the first working fluid to a high temperature to generate a heated fluid.
- the heated fluid is received by a third means 3 and fourth means 4.
- the means 3 and 4 expands it till it drops to a certain temperature and pressure for the purposes of power generation.
- waste heat (latent heat) generated in this stage is transferred to the second stage working fluid in latent heat exchange mechanism A 100.
- the first working fluid is converted back to liquid phase and again provided to the first mean 1 and the cycle is repeated in 1000
- FIG 6 illustrates a method performed during the second stage power cycle 2000, in accordance with an embodiment of the present subject matter.
- the second working fluid at a high pressure is passed using a seventh means 7.
- the second working fluid of stage B 2000 absorbs all the waste heat (latent heat of vaporization /condensation) of the first working fluid of stage A 1000 and in the process significantly raises its temperature and energy content.
- the second working fluid at high temperature and pressure exits from the heat exchanger mechanism 100 wherein the latent heat from stage A 1000 is provided to the second working fluid, is received by the fifth means 5 at a high temperature and pressure and further heated if desired to the final temperature.
- the second working fluid enters the sixth means 6 at high temperature and pressure for the purposes of energy generation.
- any existing means for enhancing efficiency may also be utilized as desired.
- the excess waste heat generated in second stage 2000 is either transferred to a third working fluid or emitted or ejected out into the atmosphere by the heat exchanger 200.
- the second working fluid is converted back to liquid phase and again provided to the seventh mean 7 and the cycle is repeated in stage B 2000.
- the massive amount of energy that is released in a phase change of steam to liquid water can only be removed with a phase change (complete or partial) in another liquid which in this example is ammonia.
- the alternative is to use the existing technique of massive amounts of cooling water from rivers or oceans in which case the latent heat is lost to the environment as low temperature waste heat.
- the present invention enables to transfer all the latent energy of a working fluid at relatively low pressure into the high pressure input stage of another turbine cycle. With proper choice of working fluids, pressures, and temperatures it is possible to achieve any efficiency one desires.
- the choice of temperatures and pressures or coolants used are just an example to help in understanding the process, and any temperature or pressure or coolant could be used depending on individual situations.
- the important point is that the latent heat is not rejected into the atmosphere as waste heat but is transferred into the next stage with proper choice of turbine exit pressures and temperatures depending on the coolant.
- the reason why we can exceed the limits set by the Carnot Equations is that they were never really applicable to any system that utilizes a phase change in order to extract energy from heat.
- the obvious example to support this statement is the very fact that no system in operation has come even remotely close to the efficiencies defined by the Carnot Equations. In any system employing a phase change the actual maximum efficiency under ideal conditions should be described as :
- AH vap is the latent heat of vaporization in kJ/Kg at the turbine exit pressure.
- the steam exiting the turbine is not a saturated vapour. If a saturated vapour is allowed or desired, the latent heat value should be adjusted accordingly. In the event that two stages as described earlier in the document are used the equation would be as:
- AH y apis the latent heat of vaporization in kJ/Kg at the turbine exit pressure in stage A
- AH yap is the latent heat of vaporization in kJ/Kg at the turbine exit pressure in stage B
- ⁇ if the flow factor to compensate for the different flow rates that may exist between stages A and B and would be defined as (mass flow rate of stage B)/(mass flow rate of stage A)
- n is the number of stages and ⁇ ⁇ is the mass flow rate in stage n divided by the mass flow rate of stage A.
- E t is the total energy loss in the entire system.
- Ammonia will undergo a phase change above 125.17°C whereas the steam in stage A at 10 bar will change phase below 179.88°C.
- This temperature difference will allow for the energy transfer from stage A to B in heat exchanger A and as the Ammonia goes from liquid phase to a vapour phase, the steam in stage A cools down to a liquid which can then be pumped to a higher pressure to continue the cycle.
- the large amount of energy released by a phase change of steam to liquid water can only be absorbed because the ammonia changes phase from liquid to vapour.
- the ammonia leaves the heat exchanger A at 180°C with an Enthalpy of 1831kJ/Kg, it has absorbed all the latent energy available in the water in stage A.
- stage B could be higher or lower than that of stage A so as to match the amount of energy that needs to be transferred between stages.
- the steam releases 2027kJ/Kg (2777kJ/Kg-750kJ/Kg) whereas the ammonia can absorb only 1295kJ/Kg (1831kJ/Kg-536kJ/Kg).
- the mass flow rate of Ammonia would have to be 1.56 (2027kJ/Kg/1295kJ/Kg) times greater than the mass flow rate of water in order to absorb all the energy required to convert it to liquid. If a lower or higher flow rate ratio is preferred for the ammonia cycle, one need only to simply increase or decrease the turbine exit pressure and temperature of stage A according to the requirements.
- This figure of course is an approximation since no energy losses have been taken into account.
- the third stage will result in an efficiency that will exceed those set by the Carnot equations thus invalidating them. With an unlimited number of stages and ideal systems, one could actually approach near 100% efficiency.
- First means and Seventh means may include but not limited to pumps and the like devices having similar functionality or purpose as that of the pump.
- Second means and Fifth means may include but not limited to boilers and the like devices having similar functionality or purpose as that of the boilers.
- Third means, Fourth means, and Sixth means may include but not limited to high pressure turbines, low pressure turbines, and the like devices having similar functionality or purpose as that of the high / low pressure turbines.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IN3127DE2014 | 2014-10-31 | ||
PCT/IB2015/058331 WO2016067225A2 (en) | 2014-10-31 | 2015-10-29 | A system for high efficiency energy conversion cycle by recycling latent heat of vaporization |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3227533A1 true EP3227533A1 (en) | 2017-10-11 |
EP3227533A4 EP3227533A4 (en) | 2018-07-11 |
Family
ID=55858474
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15890168.6A Pending EP3227533A4 (en) | 2014-10-31 | 2015-10-29 | A system for high efficiency energy conversion cycle by recycling latent heat of vaporization |
Country Status (12)
Country | Link |
---|---|
US (1) | US20170248040A1 (en) |
EP (1) | EP3227533A4 (en) |
JP (1) | JP2017533380A (en) |
KR (2) | KR20200128594A (en) |
CN (1) | CN107002511A (en) |
AU (1) | AU2015413548B2 (en) |
BR (1) | BR112017008206B1 (en) |
CA (1) | CA2964325C (en) |
EA (1) | EA038785B1 (en) |
MX (1) | MX2017005131A (en) |
MY (1) | MY189450A (en) |
WO (1) | WO2016067225A2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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GB2535181A (en) * | 2015-02-11 | 2016-08-17 | Futurebay Ltd | Apparatus and method for energy storage |
GB2552963A (en) * | 2016-08-15 | 2018-02-21 | Futurebay Ltd | Thermodynamic cycle apparatus and method |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS61152915A (en) * | 1984-12-26 | 1986-07-11 | Kawasaki Heavy Ind Ltd | Energy recovering system |
US5440882A (en) * | 1993-11-03 | 1995-08-15 | Exergy, Inc. | Method and apparatus for converting heat from geothermal liquid and geothermal steam to electric power |
US5822990A (en) * | 1996-02-09 | 1998-10-20 | Exergy, Inc. | Converting heat into useful energy using separate closed loops |
DE19907512A1 (en) * | 1999-02-22 | 2000-08-31 | Frank Eckert | Apparatus for Organic Rankine Cycle (ORC) process has a fluid regenerator in each stage to achieve a greater temperature differential between the cascade inlet and outlet |
JP2002285907A (en) * | 2001-03-27 | 2002-10-03 | Sanyo Electric Co Ltd | Recovery refrigeration system of exhaust heat for micro gas turbine |
US6948315B2 (en) * | 2004-02-09 | 2005-09-27 | Timothy Michael Kirby | Method and apparatus for a waste heat recycling thermal power plant |
US20100263380A1 (en) * | 2007-10-04 | 2010-10-21 | United Technologies Corporation | Cascaded organic rankine cycle (orc) system using waste heat from a reciprocating engine |
US8522552B2 (en) * | 2009-02-20 | 2013-09-03 | American Thermal Power, Llc | Thermodynamic power generation system |
CN101614139A (en) * | 2009-07-31 | 2009-12-30 | 王世英 | Multicycle power generation thermodynamic system |
US9046006B2 (en) * | 2010-06-21 | 2015-06-02 | Paccar Inc | Dual cycle rankine waste heat recovery cycle |
US20130160449A1 (en) * | 2011-12-22 | 2013-06-27 | Frederick J. Cogswell | Cascaded organic rankine cycle system |
US9018778B2 (en) * | 2012-01-04 | 2015-04-28 | General Electric Company | Waste heat recovery system generator varnishing |
JP6013140B2 (en) * | 2012-11-01 | 2016-10-25 | 株式会社東芝 | Power generation system |
-
2015
- 2015-10-29 WO PCT/IB2015/058331 patent/WO2016067225A2/en active Application Filing
- 2015-10-29 MX MX2017005131A patent/MX2017005131A/en unknown
- 2015-10-29 KR KR1020207031645A patent/KR20200128594A/en not_active Application Discontinuation
- 2015-10-29 EP EP15890168.6A patent/EP3227533A4/en active Pending
- 2015-10-29 KR KR1020177013549A patent/KR20170077159A/en not_active IP Right Cessation
- 2015-10-29 US US15/517,285 patent/US20170248040A1/en not_active Abandoned
- 2015-10-29 EA EA201790859A patent/EA038785B1/en unknown
- 2015-10-29 BR BR112017008206-3A patent/BR112017008206B1/en active IP Right Grant
- 2015-10-29 CN CN201580055257.XA patent/CN107002511A/en active Pending
- 2015-10-29 JP JP2017519926A patent/JP2017533380A/en active Pending
- 2015-10-29 AU AU2015413548A patent/AU2015413548B2/en active Active
- 2015-10-29 MY MYPI2017701248A patent/MY189450A/en unknown
- 2015-10-29 CA CA2964325A patent/CA2964325C/en active Active
Also Published As
Publication number | Publication date |
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KR20170077159A (en) | 2017-07-05 |
MX2017005131A (en) | 2019-02-20 |
WO2016067225A2 (en) | 2016-05-06 |
JP2017533380A (en) | 2017-11-09 |
CN107002511A (en) | 2017-08-01 |
WO2016067225A3 (en) | 2016-06-23 |
US20170248040A1 (en) | 2017-08-31 |
CA2964325A1 (en) | 2016-05-06 |
AU2015413548A1 (en) | 2017-08-03 |
CA2964325C (en) | 2020-10-27 |
BR112017008206B1 (en) | 2023-10-31 |
EA201790859A1 (en) | 2017-11-30 |
KR20200128594A (en) | 2020-11-13 |
AU2015413548B2 (en) | 2019-08-15 |
BR112017008206A2 (en) | 2017-12-26 |
EP3227533A4 (en) | 2018-07-11 |
EA038785B1 (en) | 2021-10-19 |
MY189450A (en) | 2022-02-14 |
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