US20110094227A1 - Waste Heat Recovery System - Google Patents
Waste Heat Recovery System Download PDFInfo
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- US20110094227A1 US20110094227A1 US12/606,571 US60657109A US2011094227A1 US 20110094227 A1 US20110094227 A1 US 20110094227A1 US 60657109 A US60657109 A US 60657109A US 2011094227 A1 US2011094227 A1 US 2011094227A1
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- Prior art keywords
- working fluid
- exhaust gas
- recovery system
- heat
- waste heat
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- 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
- F01K23/065—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 the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
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- 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
Definitions
- the subject matter disclosed herein relates to waste heat recovery systems, and more specifically, to systems for recovering waste heat from exhaust gas.
- power generation systems such as combustion engines, may produce exhaust gas in addition to power.
- a bottoming Rankine cycle may be employed to recover waste heat from the exhaust gas as well as from other heat sources, such as the cooling system.
- the power output of the bottoming Rankine cycle may generally increase the more that the exhaust gas is cooled.
- the temperature to which the exhaust gas may be cooled may be limited by corrosive elements in the exhaust gas.
- exhaust gas may include sulfur that may mix with water upon condensation of the exhaust gas to produce sulfuric acid. Accordingly, to inhibit corrosion in certain bottoming Rankine cycles, the exhaust gas may not be cooled below the dew point and/or to temperatures that may produce condensation of the exhaust gas.
- a waste heat recovery system includes an exhaust system that generates exhaust gas and a Rankine cycle system for circulating a working fluid.
- the Rankine cycle system includes an evaporator configured to transfer sensible heat from the exhaust gas to the working fluid to produce cooled exhaust gas and an economizer configured to transfer latent heat from the exhaust gas to the working fluid.
- the economizer includes a carbon steel heat exchanger with a corrosion resistant coating.
- a waste heat recovery system in another embodiment, includes an exhaust system that generates hot exhaust gas, a first Rankine cycle system for circulating a first working fluid, a second Rankine cycle system for circulating a second working fluid and configured to transfer heat from an engine heat source to the second working fluid, and a shared heat exchanger common to the first and second Rankine cycle systems and configured to transfer heat from the first working fluid to the second working fluid to condense the first working fluid and to evaporate the second working fluid.
- the first Rankine cycle system includes an evaporator configured to transfer sensible heat from the hot exhaust gas to the first working fluid to produce cooled exhaust gas and an economizer configured to transfer latent heat from the cooled exhaust gas to the working fluid.
- the economizer includes a carbon steel heat exchanger with a corrosion resistant coating.
- a waste heat recovery system in yet another embodiment, includes an exhaust system that generates hot exhaust gas and a Rankine cycle system for circulating a working fluid.
- the Rankine cycle system includes an evaporator configured to transfer heat from the hot exhaust gas to the working fluid to at least partially vaporize the working fluid and to produce cooled exhaust gas, a condenser configured to receive and to condense the vaporized working fluid, and an economizer configured to transfer heat from the cooled exhaust gas to the condensed working fluid to at least partially condense the cooled exhaust gas.
- the economizer includes a carbon steel heat exchanger with a silica coating.
- FIG. 1 is a diagrammatical representation of an embodiment of a waste heat recovery system
- FIG. 2 is a cross-sectional view of a portion of the economizer shown in FIG. 1 .
- a waste heat recovery system may include a pair of organic Rankine cycle (ORC) systems arranged in a cascade configuration.
- the high temperature ORC system may recover waste heat from exhaust gas
- the low temperature ORC system may recover waste heat from another heat source, such as an engine cooling system.
- the high temperature ORC system may include a working fluid economizer designed to recover latent heat from condensing water in the exhaust gas in addition to sensible heat.
- the economizer may allow the exhaust gas to be cooled below the dew point of the exhaust gas, which may increase the power output of the waste heat recovery system.
- the economizer may be constructed of carbon steel with a corrosion resistant coating. The coating may facilitate decreased manufacturing and/or capital costs by allowing low cost carbon steel to be employed rather than more expensive stainless steel.
- FIG. 1 depicts a waste heat recovery system 10 that may employ a carbon steel economizer with a corrosion resistant coating.
- the waste heat recovery system 10 may recover heat from a heat generation system, such as an engine 12 .
- the engine 12 may be part of a power generation system and may run on fuels such as biogas, natural gas, landfill gas, coal mine gas, sewage gas, or combustible industrial waste gases, among others.
- fuels such as biogas, natural gas, landfill gas, coal mine gas, sewage gas, or combustible industrial waste gases, among others.
- the engine 12 is depicted as a combustion engine, in other embodiments, any suitable heat generation system that produces exhaust gas may be employed, such as a gas turbine, micro-turbine, reciprocating engine, or geothermal, solar thermal, industrial, or residential heat sources.
- the waste heat recovery system 10 includes a pair of ORC systems 14 and 16 arranged in a cascade configuration with a shared heat exchanger 18 that transfers heat between the ORC systems 14 and 16 .
- Each ORC system 14 and 16 may include a closed loop that circulates a working fluid through a Rankine cycle within the ORC system 14 and 16 .
- the high temperature ORC system 14 may circulate a first working fluid
- the low temperature ORC system 16 may circulate a second working fluid.
- the first and second working fluids may include organic working fluids.
- steam may be employed as the first and/or second working fluid.
- the first working fluid may have a condensation temperature above the boiling point of the second working fluid.
- the first working fluid may include cyclohexane, cyclopentane, thiophene, ketones, aromatics, or combinations thereof.
- the second working fluid may include propane, butane, fluoro-propane, pentafluoro-butane, pentafluoro-polyether, oil, or combinations thereof, among others.
- the first and/or second organic working fluids may include a binary fluid such as cyclohexane-propane, cyclohexane-butane, cyclopentane-butane, or cyclopentane-pentafluoro propane, among others.
- Each ORC system 14 and 16 may be coupled to a generator 20 and 22 that converts heat recovered from the engine 12 to electricity. Specifically, the high temperature ORC system 14 may recover heat from an exhaust system 24 of the engine 12 , and the low temperature ORC system 16 may recover heat from another heat source of the engine 12 , such as the engine cooling system 26 .
- the first ORC system 14 may recover heat from the exhaust system 24 through a heat exchanger 28 and an economizer 30 .
- the heat exchanger 28 and the economizer 30 may allow the first ORC system 14 to recover heat from the exhaust gas at two different temperatures.
- the heat exchanger 28 may transfer heat from the hot exhaust gas existing the exhaust system 24 to the first ORC system 14 to produce cooled exhaust gas.
- the cooled exhaust gas may then be direct to the economizer 30 , which transfers heat from the cooled exhaust gas to the first ORC system 14 .
- the exhaust gas may exit the exhaust system at a temperature of approximately 400 to 500° C., may be cooled to a temperature of approximately 150 to 200° C. in the heat exchanger 28 , and may be cooled to a temperature of approximately 100 to 110° C. in the economizer 30 . More specifically, the exhaust gas may exit the exhaust system at a temperature of approximately 427° C., may be cooled to a temperature of approximately 180° C. by the heat exchanger 28 , and may be cooled to a temperature of approximately 104° C. by the economizer 30 . In yet another example, the heat exchanger 28 may reduce the temperature of the exhaust gas by approximately 200 to 300° C., and the economizer 30 may reduce the temperature of the exhaust gas by approximately 80 to 90° C.
- the heat exchanger 28 may recover primarily sensible heat from the exhaust gas, and the economizer 30 may recovery primarily latent heat from the exhaust gas.
- the exhaust gas flowing through the heat exchanger 28 may be cooled to reduce its temperature while the exhaust gas remains in the gaseous phase, while the exhaust gas flowing through the economizer 30 may be all or partially condensed to produce liquid phase exhaust gas.
- the heat exchanger 28 may transfer heat from the exhaust gas to the first ORC system 14 through a thermal oil loop 32 in heat transfer communication with the first working fluid. Specifically, as the exhaust gas flows through the heat exchanger 28 , the exhaust gas may heat the thermal oil flowing within the thermal oil loop 32 . For example, in certain embodiments, the exhaust gas may heat the thermal oil from a temperature of approximately 160° C. to a temperature of approximately 280° C. A pump 34 may circulate the thermal oil within the thermal oil loop 32 , and the heated thermal oil exiting the heat exchanger 28 may enter an evaporator 36 of the first ORC system 14 . As the heated oil flows through the evaporator 36 , the heated thermal oil may transfer heat to the first working fluid flowing within the first ORC system 14 . In other embodiments, the thermal oil loop 32 may be replaced by another closed loop circulating any suitable type of heat transfer fluid for transferring heat from the exhaust gas to the first working fluid.
- the first working fluid may absorb heat from the thermal oil and may be evaporated and/or superheated. In certain embodiments, the first working fluid may be heated to a temperature of approximately 225° C. Upon exiting the evaporator 36 , the vapor phase working fluid may then flow to an expander 38 where the fluid may be expanded to drive the generator 20 .
- the expander may be a radial expander, axial expander, impulse type expander, or high temperature screw type expander, among others.
- the first working fluid may be expanded to produce a low temperature and pressure vapor.
- the first working fluid may enter the shared heat exchanger 18 as a low temperature and pressure vapor.
- the first working fluid may transfer heat to the second working fluid flowing through the shared heat exchanger 18 within the second ORC system 16 .
- the first working fluid may transfer heat to the second working fluid and condense into a liquid.
- the liquid phase first working fluid may then flow through a pump 40 that circulates the first working fluid within the first ORC system 14 .
- the first working fluid may flow through the economizer 30 where the first working fluid may be heated by the exhaust gas flowing through the economizer 30 .
- the exhaust gas flowing through the economizer 30 may be partially or completely condensed to transfer latent heat to the first working fluid.
- the heat from the exhaust gas may be transferred to the first working fluid to preheat the first working fluid before the first working fluid enters the evaporator 36 .
- the preheating within the economizer 30 may improve the efficiency of the waste heat recovery system 10 by allowing additional heat to be extracted from the exhaust gas.
- the first working fluid may then return to the evaporator 36 where the cycle may begin again.
- the first working fluid flowing within the first ORC system 14 may transfer heat to the second working fluid flowing within the second ORC system 16 .
- the second working fluid may absorb heat from the first working fluid and may evaporate.
- the vapor phase second working fluid may then enter an expander 44 and expand to drive the generator 22 .
- the expander 44 may be a radial expander, axial expander, impulse type expander, or high temperature screw type expander, among others.
- the second working fluid may exit the expander 44 as a low temperature and pressure vapor.
- the vapor phase second working fluid may flow through an air-to-liquid heat exchanger 46 where the second working fluid may be condensed by air flowing across the air-to-liquid heat exchanger 46 .
- the air-to liquid-heat exchanger may include a motor with a fan that draws ambient air across the air-to-liquid heat exchanger.
- the condensed second working fluid may then enter a pump 48 that circulates the second working fluid within the second ORC system 16 .
- the second working fluid may flow through a preheater 42 that may heat the second working fluid.
- the preheater 42 may circulate a fluid from a heat source within the engine 12 .
- the preheater 42 may circulate heated cooling fluid from the cooling system 26 of the engine 12 .
- the temperature of the fluid entering the preheater 42 from the engine 12 may generally be lower than the temperature of the exhaust gas entering the heat exchanger 28 and the economizer 30 .
- the fluid from the engine 12 may enter the preheater 42 at a temperature of approximately 80 to 100° C.
- the fluid may transfer heat to the second working fluid to cool the fluid from the engine 12 .
- the fluid from the engine 12 may exit the preheater 42 at a temperature of approximately 30° C.
- the cooled fluid may then be returned to the engine 12 .
- the preheater may receive fluid from one or more heat sources within the engine 12 instead of, or in addition to, the cooling system 26 .
- the pre-heater 42 may receive fluid from gas turbines and/or intercoolers.
- the preheater 42 may transfer heat from the engine 12 to the second working fluid.
- the second working fluid may partially evaporate to form a liquid-vapor mixture.
- the second working fluid may remain in a liquid phase.
- the second working fluid may return to the shared heat exchanger 18 where the cycle may begin again.
- the cascade arrangement of the first and second ORC systems 14 and 16 may generally allow an increased heat recovery over a larger temperature range.
- the first ORC system 14 may allow recovery of heat in higher temperature ranges, such as approximately 400 to 500° C. while the second ORC system 16 facilitates recovery of heat in lower temperature range, such as approximately 50 to 100° C.
- the inclusion of the economizer 30 in the first ORC system 14 may allow additional heat in an intermediate temperature range, such as approximately 150 to 250° C., to be recovered from the exhaust gas. For example, rather than recovering heat solely through the heat exchanger 28 , additional heat in an intermediate temperature range also may be recovered through the use of the economizer 30 .
- the additional heat percent when compared to ORC systems without an economizer may be constructed of carbon steel and coated with a corrosion resistant coating.
- the coating may allow carbon steel, rather than stainless steel, to be employed for the economizer, which may reduce manufacturing and/or capital costs.
- the waste heat recovery system 10 may include additional equipment such as pumps, valves, control circuitry, pressure and/or temperature transducers or switches, among others.
- additional equipment such as pumps, valves, control circuitry, pressure and/or temperature transducers or switches, among others may be included within the waste heat recovery system 10 .
- the types of equipment included within the waste heat recovery system 10 may vary.
- the heat exchangers 18 , 28 , 30 , 36 , and 42 may include shell and tube heat exchangers, fin and tube heat exchangers, plate heat exchangers, plate and shell heat exchangers, or combinations thereof, among others.
- FIG. 2 is a cross-sectional view taken through the economizer 30 illustrating a surface 50 of the economizer that includes a corrosion resistant coating 52 .
- the coating 52 may be applied to surfaces 50 of the economizer that are exposed to the exhaust gas.
- the coating 52 may be applied to the exterior surfaces of the tubes and the interior surface of the shell.
- the coating 52 may be applied to the external surfaces of the tubes, to the fins, and to the interior surfaces of the enclosure surrounding the fin and tube heat exchanger.
- the coating 52 may be applied to the interior surfaces of the tubes.
- the coating 52 may be designed to inhibit corrosion that may occur during condensation of the exhaust gas.
- the coating 52 may include a silicon dioxide (silica) coating that provides a barrier layer to inhibit corrosion to the surface 50 of the economizer 30 .
- the coating 52 may inhibit corrosion by contaminants in the exhaust gas, such as sulfur that may react with water upon condensation to form sulfuric acid that may corrode and/or pit the surface 50 .
- the coating 52 may exhibit hydrophobic, oleophobic, and/or antistatic properties.
- the coating 52 may include a nanoparticle coating of colloidal silica with particles ranging in size from approximately one to five nanometers. However, in other embodiments, the size of the nanoparticles may vary.
- the coating may be applied by any suitable manufacturing process, such as spray coating, dipping, or flooding.
- the external surfaces of the tubes and/or fins may be spray coated to apply the coating.
- the coating may then be cured upon startup of the engine 12 or through a separate curing step where the coating 52 may be exposed to high temperatures.
- the heat exchanger may be flooded with the coating and then drained to allow the coating to adhere to surfaces of the economizer 30 .
- the coating 52 also may be applied to other heat exchangers within the waste heat recovery system 10 .
- the coating 52 may be applied to surfaces of the heat exchanger 28 .
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Abstract
In one embodiment, a waste heat recovery system includes a Rankine cycle system that circulates a working fluid that absorbs heat from exhaust gas. The Rankine cycle system includes an evaporator that may transfer sensible heat from the exhaust gas to the working fluid to produce cooled exhaust gas. The Rankine cycle system also includes an economizer that may transfer latent heat from the exhaust gas to the working fluid. The economizer is a carbon steel heat exchanger with a corrosion resistant coating.
Description
- The subject matter disclosed herein relates to waste heat recovery systems, and more specifically, to systems for recovering waste heat from exhaust gas.
- In general, power generation systems, such as combustion engines, may produce exhaust gas in addition to power. A bottoming Rankine cycle may be employed to recover waste heat from the exhaust gas as well as from other heat sources, such as the cooling system. The power output of the bottoming Rankine cycle may generally increase the more that the exhaust gas is cooled. However, the temperature to which the exhaust gas may be cooled may be limited by corrosive elements in the exhaust gas. For example, exhaust gas may include sulfur that may mix with water upon condensation of the exhaust gas to produce sulfuric acid. Accordingly, to inhibit corrosion in certain bottoming Rankine cycles, the exhaust gas may not be cooled below the dew point and/or to temperatures that may produce condensation of the exhaust gas.
- In one embodiment, a waste heat recovery system includes an exhaust system that generates exhaust gas and a Rankine cycle system for circulating a working fluid. The Rankine cycle system includes an evaporator configured to transfer sensible heat from the exhaust gas to the working fluid to produce cooled exhaust gas and an economizer configured to transfer latent heat from the exhaust gas to the working fluid. The economizer includes a carbon steel heat exchanger with a corrosion resistant coating.
- In another embodiment, a waste heat recovery system includes an exhaust system that generates hot exhaust gas, a first Rankine cycle system for circulating a first working fluid, a second Rankine cycle system for circulating a second working fluid and configured to transfer heat from an engine heat source to the second working fluid, and a shared heat exchanger common to the first and second Rankine cycle systems and configured to transfer heat from the first working fluid to the second working fluid to condense the first working fluid and to evaporate the second working fluid. The first Rankine cycle system includes an evaporator configured to transfer sensible heat from the hot exhaust gas to the first working fluid to produce cooled exhaust gas and an economizer configured to transfer latent heat from the cooled exhaust gas to the working fluid. The economizer includes a carbon steel heat exchanger with a corrosion resistant coating.
- In yet another embodiment, a waste heat recovery system includes an exhaust system that generates hot exhaust gas and a Rankine cycle system for circulating a working fluid. The Rankine cycle system includes an evaporator configured to transfer heat from the hot exhaust gas to the working fluid to at least partially vaporize the working fluid and to produce cooled exhaust gas, a condenser configured to receive and to condense the vaporized working fluid, and an economizer configured to transfer heat from the cooled exhaust gas to the condensed working fluid to at least partially condense the cooled exhaust gas. The economizer includes a carbon steel heat exchanger with a silica coating.
- These and other features, aspects, and advantages of the present invention will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
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FIG. 1 is a diagrammatical representation of an embodiment of a waste heat recovery system; and -
FIG. 2 is a cross-sectional view of a portion of the economizer shown inFIG. 1 . - One or more specific embodiments of the present invention will be described below. In an effort to provide a concise description of these embodiments, all features of an actual implementation may not be described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers' specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.
- When introducing elements of various embodiments of the present invention, the articles “a,” “an,” “the,” and “said” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements.
- The present disclosure is directed to techniques for recovering waste heat from exhaust gas. In accordance with certain embodiments, a waste heat recovery system may include a pair of organic Rankine cycle (ORC) systems arranged in a cascade configuration. The high temperature ORC system may recover waste heat from exhaust gas, and the low temperature ORC system may recover waste heat from another heat source, such as an engine cooling system. The high temperature ORC system may include a working fluid economizer designed to recover latent heat from condensing water in the exhaust gas in addition to sensible heat. Specifically, the economizer may allow the exhaust gas to be cooled below the dew point of the exhaust gas, which may increase the power output of the waste heat recovery system. To inhibit corrosion that may occur during condensation of the exhaust gas, the economizer may be constructed of carbon steel with a corrosion resistant coating. The coating may facilitate decreased manufacturing and/or capital costs by allowing low cost carbon steel to be employed rather than more expensive stainless steel.
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FIG. 1 depicts a wasteheat recovery system 10 that may employ a carbon steel economizer with a corrosion resistant coating. The wasteheat recovery system 10 may recover heat from a heat generation system, such as anengine 12. In certain embodiments, theengine 12 may be part of a power generation system and may run on fuels such as biogas, natural gas, landfill gas, coal mine gas, sewage gas, or combustible industrial waste gases, among others. Further, although theengine 12 is depicted as a combustion engine, in other embodiments, any suitable heat generation system that produces exhaust gas may be employed, such as a gas turbine, micro-turbine, reciprocating engine, or geothermal, solar thermal, industrial, or residential heat sources. - The waste
heat recovery system 10 includes a pair ofORC systems heat exchanger 18 that transfers heat between theORC systems ORC system ORC system temperature ORC system 14 may circulate a first working fluid, and the lowtemperature ORC system 16 may circulate a second working fluid. According to certain embodiments, the first and second working fluids may include organic working fluids. However, in other embodiments, steam may be employed as the first and/or second working fluid. Further, in certain embodiments, the first working fluid may have a condensation temperature above the boiling point of the second working fluid. According to certain embodiments, the first working fluid may include cyclohexane, cyclopentane, thiophene, ketones, aromatics, or combinations thereof. The second working fluid may include propane, butane, fluoro-propane, pentafluoro-butane, pentafluoro-polyether, oil, or combinations thereof, among others. Further, in certain embodiments, the first and/or second organic working fluids may include a binary fluid such as cyclohexane-propane, cyclohexane-butane, cyclopentane-butane, or cyclopentane-pentafluoro propane, among others. - Each
ORC system generator engine 12 to electricity. Specifically, the hightemperature ORC system 14 may recover heat from anexhaust system 24 of theengine 12, and the lowtemperature ORC system 16 may recover heat from another heat source of theengine 12, such as theengine cooling system 26. - The
first ORC system 14 may recover heat from theexhaust system 24 through aheat exchanger 28 and aneconomizer 30. Theheat exchanger 28 and theeconomizer 30 may allow thefirst ORC system 14 to recover heat from the exhaust gas at two different temperatures. Specifically, theheat exchanger 28 may transfer heat from the hot exhaust gas existing theexhaust system 24 to thefirst ORC system 14 to produce cooled exhaust gas. The cooled exhaust gas may then be direct to theeconomizer 30, which transfers heat from the cooled exhaust gas to thefirst ORC system 14. - In certain embodiments, the exhaust gas may exit the exhaust system at a temperature of approximately 400 to 500° C., may be cooled to a temperature of approximately 150 to 200° C. in the
heat exchanger 28, and may be cooled to a temperature of approximately 100 to 110° C. in theeconomizer 30. More specifically, the exhaust gas may exit the exhaust system at a temperature of approximately 427° C., may be cooled to a temperature of approximately 180° C. by theheat exchanger 28, and may be cooled to a temperature of approximately 104° C. by theeconomizer 30. In yet another example, theheat exchanger 28 may reduce the temperature of the exhaust gas by approximately 200 to 300° C., and theeconomizer 30 may reduce the temperature of the exhaust gas by approximately 80 to 90° C. - In certain embodiments, the
heat exchanger 28 may recover primarily sensible heat from the exhaust gas, and theeconomizer 30 may recovery primarily latent heat from the exhaust gas. In other words, the exhaust gas flowing through theheat exchanger 28 may be cooled to reduce its temperature while the exhaust gas remains in the gaseous phase, while the exhaust gas flowing through theeconomizer 30 may be all or partially condensed to produce liquid phase exhaust gas. - The
heat exchanger 28 may transfer heat from the exhaust gas to thefirst ORC system 14 through athermal oil loop 32 in heat transfer communication with the first working fluid. Specifically, as the exhaust gas flows through theheat exchanger 28, the exhaust gas may heat the thermal oil flowing within thethermal oil loop 32. For example, in certain embodiments, the exhaust gas may heat the thermal oil from a temperature of approximately 160° C. to a temperature of approximately 280°C. A pump 34 may circulate the thermal oil within thethermal oil loop 32, and the heated thermal oil exiting theheat exchanger 28 may enter anevaporator 36 of thefirst ORC system 14. As the heated oil flows through theevaporator 36, the heated thermal oil may transfer heat to the first working fluid flowing within thefirst ORC system 14. In other embodiments, thethermal oil loop 32 may be replaced by another closed loop circulating any suitable type of heat transfer fluid for transferring heat from the exhaust gas to the first working fluid. - Within the
evaporator 36, the first working fluid may absorb heat from the thermal oil and may be evaporated and/or superheated. In certain embodiments, the first working fluid may be heated to a temperature of approximately 225° C. Upon exiting theevaporator 36, the vapor phase working fluid may then flow to anexpander 38 where the fluid may be expanded to drive thegenerator 20. In certain embodiments, the expander may be a radial expander, axial expander, impulse type expander, or high temperature screw type expander, among others. Within theexpander 38, the first working fluid may be expanded to produce a low temperature and pressure vapor. - From the
expander 38, the first working fluid may enter the sharedheat exchanger 18 as a low temperature and pressure vapor. Within the sharedheat exchanger 18, the first working fluid may transfer heat to the second working fluid flowing through the sharedheat exchanger 18 within thesecond ORC system 16. Specifically, the first working fluid may transfer heat to the second working fluid and condense into a liquid. The liquid phase first working fluid may then flow through apump 40 that circulates the first working fluid within thefirst ORC system 14. - From the
pump 40, the first working fluid may flow through theeconomizer 30 where the first working fluid may be heated by the exhaust gas flowing through theeconomizer 30. As noted above, the exhaust gas flowing through theeconomizer 30 may be partially or completely condensed to transfer latent heat to the first working fluid. Within theeconomizer 30, the heat from the exhaust gas may be transferred to the first working fluid to preheat the first working fluid before the first working fluid enters theevaporator 36. In certain embodiments, the preheating within theeconomizer 30 may improve the efficiency of the wasteheat recovery system 10 by allowing additional heat to be extracted from the exhaust gas. The first working fluid may then return to theevaporator 36 where the cycle may begin again. - Through the shared
heat exchanger 18, the first working fluid flowing within thefirst ORC system 14 may transfer heat to the second working fluid flowing within thesecond ORC system 16. Specifically, as the second working fluid flows through the sharedheat exchanger 18, the second working fluid may absorb heat from the first working fluid and may evaporate. The vapor phase second working fluid may then enter an expander 44 and expand to drive thegenerator 22. In certain embodiments, the expander 44 may be a radial expander, axial expander, impulse type expander, or high temperature screw type expander, among others. The second working fluid may exit the expander 44 as a low temperature and pressure vapor. - From the expander 44, the vapor phase second working fluid may flow through an air-to-
liquid heat exchanger 46 where the second working fluid may be condensed by air flowing across the air-to-liquid heat exchanger 46. In certain embodiments, the air-to liquid-heat exchanger may include a motor with a fan that draws ambient air across the air-to-liquid heat exchanger. The condensed second working fluid may then enter apump 48 that circulates the second working fluid within thesecond ORC system 16. - From the
pump 48, the second working fluid may flow through apreheater 42 that may heat the second working fluid. Thepreheater 42 may circulate a fluid from a heat source within theengine 12. For example, thepreheater 42 may circulate heated cooling fluid from thecooling system 26 of theengine 12. The temperature of the fluid entering thepreheater 42 from theengine 12 may generally be lower than the temperature of the exhaust gas entering theheat exchanger 28 and theeconomizer 30. For example, in certain embodiments, the fluid from theengine 12 may enter thepreheater 42 at a temperature of approximately 80 to 100° C. Within thepreheater 42, the fluid may transfer heat to the second working fluid to cool the fluid from theengine 12. For example, in certain embodiments, the fluid from theengine 12 may exit thepreheater 42 at a temperature of approximately 30° C. The cooled fluid may then be returned to theengine 12. In other embodiments, the preheater may receive fluid from one or more heat sources within theengine 12 instead of, or in addition to, thecooling system 26. For example, the pre-heater 42 may receive fluid from gas turbines and/or intercoolers. - Regardless of the heat source, the
preheater 42 may transfer heat from theengine 12 to the second working fluid. In certain embodiments, the second working fluid may partially evaporate to form a liquid-vapor mixture. However, in other embodiments, the second working fluid may remain in a liquid phase. Upon exiting thepreheater 42, the second working fluid may return to the sharedheat exchanger 18 where the cycle may begin again. - The cascade arrangement of the first and
second ORC systems first ORC system 14 may allow recovery of heat in higher temperature ranges, such as approximately 400 to 500° C. while thesecond ORC system 16 facilitates recovery of heat in lower temperature range, such as approximately 50 to 100° C. Further, the inclusion of theeconomizer 30 in thefirst ORC system 14 may allow additional heat in an intermediate temperature range, such as approximately 150 to 250° C., to be recovered from the exhaust gas. For example, rather than recovering heat solely through theheat exchanger 28, additional heat in an intermediate temperature range also may be recovered through the use of theeconomizer 30. In certain embodiments, the additional heat percent when compared to ORC systems without an economizer. Further, as will be discussed below with respect toFIG. 2 , theeconomizer 30 may be constructed of carbon steel and coated with a corrosion resistant coating. The coating may allow carbon steel, rather than stainless steel, to be employed for the economizer, which may reduce manufacturing and/or capital costs. - As may be appreciated, additional equipment such as pumps, valves, control circuitry, pressure and/or temperature transducers or switches, among others may be included within the waste
heat recovery system 10. Furthermore, the types of equipment included within the wasteheat recovery system 10 may vary. For example, according to certain embodiments, theheat exchangers -
FIG. 2 is a cross-sectional view taken through theeconomizer 30 illustrating asurface 50 of the economizer that includes a corrosionresistant coating 52. In general, thecoating 52 may be applied tosurfaces 50 of the economizer that are exposed to the exhaust gas. For example, in a shell and tube heat exchanger where the exhaust gas flows through the shell portion, thecoating 52 may be applied to the exterior surfaces of the tubes and the interior surface of the shell. In another example where the exhaust gas flows across tubes circulating a working fluid within a fin and tube heat exchanger, thecoating 52 may be applied to the external surfaces of the tubes, to the fins, and to the interior surfaces of the enclosure surrounding the fin and tube heat exchanger. In a further example where the exhaust gas flows through the tubes of a shell and tube heat exchanger, thecoating 52 may be applied to the interior surfaces of the tubes. - The
coating 52 may be designed to inhibit corrosion that may occur during condensation of the exhaust gas. Thecoating 52 may include a silicon dioxide (silica) coating that provides a barrier layer to inhibit corrosion to thesurface 50 of theeconomizer 30. In certain embodiments, thecoating 52 may inhibit corrosion by contaminants in the exhaust gas, such as sulfur that may react with water upon condensation to form sulfuric acid that may corrode and/or pit thesurface 50. Further, in addition to corrosion resistant properties, thecoating 52 may exhibit hydrophobic, oleophobic, and/or antistatic properties. According to certain embodiments, thecoating 52 may include a nanoparticle coating of colloidal silica with particles ranging in size from approximately one to five nanometers. However, in other embodiments, the size of the nanoparticles may vary. - The coating may be applied by any suitable manufacturing process, such as spray coating, dipping, or flooding. For example, in certain embodiments, the external surfaces of the tubes and/or fins may be spray coated to apply the coating. The coating may then be cured upon startup of the
engine 12 or through a separate curing step where thecoating 52 may be exposed to high temperatures. In another example, the heat exchanger may be flooded with the coating and then drained to allow the coating to adhere to surfaces of theeconomizer 30. Further, in other embodiments, thecoating 52 also may be applied to other heat exchangers within the wasteheat recovery system 10. For example, thecoating 52 may be applied to surfaces of theheat exchanger 28. - This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims.
Claims (20)
1. A waste heat recovery system, comprising:
an exhaust system that generates exhaust gas; and
a Rankine cycle system for circulating a working fluid and comprising:
an evaporator configured to transfer sensible heat from the exhaust gas to the working fluid to produce cooled exhaust gas; and
an economizer configured to transfer latent heat from the exhaust gas to the working fluid, wherein the economizer comprises a carbon steel heat exchanger with a corrosion resistant coating.
2. The waste heat recovery system of claim 1 , wherein the corrosion resistant coating comprises a silica coating.
3. The waste heat recovery system of claim 1 , wherein the corrosion resistant coating exhibits at least one of hydrophobic, oleophobic, or antistatic properties.
4. The waste heat recovery system of claim 1 , wherein the working fluid comprises an organic working fluid.
5. The waste heat recovery system of claim 1 , wherein the Rankine cycle system comprises an expander configured to expand the working fluid evaporated by the evaporator to drive a generator.
6. The waste heat recovery system of claim 1 , wherein the Rankine cycle system comprises a condenser configured to condense the working fluid.
7. The waste heat recovery system of claim 1 , wherein the evaporator is configured to at least partially evaporate and/or to superheat the working fluid.
8. The waste heat recovery system of claim 1 , comprising an exhaust gas heat exchanger configured to transfer the sensible heat from the exhaust gas to an intermediate fluid in heat transfer communication with the working fluid.
9. A waste heat recovery system, comprising:
an exhaust system that generates hot exhaust gas;
a first Rankine cycle system for circulating a first working fluid and comprising:
an evaporator configured to transfer sensible heat from the hot exhaust gas to the first working fluid to produce cooled exhaust gas; and
an economizer configured to transfer latent heat from the cooled exhaust gas to the working fluid, wherein the economizer comprises a carbon steel heat exchanger with a corrosion resistant coating;
a second Rankine cycle system for circulating a second working fluid and configured to transfer heat from an engine heat source to the second working fluid; and
a shared heat exchanger common to the first and second Rankine cycle systems and configured to transfer heat from the first working fluid to the second working fluid to condense the first working fluid and to evaporate the second working fluid.
10. The waste heat recovery system of claim 9 , wherein the first and second working fluids comprise organic working fluids, and wherein the first working fluid has a condensation temperature above a boiling point of the second working fluid.
11. The waste heat recovery system of claim 9 , wherein the engine heat source comprises an engine cooling system.
12. The waste heat recovery system of claim 9 , wherein the second Rankine cycle system comprises a preheater configured to transfer heat from the heat source to the second working fluid to at least partially evaporate the second working fluid prior to directing the second working fluid to the shared heat exchanger.
13. A waste heat recovery system, comprising:
an exhaust system that generates hot exhaust gas; and
a Rankine cycle system for circulating a working fluid and comprising:
an evaporator configured to transfer heat from the hot exhaust gas to the working fluid to at least partially vaporize the working fluid and to produce cooled exhaust gas;
a condenser configured to receive and to condense the vaporized working fluid; and
an economizer configured to transfer heat from the cooled exhaust gas to the condensed working fluid to at least partially condense the cooled exhaust gas, wherein the economizer comprises a carbon steel heat exchanger with a silica coating.
14. The waste heat recovery system of claim 13 , wherein the working fluid comprises cyclohexane.
15. The waste heat recovery system of claim 13 , wherein the silica coating comprises silica nanoparticles disposed on surfaces of the heat exchanger exposed to the cooled exhaust gas.
16. The waste heat recovery system of claim 13 , wherein the carbon steel heat exchanger comprises a carbon steel shell configured to receive the cooled exhaust gas and carbon steel tubes configured to receive the working fluid and wherein the corrosion resistant coating is disposed on an interior surface of the carbon steel shell and on an exterior surface of the carbon steel tubes.
17. The waste heat recovery system of claim 13 , comprising a thermal oil loop for circulating thermal oil between the evaporator and an exhaust gas heat exchanger configured to receive the hot exhaust gas and transfer heat from the hot exhaust gas to the thermal oil.
18. The waste heat recovery system of claim 13 , comprising an exhaust gas heat exchanger configured to receive the hot exhaust gas and transfer heat from the hot exhaust gas to an intermediate fluid in thermal communication with the working fluid.
19. The waste heat recovery system of claim 13 , wherein the evaporator is configured to transfer sensible heat from the hot exhaust gas to the working fluid, and wherein the economizer is configured to transfer latent heat from the cooled exhaust gas to the working fluid.
20. The waste heat recovery system of claim 13 , comprising a gas engine configured to combust biogas to generate the hot exhaust gas.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US12/606,571 US20110094227A1 (en) | 2009-10-27 | 2009-10-27 | Waste Heat Recovery System |
EP10188625.7A EP2360356A3 (en) | 2009-10-27 | 2010-10-22 | Waste heat recovery system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US12/606,571 US20110094227A1 (en) | 2009-10-27 | 2009-10-27 | Waste Heat Recovery System |
Publications (1)
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US20110094227A1 true US20110094227A1 (en) | 2011-04-28 |
Family
ID=43897208
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US12/606,571 Abandoned US20110094227A1 (en) | 2009-10-27 | 2009-10-27 | Waste Heat Recovery System |
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EP (1) | EP2360356A3 (en) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103291390A (en) * | 2013-06-20 | 2013-09-11 | 华效资源有限公司 | Heating furnace flue gas and steam waste heat recycling and power generating system and power generating method |
US20140062097A1 (en) * | 2011-04-08 | 2014-03-06 | Cummins Generator Technologies Limited | Power generation system |
CN104197764A (en) * | 2014-09-18 | 2014-12-10 | 北京华晟环能科技有限公司 | Flue waste heat recovery system |
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EP2824292A3 (en) * | 2013-07-09 | 2015-08-19 | Volkswagen Aktiengesellschaft | Drive unit for a motor vehicle |
US20150285542A1 (en) * | 2014-04-02 | 2015-10-08 | King Fahd University Of Petroleum And Minerals | Intermittent absorption system with a liquid-liquid heat exchanger |
US9181866B2 (en) * | 2013-06-21 | 2015-11-10 | Caterpillar Inc. | Energy recovery and cooling system for hybrid machine powertrain |
US20190010893A1 (en) * | 2017-07-05 | 2019-01-10 | Cummins Inc. | Systems and methods for waste heat recovery for internal combustion engines |
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US10544705B2 (en) | 2018-03-16 | 2020-01-28 | Hamilton Sundstrand Corporation | Rankine cycle powered by bleed heat |
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WO2022011995A1 (en) * | 2020-07-12 | 2022-01-20 | 李华玉 | Second-type single-working-medium combined cycle |
US20220298955A1 (en) * | 2019-08-21 | 2022-09-22 | Innio Jenbacher Gmbh & Co Og | Power plant and method for operating a power plant |
Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3769789A (en) * | 1971-07-06 | 1973-11-06 | Sundstrand Corp | Rankine cycle engine |
US4536420A (en) * | 1983-12-05 | 1985-08-20 | General Electric Company | Process and composition for producing permanently water wettable surfaces |
US4551436A (en) * | 1984-04-11 | 1985-11-05 | General Electric Company | Fabrication of small dense silicon carbide spheres |
US4577380A (en) * | 1979-10-04 | 1986-03-25 | Heat Exchanger Industries, Inc. | Method of manufacturing heat exchangers |
US5440871A (en) * | 1992-11-13 | 1995-08-15 | Foster Wheeler Energy Corporation | Circulating fluidized bed reactor combined cycle power generation system |
US5805973A (en) * | 1991-03-25 | 1998-09-08 | General Electric Company | Coated articles and method for the prevention of fuel thermal degradation deposits |
US6101813A (en) * | 1998-04-07 | 2000-08-15 | Moncton Energy Systems Inc. | Electric power generator using a ranking cycle drive and exhaust combustion products as a heat source |
US6953083B2 (en) * | 2000-03-17 | 2005-10-11 | Honda Giken Kogyo Kabushiki Kaisha | Condenser |
US7251944B2 (en) * | 2004-02-10 | 2007-08-07 | The Texas A&M University System | Vapor-compression evaporation system and method |
US7311979B2 (en) * | 2002-09-13 | 2007-12-25 | General Electric Company | Method and coating system for reducing carbonaceous deposits on surfaces exposed to hydrocarbon fuels at elevated temperatures |
US20080060357A1 (en) * | 2005-03-01 | 2008-03-13 | Ormat Technologies, Inc. | Organic working fluids |
US20080141673A1 (en) * | 2006-12-13 | 2008-06-19 | General Electric Company | System and method for power generation in rankine cycle |
US20090000299A1 (en) * | 2007-06-29 | 2009-01-01 | General Electric Company | System and method for recovering waste heat |
US20090151356A1 (en) * | 2007-12-14 | 2009-06-18 | General Electric Company | System and method for controlling an expansion system |
US20100015429A1 (en) * | 2008-07-16 | 2010-01-21 | Wisconsin Alumni Research Foundation | Metal substrates including metal oxide nanoporous thin films and methods of making the same |
US20100263380A1 (en) * | 2007-10-04 | 2010-10-21 | United Technologies Corporation | Cascaded organic rankine cycle (orc) system using waste heat from a reciprocating engine |
US20110209474A1 (en) * | 2008-08-19 | 2011-09-01 | Waste Heat Solutions Llc | Solar thermal power generation using multiple working fluids in a rankine cycle |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19506727A1 (en) * | 1995-02-27 | 1996-08-29 | Abb Management Ag | Process for operating a power plant |
US7220365B2 (en) * | 2001-08-13 | 2007-05-22 | New Qu Energy Ltd. | Devices using a medium having a high heat transfer rate |
JP2006275410A (en) * | 2005-03-29 | 2006-10-12 | Miura Co Ltd | Boiler device |
JP2008116150A (en) * | 2006-11-06 | 2008-05-22 | Dai Ichi High Frequency Co Ltd | Panel for boiler waterwall |
-
2009
- 2009-10-27 US US12/606,571 patent/US20110094227A1/en not_active Abandoned
-
2010
- 2010-10-22 EP EP10188625.7A patent/EP2360356A3/en not_active Withdrawn
Patent Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3769789A (en) * | 1971-07-06 | 1973-11-06 | Sundstrand Corp | Rankine cycle engine |
US4577380A (en) * | 1979-10-04 | 1986-03-25 | Heat Exchanger Industries, Inc. | Method of manufacturing heat exchangers |
US4536420A (en) * | 1983-12-05 | 1985-08-20 | General Electric Company | Process and composition for producing permanently water wettable surfaces |
US4551436A (en) * | 1984-04-11 | 1985-11-05 | General Electric Company | Fabrication of small dense silicon carbide spheres |
US5805973A (en) * | 1991-03-25 | 1998-09-08 | General Electric Company | Coated articles and method for the prevention of fuel thermal degradation deposits |
US5440871A (en) * | 1992-11-13 | 1995-08-15 | Foster Wheeler Energy Corporation | Circulating fluidized bed reactor combined cycle power generation system |
US6101813A (en) * | 1998-04-07 | 2000-08-15 | Moncton Energy Systems Inc. | Electric power generator using a ranking cycle drive and exhaust combustion products as a heat source |
US6953083B2 (en) * | 2000-03-17 | 2005-10-11 | Honda Giken Kogyo Kabushiki Kaisha | Condenser |
US7311979B2 (en) * | 2002-09-13 | 2007-12-25 | General Electric Company | Method and coating system for reducing carbonaceous deposits on surfaces exposed to hydrocarbon fuels at elevated temperatures |
US7251944B2 (en) * | 2004-02-10 | 2007-08-07 | The Texas A&M University System | Vapor-compression evaporation system and method |
US20080060357A1 (en) * | 2005-03-01 | 2008-03-13 | Ormat Technologies, Inc. | Organic working fluids |
US20080141673A1 (en) * | 2006-12-13 | 2008-06-19 | General Electric Company | System and method for power generation in rankine cycle |
US20090000299A1 (en) * | 2007-06-29 | 2009-01-01 | General Electric Company | System and method for recovering waste heat |
US20100263380A1 (en) * | 2007-10-04 | 2010-10-21 | United Technologies Corporation | Cascaded organic rankine cycle (orc) system using waste heat from a reciprocating engine |
US20090151356A1 (en) * | 2007-12-14 | 2009-06-18 | General Electric Company | System and method for controlling an expansion system |
US20100015429A1 (en) * | 2008-07-16 | 2010-01-21 | Wisconsin Alumni Research Foundation | Metal substrates including metal oxide nanoporous thin films and methods of making the same |
US20110209474A1 (en) * | 2008-08-19 | 2011-09-01 | Waste Heat Solutions Llc | Solar thermal power generation using multiple working fluids in a rankine cycle |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140062097A1 (en) * | 2011-04-08 | 2014-03-06 | Cummins Generator Technologies Limited | Power generation system |
CN103291390A (en) * | 2013-06-20 | 2013-09-11 | 华效资源有限公司 | Heating furnace flue gas and steam waste heat recycling and power generating system and power generating method |
US9181866B2 (en) * | 2013-06-21 | 2015-11-10 | Caterpillar Inc. | Energy recovery and cooling system for hybrid machine powertrain |
US9670836B2 (en) | 2013-07-09 | 2017-06-06 | Volkswagen Aktiengesellschaft | Drive unit for a motor vehicle |
CN104279032A (en) * | 2013-07-09 | 2015-01-14 | 大众汽车有限公司 | Drive unit for a motor vehicle |
EP2863022A3 (en) * | 2013-07-09 | 2015-08-12 | Volkswagen Aktiengesellschaft | Drive unit for a motor vehicle |
EP2824292A3 (en) * | 2013-07-09 | 2015-08-19 | Volkswagen Aktiengesellschaft | Drive unit for a motor vehicle |
US9207003B2 (en) * | 2014-04-02 | 2015-12-08 | King Fahd University Of Petroleum And Minerals | Intermittent absorption system with a liquid-liquid heat exchanger |
US20150285542A1 (en) * | 2014-04-02 | 2015-10-08 | King Fahd University Of Petroleum And Minerals | Intermittent absorption system with a liquid-liquid heat exchanger |
CN104197764A (en) * | 2014-09-18 | 2014-12-10 | 北京华晟环能科技有限公司 | Flue waste heat recovery system |
US20190010893A1 (en) * | 2017-07-05 | 2019-01-10 | Cummins Inc. | Systems and methods for waste heat recovery for internal combustion engines |
US10815929B2 (en) * | 2017-07-05 | 2020-10-27 | Cummins Inc. | Systems and methods for waste heat recovery for internal combustion engines |
WO2019103799A1 (en) * | 2017-11-21 | 2019-05-31 | Bl Technologies, Inc. | Improving steam power plant efficiency with novel steam cycle treatments |
US11261762B2 (en) * | 2017-11-21 | 2022-03-01 | Bl Technologies, Inc. | Improving steam power plant efficiency with novel steam cycle treatments |
US10544705B2 (en) | 2018-03-16 | 2020-01-28 | Hamilton Sundstrand Corporation | Rankine cycle powered by bleed heat |
US20220298955A1 (en) * | 2019-08-21 | 2022-09-22 | Innio Jenbacher Gmbh & Co Og | Power plant and method for operating a power plant |
US11746689B2 (en) * | 2019-08-21 | 2023-09-05 | Innio Jenbacher Gmbh & Co Og | Power plant and method for operating a power plant |
WO2022011995A1 (en) * | 2020-07-12 | 2022-01-20 | 李华玉 | Second-type single-working-medium combined cycle |
CN112901300A (en) * | 2021-03-15 | 2021-06-04 | 西安交通大学 | Novel flue gas whitening system and method |
Also Published As
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EP2360356A2 (en) | 2011-08-24 |
EP2360356A3 (en) | 2017-07-05 |
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