US20110100009A1 - Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method - Google Patents

Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method Download PDF

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Publication number
US20110100009A1
US20110100009A1 US12/609,348 US60934809A US2011100009A1 US 20110100009 A1 US20110100009 A1 US 20110100009A1 US 60934809 A US60934809 A US 60934809A US 2011100009 A1 US2011100009 A1 US 2011100009A1
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United States
Prior art keywords
fluid
pipe
wall
heat exchanger
heat
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Abandoned
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US12/609,348
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English (en)
Inventor
Matthew Alexander Lehar
Thomas Frey
Gabor Ast
Sebastian Freund
Richard Aumann
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Nuovo Pignone SpA
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Nuovo Pignone SpA
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Application filed by Nuovo Pignone SpA filed Critical Nuovo Pignone SpA
Priority to US12/609,348 priority Critical patent/US20110100009A1/en
Assigned to NUOVO PIGNONE S.P.A reassignment NUOVO PIGNONE S.P.A ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AUMANN, RICHARD, AST, GABOR, FREUND, SEBASTIAN, FREY, THOMAS, LEHAR, MATTHEW ALEXANDER
Priority to MX2012005081A priority patent/MX2012005081A/es
Priority to BR112012010150A priority patent/BR112012010150A2/pt
Priority to AU2010311522A priority patent/AU2010311522A1/en
Priority to EP10770842.2A priority patent/EP2780558A2/en
Priority to PCT/EP2010/066282 priority patent/WO2011051353A2/en
Priority to RU2012116621/06A priority patent/RU2012116621A/ru
Priority to PE2012000599A priority patent/PE20130026A1/es
Priority to CA2779074A priority patent/CA2779074A1/en
Priority to CN2010800600551A priority patent/CN103228912A/zh
Publication of US20110100009A1 publication Critical patent/US20110100009A1/en
Priority to CL2012001098A priority patent/CL2012001098A1/es
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of 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
    • 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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/12—Forms of water tubes, e.g. of varying cross-section

Definitions

  • the embodiments of the subject matter disclosed herein generally relate to power generation systems and more particularly to Organic Rankine Cycle (ORC) systems.
  • ORC Organic Rankine Cycle
  • Rankine cycles use a working fluid in a closed cycle to gather heat from a heating source or a hot reservoir by generating a hot gaseous stream that expands through a turbine to generate power.
  • the expanded stream is condensed in a condenser by transferring the heat to a cold reservoir.
  • the working fluid in a Rankine cycle follows a closed loop and is re-used constantly.
  • a system for power generation using a Rankine cycle is shown in FIG. 1 .
  • These systems for power generation can be described based on the power generated as primary power generation and secondary power generation systems. Additionally, secondary power generation systems tend to use the waste heat, e.g., hot exhaust gases, from the primary power generation system to improve overall system efficiency.
  • the power generation using the Rankine cycle is traditionally used as a secondary power generation system.
  • the power generation system 100 includes a heat exchanger 2 , or in some cases a boiler, a turbine 4 , a condenser 6 and a pump 8 .
  • a heat exchanger 2 or in some cases a boiler, a turbine 4 , a condenser 6 and a pump 8 .
  • an external heat source 10 e.g., hot flue gases
  • heats the heat exchanger 2 This causes the received pressurized liquid medium 12 to turn into a pressurized vapor 14 which flows to the turbine/generator 4 .
  • the turbine 4 receives the pressurized vapor stream 14 and can generate power 16 by, for example, rotating a mechanical shaft (not shown) as the pressurized vapor 14 expands inside the turbine 4 .
  • the expanded lower pressure vapor stream 18 then enters a condenser 6 which condenses the expanded lower pressure vapor stream 18 into a lower pressure liquid stream 20 .
  • the lower pressure liquid stream 20 then enters a pump 8 which both generates the higher pressure liquid stream 12 and keeps the closed loop system flowing.
  • the higher pressure liquid stream 12 then is pumped to the heat exchanger 2 to continue this process.
  • ORC organic rankine cycle
  • ORCs systems have been deployed as retrofits for small-scale and medium-scale gas turbines, to capture waste heat from the hot flue gas stream generated by an engine. These systems may generate up to an additional 20% power on top of the engine's baseline output, i.e., ORC systems are typically used in secondary power generation systems.
  • This ORC working fluid is typically a hydrocarbon with a boiling temperature slightly above the International Organization for Standardization's baseline for atmospheric pressure.
  • a currently used method for limiting the surface temperature of the heat exchanging surfaces in an evaporator which contains the ORC working fluids is to introduce an intermediate thermo-oil loop into the heat exchange system, i.e., to avoid the ORC liquid circulating through the exhaust stack of the gas turbine.
  • ORC systems when exposed directly to hot gasses, is their potential flammability. If a leak were to occur in a system using the ORC fluids, and the ORC fluid were to leak into the hot exhaust gas stream, e.g., the hot flue gas, combustion and/or an explosion could occur which could potentially be of a catastrophic nature to the power generation system and/or power plant.
  • a currently used method for both limiting the surface temperature of the heat exchanging surfaces in an evaporator which contains the ORC working fluids and reducing the risk of explosion is to introduce the intermediate thermo-oil loop into the heat exchange system, which separates the ORC fluid from the exhaust stack as discussed next.
  • the intermediate thermo-oil loop can be used between the hot flue gas and the vaporizable ORC fluid.
  • the intermediate thermo-oil loop is used as an intermediate heat exchanger, i.e., heat is transferred from the hot flue gas to the oil, which is in its own closed loop system, and then from the oil to the ORC fluid using a separate heat exchanger. Separating the ORC fluid from direct exposure to the hot flue gas can protect the ORC fluid from degradation and decomposition.
  • the oil used in the intermediate thermo-oil loop is flammable, this oil is generally less flammable than ORC working fluids. However, this thermal oil system takes additional physical space and can represent up to one quarter of the cost of an ORC system.
  • the system includes: a heat exchanger configured to be mounted inside an exhaust stack that guides hot flue gases and having an inlet and an outlet, the heat exchanger being configured to receive a liquid stream of a first fluid through the inlet and to generate a vapor stream of the first fluid and the heat exchanger is configured to include a double walled pipe, wherein the first fluid is disposed within an inner wall of the double walled pipe and a second fluid is disposed between the inner wall and an outer wall of the double walled pipe; an expander fluidly connected to the outlet of the heat exchanger and configured to expand the vapor stream of the first fluid, to generate power; a condenser fluidly connected to an outlet of the expander and configured to receive and condense an expanded vapor stream; and a pump fluidly connected to an outlet of the condenser and configured to receive the liquid stream of the first fluid, to pressurize the liquid stream of the first fluid and to circulate the
  • an Organic Rankine Cycle (ORC) fluid in a power generation system includes: transferring heat from a flue gas in an exhaust stack through a first wall of a heat exchanger to a heat pipe medium which changes a first phase of the heat pipe medium from a liquid phase to a gaseous phase inside a compartment of the heat exchanger; and vaporizing the ORC fluid when transferring heat from the heat pipe medium in the gaseous phase through a second wall to the ORC fluid which is contained inside the heat exchanger within the exhaust stack which changes a second phase of the heat pipe medium from the gaseous phase to the liquid phase, wherein the second wall is provided inside the first wall.
  • ORC Organic Rankine Cycle
  • the heat exchanger includes: a first pipe configured to receive a heat pipe fluid and further includes a second pipe, wherein a volume between the first pipe and the second pipe is hermetically sealed and is divided into compartments which are bound by an inner wall of the first pipe, an outer wall of the second pipe and separating walls between the compartments; the second pipe configured to receive an Organic Rankine Cycle (ORC) fluid; and the separating walls configured to link the first pipe to the second pipe, the heat exchanger configured to receive heat from the hot flue gases and configured to receive a liquid stream of the ORC fluid through an inlet and to generate a vapor stream of the ORC fluid through an outlet.
  • ORC Organic Rankine Cycle
  • FIG. 1 depicts a conventional Rankine Cycle
  • FIG. 2 illustrates a heat exchanger which uses an organic fluid disposed within an exhaust stack according to exemplary embodiments
  • FIG. 3 shows a double walled pipe according to exemplary embodiments
  • FIG. 4 illustrates a partial cross section of the double walled pipe of FIG. 3 with compartments according to exemplary embodiments
  • FIG. 5 shows a view of the double walled pipe with toroid compartments according to exemplary embodiments
  • FIG. 6 is a flowchart for a method for heat exchange according to exemplary embodiments
  • FIG. 7 illustrates exhaust paths according to exemplary embodiments.
  • FIG. 8 shows a flowchart for a method for vaporizing an ORC fluid according to exemplary embodiments.
  • a Rankine cycle can be used in secondary power generation systems to use some of the wasted energy from the hot exhaust gases of the primary power generation systems.
  • a primary system produces the bulk of the energy while also wasting energy.
  • a secondary system can be used to capture a portion of the wasted energy from the primary system.
  • An Organic Rankine Cycle (ORC) can be used in these power generation systems depending upon system temperatures and other specifics of the power generation systems. According to exemplary embodiments, ORCs can be used for small to mid-sized gas turbine power generation systems to capture additional heat/energy from the hot flue gas which may be released directly to the atmosphere.
  • heat can be introduced into the cycle through a heat exchanger 2 or some similar process, e.g., an evaporator or boiler.
  • Previous ORC systems have used an intermediate thermo-oil loop system to transfer heat from the hot flue gases to the ORC working fluid. In these cases the ORC system is outside of the path of the hot flue gases and located outside of the stack.
  • a more direct approach for heat exchange can be used which removes the need for thermo-oil loop and locates the heat exchanger for the ORC system in the exhaust stack in contact with the hot flue gases, e.g., temperatures between 350 degrees Celsius and 600 degrees Celsius, which can be found in electrical power generation systems.
  • temperatures and temperature ranges may be used.
  • heat exchanging coils 202 can wind in a serpentine manner through a stack 204 , or equivalent waste heat exhaust structure, as shown in FIG. 2 .
  • the pressurized liquid ORC fluid 12 enters from an inlet side into the heat exchanger 200 .
  • This working fluid may enter into the cooler side of the heat exchanger 200 and travel through the heat exchanging coils 202 and exit from the heat exchanger 200 from the hotter side, e.g., closer to the heat source, as a pressurized vapor ORC fluid 14 at the outlet side.
  • the coils shown closer to arrow 206 are closer to the heat source (not shown).
  • Heat sources for ORCs include, but are not limited to, exhaust gases from combustion systems (power plants or industrial processes), hot liquid or gaseous streams from industrial processes, geothermal and solar thermal sources.
  • a double walled pipe (which can also be considered as a pipe within a pipe) can be used as the heat exchanging coils 202 in the heat exchanger 200 of the ORC system to protect the ORC working fluid from decomposition and degradation.
  • ORC fluid can degrade and/or decompose at localized temperatures of 300° C. or possibly average temperatures of 240° C. in larger volumes of the ORC fluid. This operating range is generally applicable to whichever hydrocarbon is used as the ORC fluid except for aromatic hydrocarbons, e.g., thiophene, which may be able to operate at higher temperatures.
  • the heat exchanging coil 202 of FIG. 2 can include a double walled pipe 300 with an outer wall 302 and an inner wall 306 .
  • a heat pipe fluid can be placed in the outer section 304 between the two walls and the ORC working medium is located in the inner section 308 , i.e., the volume constrained by the inner wall 306 .
  • This exemplary arrangement can allow a high temperature flue gas 206 , e.g., in the range of 350-600 degrees Celsius, to transfer heat to the heat pipe fluid in outer section 304 through the outer wall 302 .
  • the heat pipe fluid then transfers heat to the ORC fluid in the inner section 308 through inner wall 306 .
  • this heat exchange between the heat pipe fluid to the ORC fluid can be performed such that the temperature used, and potential temperature fluctuations, can be controlled such that the temperature of the ORC fluid stays below a degradation temperature while still allowing the ORC fluid to vaporize before leaving the heat exchanger 200 .
  • the heat pipe fluid selected needs to be, at the desired pressure, able to use the heat energy from the hot flue gases to change its phase from a liquid to a vapor.
  • the heat pipe fluid vapor then circulates toward the inner wall 306 , where the heat pipe fluid vapor is cooled, e.g., releases heat energy, and condenses into a heat pipe fluid liquid and circulates back toward the outer wall 302 .
  • the temperature of the heat pipe fluid remains relatively constant as the heat pipe fluid is capable to absorb large amounts of heat from the hot flue gases without increasing its temperature, due to the liquid to gas phase change.
  • various factors can be modified to achieve this effect. These factors can include, but are not limited to, exhaust gas temperature, pipe dimensions, heat exchanger size, stack size, heat pipe fluid, ORC fluid, internal pipe construction and pressure(s). For example, if the exhaust gas temperature is 200 degrees Celsius versus 500 degrees Celsius, different combinations of the above mentioned factors may be used to achieve the desired cost effective heat exchanger 200 . More details regarding these various factors are described in the exemplary embodiments below.
  • the heat pipe fluid may be hermetically sealed within section 304 .
  • the heat pipe fluid may be selected from various mediums which have some, or possibly all, of the following characteristics: being less flammable than the ORC fluid, capable to undergo a phase change to transfer heat at the desired temperature/pressure ratio, and be capable of self circulating within section 304 .
  • Examples of a heat pipe fluid may include water, sodium, thermal oil and silicon-based thermal oil.
  • the ORC fluid may be a hydrocarbon, such as, pentane, propane, cyclohexane, cyclopentane and butane or a fluorohydrocarbon such as R-245fa, a ketone such as acetone or an aromatic such as toluene or thiophene.
  • a hydrocarbon such as, pentane, propane, cyclohexane, cyclopentane and butane
  • a fluorohydrocarbon such as R-245fa
  • a ketone such as acetone
  • an aromatic such as toluene or thiophene.
  • FIG. 4 shows a partial cross section of the double walled pipe 300 between the outer wall 302 and the inner wall 306 .
  • FIG. 5 shows a view of the double walled pipe 300 with a plurality of toroid shaped compartments 406 .
  • the outer section 304 (extending the length of the outer pipe) located between the outer wall 302 and the inner wall 306 can be further compartmentalized with a plurality of compartments 406 .
  • These compartments 406 contain the heat pipe fluid, e.g., water or sodium, in liquid and gaseous phases.
  • the heat pipe fluid can be under a higher pressure than the ORC working fluid in the inner area 308 .
  • Pressures used in both the piping section containing the ORC fluid and the piping section containing the heat pipe fluid which can be at different pressures, can be established to set the desired boiling point of the respective fluid.
  • spacers 404 can be used to assist in creating the compartments 406 as well as providing structural support for the heat exchanging coil 202 .
  • These compartments 406 may be, for example, toroids in shape, i.e., the spacers 404 can be circular spacer between the inner and outer pipe.
  • the piping used in the heat exchanger can be of varying sizes and shapes to promote the desired heat exchange and to allow for/assist in the desired self circulation of the heat pipe fluid, however the diameter of the outer wall 302 is larger than the diameter of the inner wall 306 .
  • the diameter of the inner most pipe may be in the range of about 12.77 mm-25.4 mm
  • the diameter of the outer pipe may be in the range of 25.4 mm-50.8 mm.
  • the spacers 404 which connect/support the inner wall 306 to the outer wall 302 may have a length in the range of 5 mm-25.4 mm with a potential separation of up to 152.4 mm between each spacer.
  • other dimensions can be used.
  • a capillary structure e.g., a wire mesh capillary structure
  • the capillary tubes are configured to increase the heat pipe fluid in its liquid phase brought into contact with the heated surface.
  • compartment 406 is bounded by spacers 404 , inner wall 306 and outer wall 302 . Additionally, some of the spacers 404 may be configured to allow fluid communication between selected adjacent compartments.
  • Heat exchange from the hot exhaust gas to the ORC fluid can be realized through a series of exemplary steps as shown in the flowchart of FIG. 6 .
  • a phase change, e.g., vaporization, of the heat pipe fluid occurs on the inner surface of the outer wall 302 in step 604 .
  • the vaporized heat pipe fluid flows toward the inner wall 306 in step 606 .
  • Condensation of the heat pipe fluid occurs on the outer surface of the inner wall 306 in step 608 .
  • convection (if preheating or superheating) or a phase change (if boiling) of the ORC fluid occurs on or near the inner wall 306 in step 610 .
  • Continuous back stream of the liquid heat pipe fluid towards the inner surface of the outer wall 302 then occurs in compartment 404 (in part via capillaries on the heat exchanging surfaces and the spacers 404 ) in step 612 .
  • evaporation and condensation of the heat pipe fluid does not need to occur, instead buoyancy-driven self circulation can occur without the driving mechanisms of evaporation and condensation, as thermal differences within the compartment can drive self circulation which still results in the desired heat exchange occurring with the ORC fluid.
  • the double walled pipe configuration can improve the safety in power generation systems.
  • the heat pipe fluid in the outer section is at a higher pressure than the ORC fluid in the inner section. In this case, if a leak occurred between the inner and outer sections of the double walled pipe the ORC fluid would not get into the exhaust stack to become a fire hazard. Sensors can be used to monitor a pressure of the heat pipe fluid such that if a leak were to occur it could be detected and allow the system to be shutdown. Similarly, if a leak were to occur that allowed the heat pipe fluid to enter the exhaust stack, the pressure loss could be detected and again allow for a shutdown of the system. Additionally, heat pipe fluids can be chosen which are inflammable or significantly less flammable than the ORC fluid.
  • this double walled pipe can be used in various heat exchanger designs, such as, for example, shell, tube and plate heat exchangers. Additionally, multiple double walled pipes may be used in parallel configurations.
  • an ORC system in lower temperature applications, can be placed in the path of the exhaust gases without the use of a double walled pipe. In this case care is to be taken to avoid allowing the ORC fluid to leak into the path of the exhaust gases.
  • low level leakage may occur which is difficult to detect. This low level leakage (very low rate leakage of the ORC fluid) can be of a concern when the system is not in operation for extended periods of time.
  • a buildup of the ORC fluid in the general area of the heat exchanger may occur since no flue gases are ventilating out past the heat exchanger.
  • ventilation systems can be put in place to reduce and/or remove this risk as shown in FIG. 7 .
  • the hot exhaust gas follows a path from the heat source through over the heat exchanger coils 702 and out an exhaust stack 714 as shown by directional arrow 704 .
  • a baffle 706 is placed in a closed position A such that the only flow path available is the flow path shown by directional arrow 704 .
  • the exhaust follows the path designated by directional arrow 708 , and flows directly out to atmosphere. To make this occur, the baffle 706 is place in an open position B such that the only flow path available is the flow path shown by directional arrow 708 .
  • baffle 710 is opened which allows air to enter the stack at this point and flush the area around the heat exchanger coils 702 such that no appreciable amount of combustible ORC fluids can stay in the area.
  • the path of the flushing air is shown by the directional arrow path 712 .
  • baffle 710 is in a closed position C.
  • various circulating methods can be used to introduce this air into the stack, e.g., fans.
  • the controls for opening and closing the baffles 706 and 710 may be interlinked or not as desired.
  • the heat exchanger coils 702 may be of the double walled pipe design described above.
  • a method for vaporizing an ORC fluid in a power generation system includes: transferring heat from a flue gas in an exhaust stack through a first wall of a heat exchanger to a heat pipe medium in step 802 ; changing a first phase of said heat pipe medium from a liquid phase to a gaseous phase inside a compartment of said heat exchanger in step 804 ; transferring heat from said heat pipe medium in said gaseous phase through a second wall to said ORC fluid which is contained inside said heat exchanger within said exhaust stack in step 806 ; changing a second phase of said heat pipe medium from said gaseous phase to said liquid phase in step 808 ; and vaporizing said ORC fluid in step 810 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US12/609,348 2009-10-30 2009-10-30 Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method Abandoned US20110100009A1 (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US12/609,348 US20110100009A1 (en) 2009-10-30 2009-10-30 Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method
CN2010800600551A CN103228912A (zh) 2009-10-30 2010-10-27 在有机兰金循环系统中用于直接蒸发的热交换器和方法
CA2779074A CA2779074A1 (en) 2009-10-30 2010-10-27 Heat exchanger for direct evaporation in organic rankine cycle systems and method
PCT/EP2010/066282 WO2011051353A2 (en) 2009-10-30 2010-10-27 Heat exchanger for direct evaporation in organic rankine cycle systems and method
BR112012010150A BR112012010150A2 (pt) 2009-10-30 2010-10-27 sistema para gerar energia usando um ciclo organico rankine, metodo para evaporar um ciclo organico rankine em um sistema de geração de energia e cambiador termico
AU2010311522A AU2010311522A1 (en) 2009-10-30 2010-10-27 Heat exchanger for direct evaporation in Organic Rankine Cycle systems and method
EP10770842.2A EP2780558A2 (en) 2009-10-30 2010-10-27 Heat exchanger for direct evaporation in organic rankine cycle systems and method
MX2012005081A MX2012005081A (es) 2009-10-30 2010-10-27 Intercambiador de calor para evaporacion directa en sistemas de ciclo rankine organico y metodo.
RU2012116621/06A RU2012116621A (ru) 2009-10-30 2010-10-27 Теплообменник для прямого испарения в системах, использующих органический цикл ренкина, и способ его применения
PE2012000599A PE20130026A1 (es) 2009-10-30 2010-10-27 Intercambiador de calor para evaporacion directa en sistemas y metodo de ciclo organico de rankine
CL2012001098A CL2012001098A1 (es) 2009-10-30 2012-04-27 Sistema para la generación de potencia ciclo rankine orgánico, posee un intercambiador de calor que tiene una tubería de doble pared, con un primer fluido dentro de una pared interior de la tubería, y un segundo fluido entre la pared interior y una exterior de la tubería, extensor, un condensador y una bomba; método asociado; e intercambiador de calor.

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Application Number Priority Date Filing Date Title
US12/609,348 US20110100009A1 (en) 2009-10-30 2009-10-30 Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method

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US20110100009A1 true US20110100009A1 (en) 2011-05-05

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US12/609,348 Abandoned US20110100009A1 (en) 2009-10-30 2009-10-30 Heat Exchanger for Direct Evaporation in Organic Rankine Cycle Systems and Method

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US (1) US20110100009A1 (zh)
EP (1) EP2780558A2 (zh)
CN (1) CN103228912A (zh)
AU (1) AU2010311522A1 (zh)
BR (1) BR112012010150A2 (zh)
CA (1) CA2779074A1 (zh)
CL (1) CL2012001098A1 (zh)
MX (1) MX2012005081A (zh)
PE (1) PE20130026A1 (zh)
RU (1) RU2012116621A (zh)
WO (1) WO2011051353A2 (zh)

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US20140026575A1 (en) * 2011-02-18 2014-01-30 Exergy S.P.A. Apparatus and process for generation of energy by organic rankine cycle
US20140099184A1 (en) * 2011-03-29 2014-04-10 Antonio Asti Sealing systems for turboexpanders for use in organic rankine cycles
EP2846092A3 (de) * 2013-09-07 2015-03-25 Messer Austria GmbH Brenner
US9039923B2 (en) 2012-02-14 2015-05-26 United Technologies Corporation Composition of zeotropic mixtures having predefined temperature glide
EP2913487A4 (en) * 2012-10-29 2015-10-14 Panasonic Ip Man Co Ltd POWER GENERATING DEVICE AND COGENERATION SYSTEM
US20160214465A1 (en) * 2015-01-23 2016-07-28 Ford Global Technologies, Llc Thermodynamic system in a vehicle
WO2017081131A1 (en) 2015-11-13 2017-05-18 Shell Internationale Research Maatschappij B.V. Method of generating power using a combined cycle
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CN103228912A (zh) 2013-07-31
CL2012001098A1 (es) 2012-12-28
MX2012005081A (es) 2012-10-26
RU2012116621A (ru) 2013-12-10
AU2010311522A1 (en) 2012-05-24
WO2011051353A2 (en) 2011-05-05
BR112012010150A2 (pt) 2019-09-24

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