US20100326076A1 - Optimized system for recovering waste heat - Google Patents

Optimized system for recovering waste heat Download PDF

Info

Publication number
US20100326076A1
US20100326076A1 US12/494,358 US49435809A US2010326076A1 US 20100326076 A1 US20100326076 A1 US 20100326076A1 US 49435809 A US49435809 A US 49435809A US 2010326076 A1 US2010326076 A1 US 2010326076A1
Authority
US
United States
Prior art keywords
bypass
working fluid
heat
rankine cycle
coupled
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.)
Abandoned
Application number
US12/494,358
Inventor
Gabor Ast
Thomas Johannes Frey
Pierre Sebastien Huck
Herbert Kopecek
Michael Adam Bartlett
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Co
Original Assignee
General Electric Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by General Electric Co filed Critical General Electric Co
Priority to US12/494,358 priority Critical patent/US20100326076A1/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BARTLETT, MICHAEL ADAM, AST, GABOR, FREY, THOMAS JOHANNES, HUCK, PIERRE SEBASTIEN, KOPECEK, HERBERT
Publication of US20100326076A1 publication Critical patent/US20100326076A1/en
Application status is Abandoned legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02Plants 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
    • F01K23/06Plants 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
    • F01K23/065Plants 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02Plants 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
    • F01K23/04Plants 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08Plants 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
    • F01K25/10Plants 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/02Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat

Abstract

A waste heat recovery system includes at least two integrated rankine cycle systems coupled to at least two separate heat sources having different temperatures. The first rankine cycle system is coupled to a first heat source and configured to circulate a first working fluid. The second rankine cycle system is coupled to at least one second heat source and configured to circulate a second working fluid. The first and second working fluid are circulatable in heat exchange relationship through a cascading heat exchange unit for condensation of the first working fluid in the first rankine cycle system and evaporation of the second working fluid in the second rankine cycle system. At least one bypass unit is configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.

Description

    BACKGROUND
  • The embodiments disclosed herein relate generally to the field of power generation and, more particularly, to an optimized system for recovering waste heat from a plurality of heat sources having different temperatures for generation of electricity.
  • Enormous amounts of waste heat are generated by a wide variety of industrial and commercial processes and operations. Example sources of waste heat include heat from space heating assemblies, steam boilers, engines, and cooling systems. When waste heat is low grade, such as waste heat having a temperature of heat below 400 degrees Fahrenheit, for example, conventional heat recovery systems do not operate with sufficient efficiency to make recovery of energy cost-effective. The net result is that vast quantities of waste heat are simply dumped into the surroundings.
  • Combustion engines are also used to generate electricity using fuels such as gasoline, natural gas, biogas, plant oil, and diesel fuel. However, atmospheric emissions such as nitrogen oxides and particulates may be emitted.
  • In one conventional method to generate electricity from waste heat, a two-cycle system is used in heat recovery applications with waste heat sources of different temperature levels. In such two-cycle configurations, the hot heat source heats a high-boiling point liquid in a top loop, and the cold heat source heats a low-boiling point liquid in a separate bottom loop. Since the two-cycle systems are more complex and require more components, the overall cost of the two-cycle system is significantly higher.
  • In another conventional system provided to generate electricity from waste heat, a cascaded organic rankine cycle system for utilization of waste heat includes a pair of organic rankine cycle systems. The cycles are combined, and the respective organic working fluids are chosen such that the organic working fluid of the first organic rankine cycle is condensed at a condensation temperature that is above the boiling point of the organic working fluid of the second organic cycle. A single common heat exchanger is used for both the condenser of the first organic rankine cycle system and the evaporator of the second organic rankine cycle. However, performance of such a system may be reduced under different operating conditions. In other words, performance of such a system may be reduced during partial load and varying ambient conditions.
  • It is desirable to have an optimized system that effectively recovers waste heat over a wide temperature range from multiple low-grade heat sources at different operating conditions.
  • BRIEF DESCRIPTION
  • In accordance with one exemplary embodiment disclosed herein, a waste heat recovery system including at least two integrated rankine cycle systems is provided. The system includes a heat generation system comprising at least two separate heat sources having different temperatures. A first rankine cycle system is coupled to a first heat source among the at least two separate heat sources and configured to circulate a first working fluid. The first rankine system is configured to remove heat from the first heat source. A second rankine cycle system is coupled to at least one second heat source among the at least two separate heat sources and configured to circulate a second working fluid. The at least one second heat source includes a lower temperature heat source than the first heat source. The second rankine cycle system is configured to remove heat from the at least one second heat source. The first and second working fluids are circulatable in a heat exchange relationship through a cascaded heat exchange unit for condensation of the first working fluid in the first rankine cycle system and evaporation of the second working fluid in the second rankine cycle system. At least one bypass unit is configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.
  • In accordance with one exemplary embodiment disclosed herein, a waste heat recovery system including at least two integrated organic rankine cycle systems is provided. The system includes a combustion engine having an engine exhaust unit; and at least another heat source selected from a group comprising an oil heat exchanger, engine jacket, water jacket heat exchanger, lower temperature intercooler, higher temperature intercooler, or combinations thereof. A first organic rankine cycle system is coupled to the engine exhaust unit and configured to circulate a first organic working fluid. A second organic rankine cycle system is coupled to at least one other heat source selected from the group comprising the oil heat exchanger, engine jacket, water jacket heat exchanger, lower temperature intercooler, higher temperature intercooler, or combinations thereof, and configured to circulate a second organic working fluid. The one heat source includes a lower temperature heat source than at least one other heat source. The second organic rankine cycle system is configured to remove heat from the at least one other heat source. The first and second organic working fluids are circulatable in heat exchange relationship through a cascaded heat exchange unit for condensation of the first organic working fluid in the first organic rankine cycle system and evaporation of the second organic working fluid in the second organic rankine cycle system. At least one bypass unit is configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.
  • DRAWINGS
  • 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:
  • FIG. 1 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a thermal oil loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 2 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a top loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 3 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a top loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 4 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement for flow of exhaust gas in accordance with an exemplary embodiment disclosed herein;
  • FIG. 5 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a thermal oil loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 6 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a top loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 7 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a bottom loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 8 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a bottom loop in accordance with an exemplary embodiment disclosed herein;
  • FIG. 9 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a bottom loop in accordance with an exemplary embodiment disclosed herein; and
  • FIG. 10 is a diagrammatical representation of waste heat recovery system having two integrated organic rankine cycle systems with a bypass arrangement in a water loop in accordance with an exemplary embodiment disclosed herein.
  • DETAILED DESCRIPTION
  • As discussed in detail below, embodiments of the present invention provide a waste heat recovery system having at least two integrated rankine cycle systems coupled to at least two separate heat sources respectively having different temperatures. The first rankine cycle system is coupled to a first heat source and configured to circulate a first working fluid. The second rankine cycle system is coupled to at least one second heat source and configured to circulate a second working fluid. The second heat source includes a lower temperature heat source than the first heat source. The waste heat recovery system also includes a cascaded heat exchange unit. The first and second working fluids are circulated in heat exchange relationship for condensation of the first working fluid in the first rankine cycle system and evaporation of the second working fluid in the second rankine cycle system. At least one bypass unit is configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof. Various bypasses in the exemplary waste heat recovery system allow the optimized operation of the organic rankine cycle system under different operating conditions. These additional degrees of freedom enable high performance at part load and varying ambient conditions without exceeding component limits, such as maximum pressures, temperatures, or the like. Although the waste heat recovery system in the exemplary embodiments of FIGS. 1-10 is described with reference to combustion engines, the system is also applicable to other heat generation systems such as gas turbines, geothermal, solar, industrial and residential heat sources, or the like.
  • Referring to FIG. 1, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. The illustrated waste heat recovery system 10 includes a first organic rankine cycle system 12 (top cycle) and a second organic rankine cycle system 14 (bottom cycle). A first organic working fluid is circulated through the first organic rankine cycle system 12. The first organic working fluid may include cyclohexane, cyclopentane, thiophene, ketones, aromatics, or combinations thereof. In the illustrated embodiment, the first organic rankine cycle system 12 includes the evaporator 16 coupled to a first heat source 18, i.e. the exhaust unit of the engine, via a thermal oil heat exchanger 20. In the illustrated embodiment, the thermal oil heat exchanger 20 is a shell and tube type heat exchanger. The thermal oil heat exchanger 20 is used to heat thermal oil to a relatively higher temperature using exhaust gas of the engine. The evaporator 16 receives heat from the thermal oil and generates a first organic working fluid vapor. The thermal oil is then pumped back from the evaporator 16 to the thermal oil heat exchanger 20 using a pump 22. In another embodiment, the evaporator 16 may be coupled to the first heat source 18 via an exhaust economizer.
  • As discussed previously, in conventional systems performance may be reduced under different operating conditions. In other words, performance may be reduced during partial load and varying ambient conditions. In the illustrated embodiment, one bypass unit 24 is configured to divert at least a portion of thermal oil to bypass the evaporator 16. The bypass unit 24 includes a control valve 26 coupled to a bypass path 28. The control valve 26 is configured to control the flow of thermal oil through the bypass path 28. In one embodiment, during partial load conditions or transient conditions, the control valve 26 may be opened so as to divert a portion of heated thermal oil from the thermal oil heat exchanger 20 through the bypass path 28.
  • The first organic working fluid vapor from the evaporator 16 is passed through a first expander 30 (which in one example includes a radial type expander) to drive a first generator unit 32. In certain other exemplary embodiments, the first expander 30 may be axial type expander, impulse type expander, or high temperature screw type expander. After passing through the first expander 30, the first organic working fluid vapor at a relatively lower pressure and lower temperature is passed through a cascaded heat exchange unit 34. The first organic working fluid vapor is condensed into a liquid, which is then pumped via a pump 36 to the evaporator 16. The cycle may then be repeated.
  • The cascaded heat exchange unit 34 is used both as a condenser for the first organic rankine cycle system 12 and as evaporator for the second organic rankine cycle system 14. A second organic working fluid is circulated through the second organic rankine cycle system 14. The second organic working fluid may include propane, butane, pentafluoro-propane, pentafluoro-butane, pentafluoro-polyether, oil, or combinations thereof. It should be noted herein that list of first and second organic working fluids are not inclusive and other organic working fluids applicable to organic rankine cycles are also envisaged. In certain other exemplary embodiments, the first or second organic working fluid includes a binary fluid. The binary fluid may include cyclohexane-propane, cyclohexane-butane, cyclopentane-butane, or cyclopentane-pentafluoropropane, for example.
  • In the illustrated embodiment, the cascaded heat exchange unit 34 is coupled to a plurality of second heat sources such as an intercooler 38, an oil heat exchanger 40, and an engine jacket 42 via a partial evaporator 44. Such second heat sources are also typically coupled to the engine. It should be noted herein that the second heat source includes a lower temperature heat source than the first heat source. The partial evaporator 44 receives heat from a cooling water loop that collects heat from the oil heat exchanger 40, the engine jacket 42, and the intercooler 38 and generates a partially evaporated second organic working fluid two-phase stream. The second organic working fluid stream is passed through the cascaded heat exchange unit 34 for complete evaporation or even superheating of the second organic working fluid. The vaporized second organic working fluid is passed through a second expander 46 to drive a second generator unit 48. After passing through the second expander 46, the second organic working fluid vapor at lower pressure and lower temperature is passed through a condenser 50. The second organic working fluid vapor is condensed into a liquid, which is then pumped via a pump 52 to the partial evaporator 44. The partial evaporator 44 is configured to partially evaporate the liquid being supplied to the cascaded heat exchange unit 34. The fluid in the cooling water loop is pumped via a pump 54 to the oil heat exchanger 40, before being supplied to the engine jacket 42, and the intercooler 38 before it enters the partial evaporator 44. The cycle may then be repeated.
  • It should be noted that in other exemplary embodiments, first and second heat sources may include other multiple low-grade heat sources such as gas turbines with intercoolers. The cascaded heat exchange unit 24 receives heat from the first organic working fluid and generates a second organic working fluid vapor. The second organic working fluid vapor is passed through a second expander 34 (which in one example includes a screw type compressor) to drive a second generator unit 36. In certain other exemplary embodiments, the second expander 34 may be a radial type expander, an axial type expander, or an impulse type expander. In certain other exemplary embodiments, the first expander 20 and the second expander 34 are coupled to a single generator unit.
  • The cascaded organic rankine cycle system facilitates heat recovery over a temperature range that is too large for a single organic rankine cycle system to accommodate efficiently. The illustrated layout of the second heat sources facilitates effective heat removal from the plurality of lower temperature engine heat sources. This increases the effectiveness of the cooling systems and provides effective conversion of waste heat into electricity.
  • In another exemplary embodiment of the present invention, the heat generation system may include a gas turbine system. Steam may be circulated through the top cycle and the second organic working fluid may be circulated through the bottom cycle. Steam is condensed and passed in heat exchange relationship with the second organic working fluid through the cascaded heat exchange unit 34.
  • Referring to FIG. 2, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. The illustrated waste heat recovery system 10 includes the first organic rankine cycle system 12 and the second organic rankine cycle system 14. In the illustrated embodiment, the first organic rankine cycle system 12 includes the evaporator 16 coupled to the first heat source 18, for example an exhaust unit of a heat generation system 56 (for example, an engine). The evaporator 16 receives heat from the exhaust gas generated from the first heat source 18 and generates a first organic working fluid vapor. The first organic working fluid vapor is passed through the first expander 30 to drive the first generator unit 32. After passing through the first expander 20, the first organic working fluid vapor at a relatively lower pressure and lower temperature is passed through the cascaded heat exchange unit 34. The first organic working fluid vapor is condensed into a liquid, which is then pumped via the pump 36 to the evaporator 16.
  • In the illustrated embodiment, one bypass unit 58 is configured to divert at least a portion of the condensed first organic working fluid from the pump 36 to bypass the evaporator 16. The bypass unit 58 includes a control valve 60 coupled to a bypass path 62. The control valve 60 is configured to control the flow of the first organic working fluid through the bypass path 62. In one embodiment, during partial load conditions or transient conditions, the control valve 60 may be opened so as to divert a portion of the condensed first organic working fluid from the pump 36 through the bypass path 62.
  • In the illustrated embodiment, the cascaded heat exchange unit 34 may be coupled to any one or more of a plurality of second heat sources such as the intercooler 38, the oil heat exchanger 40, and a cooling water jacket heat exchanger 64. Such second heat sources are also typically coupled to the engine. After passing through the second expander 46, the second organic working fluid vapor at lower pressure and lower temperature is passed through the condenser 50. The second organic working fluid vapor is condensed into a liquid, which is then pumped via the pump 52 to the second heat sources. In the illustrated embodiment, the second organic working fluid is pumped sequentially via the intercooler 38, the oil heat exchanger 40, and the cooling water jacket heat exchanger 64.
  • Referring to FIG. 3, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. This embodiment is similar to the embodiment discussed with reference to FIG. 2. In the illustrated embodiment, one bypass unit 59 is configured to divert at least a portion of the expanded first organic working fluid from the first expander 30 to bypass the cascaded heat exchange unit 34. The bypass unit 59 includes a control valve 61 coupled to a bypass path 63. The control valve 61 is configured to control the flow of the first organic working fluid through the bypass path 63. In one embodiment, during partial load conditions or transient conditions, the control valve 61 may be opened so as to divert a portion of the expanded first organic working fluid from the first expander 30 through the bypass path 63.
  • Referring to FIG. 4, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. This embodiment is similar to the embodiment illustrated in FIG. 1. In the illustrated embodiment, the first organic rankine cycle system 12 includes the evaporator 16 coupled to the first heat source (not shown) via the thermal oil heat exchanger 20. The thermal oil heat exchanger 20 is used to heat thermal oil to a relatively higher temperature using exhaust gas of the engine. In the illustrated embodiment, one bypass unit 65 is configured to divert at least a portion of the exhaust gas from the first heat source to bypass the thermal oil heat exchanger 20. The bypass unit 65 includes a control valve 66 coupled to a bypass path 68. The control valve 66 is configured to control the flow of exhaust gas through the bypass path 68. In one embodiment, during partial load conditions or transient conditions, the control valve 66 may be opened so as to divert a portion of the exhaust gas from the first heat source through the bypass path 68.
  • Referring to FIG. 5, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. In the illustrated embodiment, the first organic rankine cycle system 12 includes the evaporator 16 coupled to the first heat source, i.e. the exhaust unit of the engine, via the thermal oil heat exchanger 20 and an exhaust economizer 70. The thermal oil is then pumped back from the evaporator 16 to the thermal oil heat exchanger 42 using the pump 22. In the illustrated embodiment, the condensed liquid (i.e. first organic working fluid) from the cascaded heat exchange unit 34 is pumped via the pump 36 to the exhaust economizer 70. The condensed liquid is heated prior to being supplied to the evaporator 16.
  • In the illustrated embodiment, one bypass unit 72 is configured to divert at least a portion of the thermal oil from the pump 22 to bypass the thermal oil heat exchanger 20. The bypass unit 72 includes a control valve 74 coupled to a bypass path 76. The control valve 74 is configured to control the flow of thermal oil through the bypass path 76. In one embodiment, during partial load conditions or transient conditions, the control valve 74 may be opened so as to divert a portion of the thermal oil from the pump 22 through the bypass path 76.
  • In the illustrated embodiment, the cascaded heat exchange unit 34 is coupled to a plurality of second heat sources such as the lower temperature intercooler 38, the oil heat exchanger 40, the water jacket heat exchanger 64, and a higher temperature intercooler 78. The heat sources disclosed herein may be coupled in series or parallel. The relative positions of the heat sources may also be varied depending upon the requirement.
  • Referring to FIG. 6, a waste heat recovery system 10 is illustrated in accordance with an exemplary embodiment of the present invention. The illustrated waste heat recovery system 10 includes the first organic rankine cycle system 12 and the second organic rankine cycle system 14. In the illustrated embodiment, the first organic rankine cycle system 12 includes the evaporator 16 coupled to the first heat source 18. The evaporator 16 receives heat from the exhaust gas generated from the first heat source 18 and generates a first organic working fluid vapor. The first organic working fluid vapor is passed through the first expander 30 to drive the first generator unit 32. After passing through the first expander 20, the first organic working fluid vapor at a relatively lower pressure and lower temperature is passed through the cascaded heat exchange unit 34. The first organic working fluid vapor is condensed into a liquid, which is then pumped via the pump 36 to the evaporator 16.
  • In the illustrated embodiment, one bypass unit 80 is configured to divert at least a portion of the first organic working fluid vapor from the evaporator 16 to bypass the first expander 20. The bypass unit 80 includes a three-way valve 82 and a pressure reduction valve 84 coupled to a bypass path 86. The three-way valve 82 is configured to control the flow of first organic working fluid through the bypass path 86. In one embodiment, during partial load conditions or transient conditions, the three-way valve 82 may be opened so as to divert a portion of the first organic working fluid vapor from the evaporator 16 through the bypass path 86. The pressure reduction valve 84 is configured to control the pressure of the first organic working fluid vapor flowing through the bypass path 86.
  • Referring to FIG. 7, a waste heat recovery system 10 is illustrated in accordance with another exemplary embodiment of the present invention. In the illustrated embodiment, the cascaded heat exchange unit 34 is coupled to a plurality of second heat sources such as the intercooler 38, the oil heat exchanger 40, and the water jacket heat exchanger 64. The second heat sources are used to preheat or partially vaporize the second organic working fluid entering the cascading heat exchange unit 34. The cascaded heat exchange unit 34 receives heat from the first organic working fluid and generates a second organic working fluid vapor. The second organic working fluid vapor is fed to the second expander 46 to drive the second generator unit 48. After passing the second organic working fluid through the second expander 46, the second organic working fluid vapor at lower pressure and lower temperature is passed through the condenser 50. The second organic working fluid vapor is condensed into a liquid, which is then pumped via the pump 52 to the lower temperature intercooler 38.
  • In the illustrated embodiment, one bypass unit 88 is configured to divert at least a portion of the second organic working fluid vapor from the cascaded heat exchange unit 34 to bypass the second expander 46. The bypass unit 88 includes a three-way valve 90 and a pressure reduction valve 92 coupled to a bypass path 94. The three-way valve 90 is configured to control the flow of second organic working fluid through the bypass path 94. In one embodiment, during partial load conditions or transient conditions, the three-way valve 90 may be opened so as to divert a portion of the second organic working fluid vapor from the cascaded heat exchange unit 34 through the bypass path 94. The pressure reduction valve 92 is configured to control the pressure of the second organic working fluid vapor flowing through the bypass path 94.
  • Referring to FIG. 8, a waste heat recovery system 10 is illustrated in accordance with another exemplary embodiment of the present invention. In the illustrated embodiment, the cascaded heat exchange unit 34 is coupled to a plurality of second heat sources such as the intercooler 38, the oil heat exchanger 40, and the engine jacket 42 via the partial evaporator 44. The partial evaporator 44 receives heat from a cooling water loop that collects heat from the oil heat exchanger 40, the engine jacket 42, and the intercooler 38 and generates a partially evaporated second organic working fluid two-phase stream. The second organic working fluid stream is passed through the cascaded heat exchange unit 34 for complete evaporation or even superheating of the second organic working fluid. The vaporized second organic working fluid is passed through the second expander 46 to drive the second generator unit 48. After passing through the second expander 46, the second organic working fluid vapor at lower pressure and lower temperature is passed through the condenser 50. The second organic working fluid vapor is condensed into a liquid, which is then pumped via the pump 52 to the partial evaporator 44.
  • In the illustrated embodiment, one bypass unit 96 is configured to divert at least a portion of the second organic working fluid from the partial evaporator 44 to bypass the cascaded heat exchange unit 34. The bypass unit 96 includes a control valve 98 coupled to a bypass path 100. The control valve 98 is configured to control the flow of second organic working fluid through the bypass path 100. In one embodiment, during partial load conditions or transient conditions, the control valve 98 may be opened so as to divert a portion of the second organic working fluid from the partial evaporator 44 through the bypass path 100.
  • Referring to FIG. 9, a waste heat recovery system 10 is illustrated in accordance with another exemplary embodiment of the present invention. This embodiment is similar to the embodiment illustrated in FIG. 8. In the illustrated embodiment, one bypass unit 102 is configured to divert at least a portion of the condensed second organic working fluid from the pump 52 to bypass the partial evaporator 44. The bypass unit 102 includes a control valve 104 coupled to a bypass path 106. The control valve 104 is configured to control the flow of the condensed second organic working fluid through the bypass path 106. In one embodiment, during partial load conditions or transient conditions, the control valve 104 may be opened so as to divert a portion of the condensed second organic working fluid from the pump 52 through the bypass path 106.
  • Referring to FIG. 10, a waste heat recovery system 10 is illustrated in accordance with another exemplary embodiment of the present invention. This embodiment is also similar to the embodiment illustrated in FIG. 8. In the illustrated embodiment, one bypass unit 108 is configured to divert at least a portion of water (mixture of water and glycol) from the intercooler 38 to bypass the partial evaporator 44. The bypass unit 108 includes a control valve 110 coupled to a bypass path 112. The control valve 110 is configured to control the flow of water through the bypass path 112. In one embodiment, during partial load conditions or transient conditions, the control valve 110 may be opened so as to divert a portion of water from the intercooler 38 through the bypass path 112.
  • It should be noted herein with the reference to embodiments discussed above, a bypass unit may include a three-way valve (for example, as discussed in embodiments of FIGS. 6 and 7), a control valve (for example, as discussed in embodiments of FIGS. 1-5, and FIGS. 8-10), a pressure reduction valve (for example, as discussed in embodiments of FIGS. 6 and 7), or combinations thereof coupled to a bypass path. In certain embodiments, a three-way valve may be used as a “splitter” and may be disposed upstream of a component to be bypassed. In some other embodiments, a three-way valve may be used as a “mixer” and may be disposed downstream of a component to be bypassed. In a particular embodiment, a control valve may also be a three-way valve.
  • With reference to the embodiments discussed above, although one evaporator 16, one cascaded heat exchange unit 34, and one partial evaporator 44 is shown, in some embodiments, more than one evaporator 16, cascaded heat exchange unit 34, partial evaporator 44 may be used. In such embodiments, an exemplary bypass unit may be provided across the more than one evaporator 16, cascaded heat exchange unit 34, and partial evaporator 44.
  • The various bypass arrangements discussed herein with reference to FIGS. 1-9 enhances thermodynamic efficiency and effective heat recovery of the overall system. It should be noted herein that in other embodiments of the exemplary recuperated waste heat recovery system, the number of second heat sources such as intercoolers, oil heat exchangers, jacket heat exchangers, evaporators and their relative positions and their relative positions in the second organic rankine cycle system may be varied depending the application. All such permutations and combinations are envisaged. Various such permutations and combinations discussed in U.S. patent application No. 11/770,895 filed on Jun. 29, 2007 is incorporated herein by reference.
  • While only certain features of the invention have been illustrated and described herein, many modifications and changes will occur to those skilled in the art. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the invention.

Claims (27)

1. A waste heat recovery system including at least two integrated rankine cycle systems, the recovery system comprising:
a heat generation system comprising at least two separate heat sources having different temperatures;
a first rankine cycle system comprising a first evaporator and a first expander, wherein the first rankine cycle system is coupled to a first heat source among the at least two separate heat sources and configured to circulate a first working fluid; wherein the first rankine system is configured to remove heat from the first heat source;
a second rankine cycle system comprising a second evaporator and a second expander; wherein the second rankine cycle system is coupled to at least one second heat source among the at least two separate heat sources and configured to circulate a second working fluid, the at least one second heat source comprising a lower temperature heat source than the first heat source, wherein the second rankine cycle system is configured to remove heat from the at least one second heat source;
a cascaded heat exchange unit, wherein the first and second working fluids are circulatable in heat exchange relationship through the cascaded heat exchange unit for condensation of the first working fluid in the first rankine cycle system and evaporation of the second working fluid in the second rankine cycle system; and
at least one bypass unit configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.
2. The recovery system of claim 1, wherein the first evaporator is coupled to the first heat source, and wherein the first heat source comprises an engine exhaust unit.
3. The recovery system of claim 2, wherein the first evaporator is coupled to the engine exhaust unit via a thermal oil heat exchanger, exhaust economizer, or combinations thereof.
4. The recovery system of claim 3, further comprising one bypass unit configured to divert at least a portion of thermal oil to bypass the first evaporator; wherein the one bypass unit comprises a control valve coupled to a bypass path.
5. The recovery system of claim 3, further comprising one bypass unit configured to divert at least a portion of thermal oil to bypass the thermal oil heat exchanger; wherein the one bypass unit comprises a control valve coupled to a bypass path.
6. The recovery system of claim 2, further comprising one bypass unit configured to divert at least a portion of engine exhaust gas to bypass the thermal oil heat exchanger; wherein the one bypass unit comprises a control valve coupled to a bypass path.
7. The recovery system of claim 1, wherein the second rankine cycle system comprises a condenser coupled to the at least one second heat source selected from a group comprising an oil heat exchanger, an engine jacket, a water jacket heat exchanger, a lower temperature intercooler, a higher temperature intercooler, or combinations thereof.
8. The recovery system of claim 7, further comprising a partial evaporator; wherein the condenser is coupled to the oil heat exchanger, the engine jacket, the water jacket heat exchanger, the engine jacket, the lower temperature intercooler, the higher temperature intercooler, or combinations thereof through the partial evaporator configured to partially evaporate the second working fluid before entering the cascaded heat exchange unit.
9. The recovery system of claim 8, further comprising one bypass unit configured to divert at least a portion of water to bypass the partial evaporator; wherein the one bypass unit comprises a control valve coupled to a bypass path.
10. The recovery system of claim 8, further comprising one bypass unit configured to divert at least a portion of the second working fluid to bypass the partial evaporator, wherein the one bypass unit comprises a control valve coupled to a bypass path.
11. The recovery system of claim 1, wherein the at least one bypass unit comprises a control valve, a three-way valve, pressure reduction valve, or combinations thereof coupled to a bypass path.
12. A waste heat recovery system including at least two integrated organic rankine cycle systems, the recovery system comprising:
a combustion engine comprising one heat source having an engine exhaust unit; and at least one other heat source selected from a group comprising an oil heat exchanger, an engine jacket, a water jacket heat exchanger, a lower temperature intercooler, a higher temperature intercooler, or combinations thereof;
a first organic rankine cycle system comprising a first evaporator and a first expander, wherein the first organic rankine cycle system is coupled to the engine exhaust unit and configured to circulate a first organic working fluid; wherein the first organic rankine system is configured to remove heat from the engine exhaust unit;
a second organic rankine cycle system comprising a second evaporator and a second expander; wherein the second organic rankine cycle system is coupled to the at least one other heat source selected from the group comprising the oil heat exchanger, the engine jacket, the water jacket heat exchanger, the lower temperature intercooler, the higher temperature intercooler, or combinations thereof; and configured to circulate a second organic working fluid, the one heat source comprising a higher temperature heat source than the at least one other heat source, wherein the second organic rankine cycle system is configured to remove heat from the at least one other heat source; and
a cascaded heat exchange unit, wherein the first and second organic working fluids are circulatable in heat exchange relationship through the cascaded heat exchange unit for condensation of the first organic working fluid in the first organic rankine cycle system and evaporation of the second organic working fluid in the second organic rankine cycle system;
at least one bypass unit configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.
13. The recovery system of claim 12, wherein the first evaporator is coupled to the engine exhaust unit via a thermal oil heat exchanger, exhaust economizer, or combinations thereof.
14. The recovery system of claim 13, further comprising one bypass unit configured to divert at least a portion of thermal oil to bypass the first evaporator; wherein the one bypass unit comprises a control valve coupled to a bypass path.
15. The recovery system of claim 13, further comprising one bypass unit configured to divert at least a portion of thermal oil to bypass the thermal oil heat exchanger; wherein the one bypass unit comprises a control valve coupled to a bypass path.
16. The recovery system of claim 12, further comprising one bypass unit configured to divert at least a portion of engine exhaust gas to bypass the thermal oil heat exchanger; wherein the one bypass unit comprises a control valve coupled to a bypass path.
17. The recovery system of claim 12, wherein the second rankine cycle system comprises a condenser coupled to the at least one other heat source selected from a group comprising an oil heat exchanger, an engine jacket, a water jacket heat exchanger, a lower temperature intercooler, a higher temperature intercooler, or combinations thereof.
18. The recovery system of claim 17, further comprising a partial evaporator; wherein the condenser is coupled to the oil heat exchanger, the engine jacket, the water jacket heat exchanger, the engine jacket, the lower temperature intercooler, the higher temperature intercooler, or combinations thereof through the partial evaporator configured to partially evaporate the second working fluid before entering the cascaded heat exchange unit.
19. The recovery system of claim 18, further comprising one bypass unit configured to divert at least a portion of water to bypass the partial evaporator; wherein the one bypass unit comprises a control valve coupled to a bypass path.
20. The recovery system of claim 18, further comprising one bypass unit configured to divert at least a portion of the second working fluid to bypass the partial evaporator, wherein the one bypass unit comprises a control valve coupled to a bypass path.
21. The recovery system of claim 12, wherein the at least one bypass unit comprises a control valve, a three-way valve, pressure reduction valve, or combinations thereof coupled to a bypass path.
22. A waste heat recovery system including at least two integrated rankine cycle systems, the recovery system comprising:
a heat generation system comprising at least two separate heat sources having different temperatures;
a first rankine cycle system comprising a first evaporator and a first expander, wherein the first rankine cycle system is coupled to a first heat source among the at least two separate heat sources and configured to circulate a first working fluid; wherein the first rankine system is configured to remove heat from the first heat source;
a second rankine cycle system comprising a second evaporator and a second expander; wherein the second rankine cycle system is coupled to at least one second heat source among the at least two separate heat sources and configured to circulate a second working fluid, the at least one second heat source comprising a lower temperature heat source than the first heat source, wherein the second rankine cycle system is configured to remove heat from the at least one second heat source;
a cascaded heat exchange unit, wherein the first and second working fluids are circulatable in heat exchange relationship through the cascaded heat exchange unit for condensation of the first working fluid in the first rankine cycle system and evaporation of the second working fluid in the second rankine cycle system; wherein the second rankine cycle is configured to preheat and/or partially evaporate the second working fluid before entering the cascaded heat exchange unit and
at least one bypass unit configured to divert at least a portion of the first working fluid to bypass the first evaporator, the first expander, the cascaded heat exchange unit, or combinations thereof; at least a portion of the second working fluid to bypass the second expander, the cascaded heat exchange unit, or combinations thereof.
23. The recovery system of claim 22, wherein the second rankine cycle system comprises a condenser coupled to the at least one second heat source selected from a group comprising an oil heat exchanger, an engine jacket, a water jacket heat exchanger, a lower temperature intercooler, a higher temperature intercooler, or combinations thereof.
24. The recovery system of claim 23, further comprising a partial evaporator; wherein the condenser is coupled to the oil heat exchanger, the engine jacket, the water jacket heat exchanger, the engine jacket, the lower temperature intercooler, the higher temperature intercooler, or combinations thereof through the partial evaporator configured to partially evaporate the second working fluid before entering the cascaded heat exchange unit.
25. The recovery system of claim 24, further comprising one bypass unit configured to divert at least a portion of water to bypass the partial evaporator; wherein the one bypass unit comprises a control valve coupled to a bypass path.
26. The recovery system of claim 24, further comprising one bypass unit configured to divert at least a portion of the second working fluid to bypass the partial evaporator, wherein the one bypass unit comprises a control valve coupled to a bypass path.
27. The recovery system of claim 22, wherein the at least one bypass unit comprises a control valve, a three-way valve, pressure reduction valve, or combinations thereof coupled to a bypass path.
US12/494,358 2009-06-30 2009-06-30 Optimized system for recovering waste heat Abandoned US20100326076A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/494,358 US20100326076A1 (en) 2009-06-30 2009-06-30 Optimized system for recovering waste heat

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12/494,358 US20100326076A1 (en) 2009-06-30 2009-06-30 Optimized system for recovering waste heat
EP10166699A EP2345799A3 (en) 2009-06-30 2010-06-21 Optimized system for recovering waste heat

Publications (1)

Publication Number Publication Date
US20100326076A1 true US20100326076A1 (en) 2010-12-30

Family

ID=43379249

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/494,358 Abandoned US20100326076A1 (en) 2009-06-30 2009-06-30 Optimized system for recovering waste heat

Country Status (2)

Country Link
US (1) US20100326076A1 (en)
EP (1) EP2345799A3 (en)

Cited By (58)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110061528A1 (en) * 2009-09-16 2011-03-17 Bha Group, Inc. Power plant emissions control using integrated organic rankine cycle
US20110072818A1 (en) * 2009-09-21 2011-03-31 Clean Rolling Power, LLC Waste heat recovery system
US20110072819A1 (en) * 2009-09-28 2011-03-31 General Electric Company Heat recovery system based on the use of a stabilized organic rankine fluid, and related processes and devices
US20110115445A1 (en) * 2009-11-19 2011-05-19 Ormat Technologies, Inc. Power system
US20110308253A1 (en) * 2010-06-21 2011-12-22 Paccar Inc Dual cycle rankine waste heat recovery cycle
CN102434236A (en) * 2011-11-17 2012-05-02 重庆川然节能技术有限公司 Threaded rod expansion/centripetal turbine low-parameter waste heat combined generator unit
CN102505973A (en) * 2011-10-28 2012-06-20 天津大学 Double expansion Rankine cycle power generation system
WO2012122631A1 (en) * 2011-03-14 2012-09-20 Pyrogenesis Canada Inc. Method to maximize energy recovery in waste-to-energy processes
EP2514931A1 (en) * 2011-04-20 2012-10-24 General Electric Company Integration of waste heat from charge air cooling into a cascaded organic rankine cycle system
US20130001958A1 (en) * 2010-03-24 2013-01-03 Lightsail Energy Inc. Storage of compressed air in wind turbine support structure
GB2498258A (en) * 2012-01-04 2013-07-10 Gen Electric Waste heat recovery system using a cascade of ORC systems
US20130219894A1 (en) * 2010-11-02 2013-08-29 John J. Bannister Heating system - modular
US8613195B2 (en) 2009-09-17 2013-12-24 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US8616323B1 (en) 2009-03-11 2013-12-31 Echogen Power Systems Hybrid power systems
US8616001B2 (en) 2010-11-29 2013-12-31 Echogen Power Systems, Llc Driven starter pump and start sequence
KR20140008963A (en) * 2012-07-13 2014-01-22 한라비스테온공조 주식회사 An apparatus for using waste heat
US20140028033A1 (en) * 2012-07-24 2014-01-30 Access Energy Llc Thermal cycle energy and pumping recovery system
US8783034B2 (en) 2011-11-07 2014-07-22 Echogen Power Systems, Llc Hot day cycle
US8794002B2 (en) 2009-09-17 2014-08-05 Echogen Power Systems Thermal energy conversion method
WO2014124139A1 (en) * 2013-02-11 2014-08-14 Access Energy Llc Controlling heat source fluid for thermal cycles
US8813497B2 (en) 2009-09-17 2014-08-26 Echogen Power Systems, Llc Automated mass management control
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US20150076831A1 (en) * 2013-09-05 2015-03-19 Echogen Power Systems, L.L.C. Heat Engine System Having a Selectively Configurable Working Fluid Circuit
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9018778B2 (en) 2012-01-04 2015-04-28 General Electric Company Waste heat recovery system generator varnishing
US9024460B2 (en) 2012-01-04 2015-05-05 General Electric Company Waste heat recovery system generator encapsulation
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US9181866B2 (en) * 2013-06-21 2015-11-10 Caterpillar Inc. Energy recovery and cooling system for hybrid machine powertrain
US20150330530A1 (en) * 2012-10-17 2015-11-19 Norgren Limited Bypass valve
WO2015200821A1 (en) * 2014-06-26 2015-12-30 Voss Mark G Organic rankine cycle waste heat recovery system
US20160017760A1 (en) * 2014-07-17 2016-01-21 Panasonic Intellectual Property Management Co., Ltd. Cogenerating system
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9540961B2 (en) 2013-04-25 2017-01-10 Access Energy Llc Heat sources for thermal cycles
US9551487B2 (en) 2012-03-06 2017-01-24 Access Energy Llc Heat recovery using radiant heat
US20170058714A1 (en) * 2015-08-24 2017-03-02 Saudi Arabian Oil Company Power Generation from Waste Heat in Integrated Crude Oil Refining and Aromatics Facilities
US20170077376A1 (en) * 2014-03-11 2017-03-16 University Of Central Florida Research Foundation, Inc. Thermoelectric power generator and combustion apparatus
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US9725652B2 (en) 2015-08-24 2017-08-08 Saudi Arabian Oil Company Delayed coking plant combined heating and power generation
US9745871B2 (en) 2015-08-24 2017-08-29 Saudi Arabian Oil Company Kalina cycle based conversion of gas processing plant waste heat into power
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US9803508B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil diesel hydrotreating and aromatics facilities
US9803506B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil hydrocracking and aromatics facilities
US9803511B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation using independent dual organic rankine cycles from waste heat systems in diesel hydrotreating-hydrocracking and atmospheric distillation-naphtha hydrotreating-aromatics facilities
US9803505B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated aromatics and naphtha block facilities
US9803507B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation using independent dual organic Rankine cycles from waste heat systems in diesel hydrotreating-hydrocracking and continuous-catalytic-cracking-aromatics facilities
US9803513B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated aromatics, crude distillation, and naphtha block facilities
US20170314420A1 (en) * 2014-11-03 2017-11-02 Echogen Power Systems, L.L.C. Valve network and method for controlling pressure within a supercritical working fluid circuit in a heat engine system with a turbopump
US9816401B2 (en) 2015-08-24 2017-11-14 Saudi Arabian Oil Company Modified Goswami cycle based conversion of gas processing plant waste heat into power and cooling
US10024195B2 (en) 2015-02-19 2018-07-17 General Electric Company System and method for heating make-up working fluid of a steam system with engine fluid waste heat
EP3361061A1 (en) * 2017-02-09 2018-08-15 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Thermal energy recovery device
US10118108B2 (en) 2014-04-22 2018-11-06 General Electric Company System and method of distillation process and turbine engine intercooler
WO2019123243A1 (en) * 2017-12-18 2019-06-27 Exergy S.P.A. Process, plant and thermodynamic cycle for production of power from variable temperature heat sources
US10487695B2 (en) 2015-10-23 2019-11-26 General Electric Company System and method of interfacing intercooled gas turbine engine with distillation process

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120000201A1 (en) * 2010-06-30 2012-01-05 General Electric Company System and method for generating and storing transient integrated organic rankine cycle energy
CN105089729B (en) * 2015-09-06 2017-03-22 东南大学 System and method for recycling waste heat of two-stage efficient circulation evaporation organic Rankine cycle coal-fired flue gas

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888084A (en) * 1974-05-20 1975-06-10 Gilbert L Hawkins Thermal recovery system
US3945210A (en) * 1974-06-07 1976-03-23 Rodina Energy R & D Corporation Energy recovery
US4033135A (en) * 1975-02-07 1977-07-05 Sulzer Brothers Limited Plant and process for vaporizing and heating liquid natural gas
US5121607A (en) * 1991-04-09 1992-06-16 George Jr Leslie C Energy recovery system for large motor vehicles
US6986251B2 (en) * 2003-06-17 2006-01-17 Utc Power, Llc Organic rankine cycle system for use with a reciprocating engine
US7121906B2 (en) * 2004-11-30 2006-10-17 Carrier Corporation Method and apparatus for decreasing marine vessel power plant exhaust temperature
US7318316B2 (en) * 2003-07-04 2008-01-15 Katsushige Yamada Reheat/regenerative type thermal power plant using Rankine cycle
US7454910B2 (en) * 2003-06-23 2008-11-25 Denso Corporation Waste heat recovery system of heat source, with Rankine cycle
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 (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2885169A1 (en) * 2005-04-27 2006-11-03 Renault Sas Onboard heat energy managing system for vehicle, has Rankine cycle energy recovery circuit comprising bypass control valve in parallel with turbine which provides mechanical energy from fluid at vapor state
US20090211253A1 (en) * 2005-06-16 2009-08-27 Utc Power Corporation Organic Rankine Cycle Mechanically and Thermally Coupled to an Engine Driving a Common Load
US8561405B2 (en) * 2007-06-29 2013-10-22 General Electric Company System and method for recovering waste heat

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888084A (en) * 1974-05-20 1975-06-10 Gilbert L Hawkins Thermal recovery system
US3945210A (en) * 1974-06-07 1976-03-23 Rodina Energy R & D Corporation Energy recovery
US4033135A (en) * 1975-02-07 1977-07-05 Sulzer Brothers Limited Plant and process for vaporizing and heating liquid natural gas
US5121607A (en) * 1991-04-09 1992-06-16 George Jr Leslie C Energy recovery system for large motor vehicles
US6986251B2 (en) * 2003-06-17 2006-01-17 Utc Power, Llc Organic rankine cycle system for use with a reciprocating engine
US7454910B2 (en) * 2003-06-23 2008-11-25 Denso Corporation Waste heat recovery system of heat source, with Rankine cycle
US7318316B2 (en) * 2003-07-04 2008-01-15 Katsushige Yamada Reheat/regenerative type thermal power plant using Rankine cycle
US7121906B2 (en) * 2004-11-30 2006-10-17 Carrier Corporation Method and apparatus for decreasing marine vessel power plant exhaust temperature
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 (111)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8616323B1 (en) 2009-03-11 2013-12-31 Echogen Power Systems Hybrid power systems
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US8236093B2 (en) * 2009-09-16 2012-08-07 Bha Group, Inc. Power plant emissions control using integrated organic rankine cycle
US20110061528A1 (en) * 2009-09-16 2011-03-17 Bha Group, Inc. Power plant emissions control using integrated organic rankine cycle
US8613195B2 (en) 2009-09-17 2013-12-24 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US9458738B2 (en) * 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
US8794002B2 (en) 2009-09-17 2014-08-05 Echogen Power Systems Thermal energy conversion method
US8813497B2 (en) 2009-09-17 2014-08-26 Echogen Power Systems, Llc Automated mass management control
US9115605B2 (en) 2009-09-17 2015-08-25 Echogen Power Systems, Llc Thermal energy conversion device
US20140096524A1 (en) * 2009-09-17 2014-04-10 Echogen Power Systems, Llc Heat Engine and Heat to Electricity Systems and Methods with Working Fluid Mass Management Control
US20110072818A1 (en) * 2009-09-21 2011-03-31 Clean Rolling Power, LLC Waste heat recovery system
US9243518B2 (en) * 2009-09-21 2016-01-26 Sandra I. Sanchez Waste heat recovery system
US20110072819A1 (en) * 2009-09-28 2011-03-31 General Electric Company Heat recovery system based on the use of a stabilized organic rankine fluid, and related processes and devices
US8193659B2 (en) * 2009-11-19 2012-06-05 Ormat Technologies, Inc. Power system
US20110115445A1 (en) * 2009-11-19 2011-05-19 Ormat Technologies, Inc. Power system
US8723347B2 (en) * 2010-03-24 2014-05-13 Lightsail Energy, Inc. Energy storage system utilizing compressed gas
US20130001958A1 (en) * 2010-03-24 2013-01-03 Lightsail Energy Inc. Storage of compressed air in wind turbine support structure
US20110308253A1 (en) * 2010-06-21 2011-12-22 Paccar Inc Dual cycle rankine waste heat recovery cycle
US9046006B2 (en) * 2010-06-21 2015-06-02 Paccar Inc Dual cycle rankine waste heat recovery cycle
US20130219894A1 (en) * 2010-11-02 2013-08-29 John J. Bannister Heating system - modular
US9797603B2 (en) * 2010-11-02 2017-10-24 Energetix Genlec Limited Heating system—modular
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US9410449B2 (en) 2010-11-29 2016-08-09 Echogen Power Systems, Llc Driven starter pump and start sequence
US8616001B2 (en) 2010-11-29 2013-12-31 Echogen Power Systems, Llc Driven starter pump and start sequence
US20170254228A1 (en) * 2011-03-14 2017-09-07 Pyrogenesis Canada Inc. Method to maximize energy recovery in waste-to-energy process
US9447705B2 (en) 2011-03-14 2016-09-20 Pyrogenesis Canada Inc. Method to maximize energy recovery in waste-to-energy process
WO2012122631A1 (en) * 2011-03-14 2012-09-20 Pyrogenesis Canada Inc. Method to maximize energy recovery in waste-to-energy processes
US8650879B2 (en) 2011-04-20 2014-02-18 General Electric Company Integration of waste heat from charge air cooling into a cascaded organic rankine cycle system
EP2514931A1 (en) * 2011-04-20 2012-10-24 General Electric Company Integration of waste heat from charge air cooling into a cascaded organic rankine cycle system
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
CN102505973A (en) * 2011-10-28 2012-06-20 天津大学 Double expansion Rankine cycle power generation system
US8783034B2 (en) 2011-11-07 2014-07-22 Echogen Power Systems, Llc Hot day cycle
CN102434236A (en) * 2011-11-17 2012-05-02 重庆川然节能技术有限公司 Threaded rod expansion/centripetal turbine low-parameter waste heat combined generator unit
GB2498258B (en) * 2012-01-04 2014-10-15 Gen Electric Waste heat recovery systems
US8984884B2 (en) 2012-01-04 2015-03-24 General Electric Company Waste heat recovery systems
US9024460B2 (en) 2012-01-04 2015-05-05 General Electric Company Waste heat recovery system generator encapsulation
US9018778B2 (en) 2012-01-04 2015-04-28 General Electric Company Waste heat recovery system generator varnishing
GB2498258A (en) * 2012-01-04 2013-07-10 Gen Electric Waste heat recovery system using a cascade of ORC systems
US9551487B2 (en) 2012-03-06 2017-01-24 Access Energy Llc Heat recovery using radiant heat
KR20140008963A (en) * 2012-07-13 2014-01-22 한라비스테온공조 주식회사 An apparatus for using waste heat
KR101888641B1 (en) * 2012-07-13 2018-08-14 한온시스템 주식회사 An apparatus for using waste heat
US9322300B2 (en) * 2012-07-24 2016-04-26 Access Energy Llc Thermal cycle energy and pumping recovery system
US20140028033A1 (en) * 2012-07-24 2014-01-30 Access Energy Llc Thermal cycle energy and pumping recovery system
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US20150330530A1 (en) * 2012-10-17 2015-11-19 Norgren Limited Bypass valve
US9964229B2 (en) * 2012-10-17 2018-05-08 Norgren Limited Bypass valve
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
WO2014124139A1 (en) * 2013-02-11 2014-08-14 Access Energy Llc Controlling heat source fluid for thermal cycles
US9540961B2 (en) 2013-04-25 2017-01-10 Access Energy Llc Heat sources for thermal cycles
US9181866B2 (en) * 2013-06-21 2015-11-10 Caterpillar Inc. Energy recovery and cooling system for hybrid machine powertrain
US20150076831A1 (en) * 2013-09-05 2015-03-19 Echogen Power Systems, L.L.C. Heat Engine System Having a Selectively Configurable Working Fluid Circuit
US9874112B2 (en) * 2013-09-05 2018-01-23 Echogen Power Systems, Llc Heat engine system having a selectively configurable working fluid circuit
US20170077376A1 (en) * 2014-03-11 2017-03-16 University Of Central Florida Research Foundation, Inc. Thermoelectric power generator and combustion apparatus
US10118108B2 (en) 2014-04-22 2018-11-06 General Electric Company System and method of distillation process and turbine engine intercooler
WO2015200821A1 (en) * 2014-06-26 2015-12-30 Voss Mark G Organic rankine cycle waste heat recovery system
US20160017760A1 (en) * 2014-07-17 2016-01-21 Panasonic Intellectual Property Management Co., Ltd. Cogenerating system
US9874114B2 (en) * 2014-07-17 2018-01-23 Panasonic Intellectual Property Management Co., Ltd. Cogenerating system
US20170314420A1 (en) * 2014-11-03 2017-11-02 Echogen Power Systems, L.L.C. Valve network and method for controlling pressure within a supercritical working fluid circuit in a heat engine system with a turbopump
US10267184B2 (en) * 2014-11-03 2019-04-23 Echogen Power Systems Llc Valve network and method for controlling pressure within a supercritical working fluid circuit in a heat engine system with a turbopump
US10024195B2 (en) 2015-02-19 2018-07-17 General Electric Company System and method for heating make-up working fluid of a steam system with engine fluid waste heat
US9803145B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil refining, aromatics, and utilities facilities
US9803507B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation using independent dual organic Rankine cycles from waste heat systems in diesel hydrotreating-hydrocracking and continuous-catalytic-cracking-aromatics facilities
US9803513B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated aromatics, crude distillation, and naphtha block facilities
US9803930B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated hydrocracking and diesel hydrotreating facilities
US9816401B2 (en) 2015-08-24 2017-11-14 Saudi Arabian Oil Company Modified Goswami cycle based conversion of gas processing plant waste heat into power and cooling
US9816759B2 (en) 2015-08-24 2017-11-14 Saudi Arabian Oil Company Power generation using independent triple organic rankine cycles from waste heat in integrated crude oil refining and aromatics facilities
US9828885B2 (en) 2015-08-24 2017-11-28 Saudi Arabian Oil Company Modified Goswami cycle based conversion of gas processing plant waste heat into power and cooling with flexibility
US9845995B2 (en) 2015-08-24 2017-12-19 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US9845996B2 (en) 2015-08-24 2017-12-19 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US9851153B2 (en) 2015-08-24 2017-12-26 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US9803508B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil diesel hydrotreating and aromatics facilities
US9869209B2 (en) 2015-08-24 2018-01-16 Saudi Arabian Oil Company Kalina cycle based conversion of gas processing plant waste heat into power
US9803505B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated aromatics and naphtha block facilities
US9745871B2 (en) 2015-08-24 2017-08-29 Saudi Arabian Oil Company Kalina cycle based conversion of gas processing plant waste heat into power
US9879918B2 (en) 2015-08-24 2018-01-30 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US9891004B2 (en) 2015-08-24 2018-02-13 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10502495B2 (en) 2015-08-24 2019-12-10 Saudi Arabian Oil Company Systems for recovery and re-use of waste energy in crude oil refining facility and aromatics complex
US9725652B2 (en) 2015-08-24 2017-08-08 Saudi Arabian Oil Company Delayed coking plant combined heating and power generation
US9803509B2 (en) * 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil refining and aromatics facilities
US9803511B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation using independent dual organic rankine cycles from waste heat systems in diesel hydrotreating-hydrocracking and atmospheric distillation-naphtha hydrotreating-aromatics facilities
US10502494B2 (en) 2015-08-24 2019-12-10 Saudi Arabian Oil Company Systems for recovery and re-use of waste energy in crude oil refining facility and aromatics complex through simultaneous intra-plant integration and plants' thermal coupling
US10113448B2 (en) 2015-08-24 2018-10-30 Saudi Arabian Oil Company Organic Rankine cycle based conversion of gas processing plant waste heat into power
US10113805B2 (en) 2015-08-24 2018-10-30 Saudi Arabian Oil Company Systems for recovery and re-use of waste energy in hydrocracking-based configuration for integrated crude oil refining and aromatics complex
US9803506B2 (en) 2015-08-24 2017-10-31 Saudi Arabian Oil Company Power generation from waste heat in integrated crude oil hydrocracking and aromatics facilities
US10119764B2 (en) 2015-08-24 2018-11-06 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10125639B2 (en) 2015-08-24 2018-11-13 Saudi Arabian Oil Company Organic Rankine cycle based conversion of gas processing plant waste heat into power and cooling
US10126067B2 (en) 2015-08-24 2018-11-13 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10125640B2 (en) 2015-08-24 2018-11-13 Saudi Arabian Oil Company Modified goswami cycle based conversion of gas processing plant waste heat into power and cooling with flexibility
US10174640B1 (en) 2015-08-24 2019-01-08 Saudi Arabian Oil Company Modified Goswami cycle based conversion of gas processing plant waste heat into power and cooling with flexibility
US10227899B2 (en) 2015-08-24 2019-03-12 Saudi Arabian Oil Company Organic rankine cycle based conversion of gas processing plant waste heat into power and cooling
US9915477B2 (en) 2015-08-24 2018-03-13 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10301977B2 (en) 2015-08-24 2019-05-28 Saudi Arabian Oil Company Kalina cycle based conversion of gas processing plant waste heat into power
US10480864B2 (en) 2015-08-24 2019-11-19 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10385275B2 (en) 2015-08-24 2019-08-20 Saudi Arabian Oil Company Delayed coking plant combined heating and power generation
US10429135B2 (en) 2015-08-24 2019-10-01 Saudi Arabian Oil Company Recovery and re-use of waste energy in industrial facilities
US10436517B2 (en) 2015-08-24 2019-10-08 Saudi Arabian Oil Company Systems for recovery and re-use of waste energy in hydrocracking-based configuration for integrated crude oil refining and aromatics complex
US20170058714A1 (en) * 2015-08-24 2017-03-02 Saudi Arabian Oil Company Power Generation from Waste Heat in Integrated Crude Oil Refining and Aromatics Facilities
US10480352B2 (en) 2015-08-24 2019-11-19 Saudi Arabian Oil Company Organic Rankine cycle based conversion of gas processing plant waste heat into power and cooling
US10443946B2 (en) 2015-08-24 2019-10-15 Saudi Arabian Oil Company Systems for recovery and re-use of waste energy in crude oil refining and aromatics complex
US10487695B2 (en) 2015-10-23 2019-11-26 General Electric Company System and method of interfacing intercooled gas turbine engine with distillation process
EP3361061A1 (en) * 2017-02-09 2018-08-15 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Thermal energy recovery device
US10508569B2 (en) 2017-02-09 2019-12-17 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Thermal energy recovery device
WO2019123243A1 (en) * 2017-12-18 2019-06-27 Exergy S.P.A. Process, plant and thermodynamic cycle for production of power from variable temperature heat sources

Also Published As

Publication number Publication date
EP2345799A3 (en) 2011-11-02
EP2345799A2 (en) 2011-07-20

Similar Documents

Publication Publication Date Title
Bombarda et al. Heat recovery from Diesel engines: A thermodynamic comparison between Kalina and ORC cycles
Kanoglu et al. Performance assessment of cogeneration plants
US6173563B1 (en) Modified bottoming cycle for cooling inlet air to a gas turbine combined cycle plant
US6065280A (en) Method of heating gas turbine fuel in a combined cycle power plant using multi-component flow mixtures
JP4607116B2 (en) Method and apparatus for obtaining heat from multiple heat sources
US9441504B2 (en) System and method for managing thermal issues in one or more industrial processes
AU2011202917B2 (en) Dual cycle rankine waste heat recovery cycle
US20040255587A1 (en) Organic rankine cycle system for use with a reciprocating engine
Vaja et al. Internal combustion engine (ICE) bottoming with organic Rankine cycles (ORCs)
Miyazaki et al. A combined power cycle using refuse incineration and LNG cold energy
US8438849B2 (en) Multi-level organic rankine cycle power system
Chacartegui et al. Alternative ORC bottoming cycles for combined cycle power plants
DE69927925T2 (en) Recovery of waste heat in an organic energy converter by means of an intermediate liquid circuit
US8544274B2 (en) Energy recovery system using an organic rankine cycle
EP1552114B1 (en) Method of converting energy
US20100263380A1 (en) Cascaded organic rankine cycle (orc) system using waste heat from a reciprocating engine
ES2634552T3 (en) Procedure and system to generate energy from a heat source
JP2008519205A (en) Cascade power system
US7458217B2 (en) System and method for utilization of waste heat from internal combustion engines
Song et al. Thermodynamic analysis and performance optimization of an Organic Rankine Cycle (ORC) waste heat recovery system for marine diesel engines
US8186161B2 (en) System and method for controlling an expansion system
Rahbar et al. Review of organic Rankine cycle for small-scale applications
CA2796831C (en) Organic motive fluid based waste heat recovery system
Yağlı et al. Parametric optimization and exergetic analysis comparison of subcritical and supercritical organic Rankine cycle (ORC) for biogas fuelled combined heat and power (CHP) engine exhaust gas waste heat
US7594399B2 (en) System and method for power generation in Rankine cycle

Legal Events

Date Code Title Description
AS Assignment

Owner name: GENERAL ELECTRIC COMPANY, NEW YORK

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:AST, GABOR;FREY, THOMAS JOHANNES;HUCK, PIERRE SEBASTIEN;AND OTHERS;SIGNING DATES FROM 20090625 TO 20090630;REEL/FRAME:022890/0100

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION