WO2014164620A1 - Système de pompe et de soupape pour commander un circuit de fluide de travail supercritique dans un système de moteur thermique - Google Patents

Système de pompe et de soupape pour commander un circuit de fluide de travail supercritique dans un système de moteur thermique Download PDF

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Publication number
WO2014164620A1
WO2014164620A1 PCT/US2014/023026 US2014023026W WO2014164620A1 WO 2014164620 A1 WO2014164620 A1 WO 2014164620A1 US 2014023026 W US2014023026 W US 2014023026W WO 2014164620 A1 WO2014164620 A1 WO 2014164620A1
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WIPO (PCT)
Prior art keywords
working fluid
pump
loop controller
governing loop
inlet
Prior art date
Application number
PCT/US2014/023026
Other languages
English (en)
Inventor
Brett A. BOWAN
Original Assignee
Echogen Power Systems, L.L.C.
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 Echogen Power Systems, L.L.C. filed Critical Echogen Power Systems, L.L.C.
Publication of WO2014164620A1 publication Critical patent/WO2014164620A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating

Definitions

  • Waste heat is often created as a byproduct of industrial processes where flowing streams of high-temperature liquids, gases, or fluids must be exhausted into the environment or removed in some way in an effort to maintain the operating temperatures of the industrial process equipment.
  • Some industrial processes utilize heat exchanger devices to capture and recycle waste heat back into the process via other process streams.
  • the capturing and recycling of waste heat is generally infeasible by industrial processes that utilize high temperatures or have insufficient mass flow or other unfavorable conditions.
  • Waste heat can be converted into useful energy by a variety of turbine generator or heat engine systems that employ thermodynamic methods, such as Rankine cycles.
  • Rankine cycles and similar thermodynamic methods are typically steam-based processes that recover and utilize waste heat to generate steam for driving a turbine, turbo, or other expander connected to an electric generator.
  • An organic Rankine cycle utilizes an organic solvent as the working fluid instead of water, as used during a traditional Rankine cycle.
  • the organic solvent has a lower boiling-point than water.
  • Exemplary lower boiling-point working fluids include hydrocarbons, such as light hydrocarbons (e.g., propane or butane) and halogenated hydrocarbon, such as hydrochlorofluorocarbons (HCFCs) or hydrofluorocarbons (H FCs) (e.g., R245fa) .
  • hydrocarbons such as light hydrocarbons (e.g., propane or butane) and halogenated hydrocarbon, such as hydrochlorofluorocarbons (HCFCs) or hydrofluorocarbons (H FCs) (e.g., R245fa) .
  • HCFCs hydrochlorofluorocarbons
  • H FCs hydrofluorocarbons
  • a turbine driven pump such as a turbo pump
  • the control of a turbine driven pump is quite relevant to the operation and efficiency of the supercritical advanced Rankine cycle process.
  • the control of the turbine driven pump is often not precise enough to achieve the most efficient or maximum operating conditions without damaging the turbine driven pump.
  • a system start pump may be used to initiate the cycle and build high system pressure P2.
  • the system inlet pressure P1 tends to decrease and "fall" to a level in which the supercritical process loses energy and the start pump may be catastrophically damaged by way of cavitation.
  • the lack of synchronization and interaction between the control valves detrimentally affects the high system pressure P2 and in turn, reduces the efficiency of the heat engine.
  • Embodiments of the invention generally provide a heat engine system and a method for generating electricity.
  • the heat engine system contains a turbo pump throttle valve fluidly coupled to the working fluid circuit and disposed upstream of a turbine inlet on a drive turbine of a turbo pump, a primary governing loop controller configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the turbo pump throttle valve, and a secondary governing loop controller configured to increase the inlet pressure if an undesirable value of the inlet pressure is less than the predetermined threshold value by modulating the turbo pump throttle valve.
  • the heat engine system contains a start pump bypass valve fluidly coupled to a start pump bypass line and disposed downstream of a pump outlet on the pump portion of the start pump, a primary governing loop controller configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the start pump bypass valve to adjust the flow of the working fluid, and a secondary governing loop controller configured to increase the inlet pressure if an undesirable value of the inlet pressure is less than the predetermined threshold value by modulating the start pump bypass valve.
  • the heat engine system contains a turbo pump bypass valve fluidly coupled to a turbo pump bypass line and disposed downstream of a pump outlet on the pump portion of the turbo pump, a primary governing loop controller configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the turbo pump bypass valve to adjust the flow of the working fluid, and a secondary governing loop controller configured to increase the inlet pressure if an undesirable value of the inlet pressure is less than the predetermined threshold value by modulating the turbo pump bypass valve.
  • the heat engine system and the method for generating electricity are configured to efficiently generate valuable electrical energy from thermal energy, such as a heated stream (e.g., a waste heat stream).
  • the heat engine system utilizes a working fluid in a supercritical state (e.g., SC-CO2) and/or a subcritical state (e.g. , sub-CC>2) contained within a working fluid circuit for capturing or otherwise absorbing thermal energy of the heated stream with one or more heat exchangers.
  • the thermal energy is transformed to mechanical energy by a power turbine and subsequently transformed to electrical energy by the power generator coupled to the power turbine.
  • the heat engine system contains several integrated sub-systems managed by a process control system for maximizing the efficiency of the heat engine system while generating electricity.
  • a method for generating electricity with a heat engine system includes controlling and circulating a working fluid within a working fluid circuit by a turbo pump.
  • the working fluid circuit has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state .
  • the method includes transferring thermal energy from a heat source stream to the working fluid by at least a primary heat exchanger fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit.
  • the method further includes flowing the working fluid into and through a power turbine while converting the thermal energy from the working fluid to mechanical energy of the power turbine and converting the mechanical energy into electrical energy by a power generator coupled to the power turbine.
  • the method also includes monitoring an inlet pressure at a pump inlet on a pump portion of the turbo pump via a process control system operatively connected to the working fluid circuit and controlling a turbo pump throttle valve by a primary governing loop controller.
  • the process control system contains a control algorithm embedded in a computer system and the control algorithm contains the primary governing loop controller as well as a secondary governing loop controller.
  • the turbo pump throttle valve may be fluidly coupled to the high pressure side of the working fluid circuit and disposed upstream of a turbine inlet on a drive turbine of the turbo pump.
  • the primary governing loop controller may be configured to control the speed of the turbo pump by modulating the turbo pump throttle valve to adjust the flow of the working fluid to the turbine inlet.
  • the method further includes detecting an undesirable value of the inlet pressure via the process control system and subsequently activating the secondary governing loop controller embedded in the process control system and deactivating the primary governing loop controller.
  • the undesirable value is less than a predetermined threshold value of the inlet pressure and the secondary governing loop controller is configured to increase the inlet pressure at the pump inlet by modulating the turbo pump throttle valve to adjust the flow of the working fluid through the turbine inlet for controlling the speed of the turbo pump.
  • the method includes controlling the turbo pump throttle valve by the secondary governing loop controller while circulating the working fluid within the working fluid circuit, detecting a desirable value of the inlet pressure via the process control system, and subsequently activating the primary governing loop controller and deactivating the secondary governing loop controller once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • a method for generating electricity with a heat engine system includes controlling and circulating a working fluid within a working fluid circuit by a motorized start pump.
  • the working fluid circuit has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state.
  • the method includes transferring thermal energy from a heat source stream to the working fluid by at least a primary heat exchanger fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit.
  • the method further includes flowing the working fluid into and through a power turbine while converting the thermal energy from the working fluid to mechanical energy of the power turbine and converting the mechanical energy into electrical energy by a power generator coupled to the power turbine.
  • the method also includes monitoring an inlet pressure at a pump inlet on a pump portion of the start pump via a process control system operatively connected to the working fluid circuit and controlling a start pump bypass valve by a primary governing loop controller embedded in the process control system.
  • the start pump bypass valve may be fluidly coupled to a start pump bypass line and disposed downstream of a pump outlet on the pump portion of the start pump.
  • the start pump bypass line is generally configured to recirculate the working fluid through the condenser while avoiding the heat exchanger and/or the power turbine.
  • One end of the start pump bypass line may be fluidly coupled to the high pressure side of the working fluid circuit at a point downstream of the pump outlet on the pump portion of the start pump.
  • the other end of the start pump bypass line may be fluidly coupled to the low pressure side of the working fluid circuit at a point downstream of a turbine outlet on the power turbine.
  • the primary governing loop controller may be configured to control the inlet pressure and other pressures within the working fluid circuit by modulating the start pump bypass valve to adjust the flow of the working fluid.
  • the method includes detecting an undesirable value of the inlet pressure via the process control system and subsequently activating a secondary governing loop controller embedded in the process control system and deactivating the primary governing loop controller.
  • the undesirable value is generally less than a predetermined threshold value of the inlet pressure and the secondary governing loop controller may be configured to increase the inlet pressure at the pump inlet by adjusting the start pump bypass valve and the flow of the working fluid.
  • the method also includes controlling the start pump bypass valve by the secondary governing loop controller while circulating the working fluid within the working fluid circuit, detecting a desirable value of the inlet pressure via the process control system, and subsequently activating the primary governing loop controller and deactivating the secondary governing loop controller once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • the process control system contains a control algorithm embedded in a computer system and the control algorithm contains the primary governing loop controller and the secondary governing loop controller.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a sliding mode controller, a pressure mode controller, a multi-mode controller, derivatives thereof, or combinations thereof.
  • the secondary governing loop controller in a deactivated or overridden mode overrides the primary governing loop controller in an activate mode upon detecting the undesirable value of the inlet pressure via the process control system.
  • the method further includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in a deactivated or overridden mode as the secondary governing loop controller is in an activate mode.
  • the primary governing loop controller in a deactivated or overridden mode overrides the secondary governing loop controller in an activate mode upon detecting the desirable value of the inlet pressure via the process control system.
  • the method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in an activate mode as the secondary governing loop controller is in a deactivate mode.
  • a method for generating electricity with a heat engine system includes controlling and circulating a working fluid within a working fluid circuit by a turbo pump.
  • the working fluid circuit has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state and transferring thermal energy from a heat source stream to the working fluid by at least a primary heat exchanger fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit.
  • the method also includes flowing the working fluid into and through a power turbine while converting the thermal energy from the working fluid to mechanical energy of the power turbine and converting the mechanical energy into electrical energy by a power generator coupled to the power turbine.
  • the method further includes monitoring an inlet pressure at a pump inlet on a pump portion of the turbo pump via a process control system operatively connected to the working fluid circuit and controlling a turbo pump bypass valve by a primary governing loop controller embedded in the process control system.
  • the turbo pump bypass valve may be fluidly coupled to a turbo pump bypass line and disposed downstream of a pump outlet on the pump portion of the turbo pump.
  • the turbo pump bypass line is generally configured to recirculate the working fluid through the condenser while avoiding the heat exchanger and the power turbine.
  • One end of the turbo pump bypass line may be fluidly coupled to the high pressure side of the working fluid circuit at a point downstream of the pump outlet on the pump portion of the turbo pump.
  • the other end of the turbo pump bypass line may be fluidly coupled to the low pressure side of the working fluid circuit at a point downstream of a turbine outlet on the power turbine.
  • the primary governing loop controller may be configured to control the inlet pressure and/or other pressures within the working fluid circuit, as well as to control the speed of the turbo pump by modulating the turbo pump bypass valve to adjust the flow of the working fluid.
  • the method further includes detecting an undesirable value of the inlet pressure via the process control system and subsequently activating a secondary governing loop controller embedded in the process control system and deactivating the primary governing loop controller.
  • the undesirable value is generally less than a predetermined threshold value of the inlet pressure.
  • the secondary governing loop controller may be configured to increase the inlet pressure at the pump inlet by modulating the turbo pump bypass valve to adjust the flow of the working fluid through the turbine inlet for controlling the speed of the turbo pump.
  • the method further includes controlling the turbo pump bypass valve by the secondary governing loop controller while circulating the working fluid within the working fluid circuit, detecting a desirable value of the inlet pressure via the process control system, and subsequently activating the primary governing loop controller and deactivating the secondary governing loop controller once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a feed forward mode controller, a sliding mode controller, a pressure mode controller, a multi-mode controller, derivatives thereof, or combinations thereof.
  • a power turbine throttle valve, a power turbine trim valve, and a turbo pump throttle valve may be fluidly coupled to the working fluid circuit and configured to control the inlet pressure by adjusting the flow of the working fluid within the working fluid circuit.
  • the method includes adjusting the turbo pump bypass valve by the primary governing loop controller or the secondary governing loop controller utilizing a feed forward mode controller.
  • the turbo pump bypass valve may be utilized to modulate the flow of the working fluid relative to anticipated adjustments of the power turbine throttle valve, the power turbine trim valve, and the turbo pump throttle valve.
  • Figure 1 illustrates an exemplary heat engine system, according to one or more embodiments disclosed herein.
  • Figure 2 illustrates another exemplary heat engine system, according to one or more embodiments disclosed herein.
  • Figure 3 is a flow charting illustrating a method for generating electricity with a heat engine system, according to one or more embodiments disclosed herein.
  • Figure 4 depicts a schematic diagram of a system controller configured to operate a turbo pump throttle valve, according to one or more embodiments disclosed herein.
  • Figure 5 is a flow charting illustrating another method for generating electricity with a heat engine system, according to one or more embodiments disclosed herein.
  • Figure 6 depicts a schematic diagram of a system controller configured to operate a start pump bypass valve, according to one or more embodiments disclosed herein.
  • Figure 7 is a flow charting illustrating another method for generating electricity with a heat engine system, according to one or more embodiments disclosed herein.
  • Figure 8 depicts a schematic diagram of a system controller configured to operate a turbo pump bypass valve, according to one or more embodiments disclosed herein. Detailed Description
  • Embodiments of the invention generally provide heat engine systems and methods for generating electricity via the heat engine systems.
  • Figure 1 depicts an exemplary heat engine system 90, which may also be referred to as a thermal engine system, an electrical generation system, a waste heat or other heat recovery system, and/or a thermal to electrical energy system, as described in one or more embodiments herein.
  • the heat engine system 90 contains a turbo pump throttle valve 263 fluidly coupled to a working fluid circuit 202 and disposed upstream of a turbine inlet on a drive turbine 264 of a turbo pump 260.
  • An inlet pressure at a pump inlet on a pump portion 262 of the turbo pump 260 is monitored by a process control system 204 operatively connected to the working fluid circuit 202.
  • a primary governing loop controller is configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the turbo pump throttle valve 263.
  • An undesirable value of the inlet pressure at the pump inlet on the pump portion 262 is less than a predetermined threshold value of the inlet pressure.
  • a secondary governing loop controller is activated and the primary governing loop controller is deactivated.
  • the first and secondary governing loop controllers for the turbo pump throttle valve 263 are independently embedded in a computer system 206 as part of a process control system 204.
  • the secondary governing loop controller is configured to increase the inlet pressure at the pump inlet on the pump portion 262 by modulating the turbo pump throttle valve 263 to adjust the flow of the working fluid through the turbine inlet on the drive turbine 264 while controlling the speed of the turbo pump 260.
  • the heat engine system 90 contains a start pump bypass valve 254 fluidly coupled to the working fluid circuit 202 by a start pump bypass line 224 and disposed downstream of a pump outlet on the pump portion 282 of the motorized start pump 280.
  • An inlet pressure at a pump inlet on a pump portion 282 of the motorized start pump 280 is monitored by the process control system 204 operatively connected to the working fluid circuit 202.
  • a primary governing loop controller is configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the start pump bypass valve 254 to adjust the flow of the working fluid passing through the start pump bypass line 224.
  • An undesirable value of the inlet pressure at the pump inlet on the pump portion 282 is less than a predetermined threshold value of the inlet pressure.
  • a secondary governing loop controller is activated and the primary governing loop controller is deactivated.
  • the first and secondary governing loop controllers for the start pump bypass valve 254 are independently embedded in the process control system 204.
  • the secondary governing loop controller is configured to increase the inlet pressure at the pump inlet on the pump portion 282 by modulating the start pump bypass valve 254 to adjust the flow of the working fluid through the start pump bypass line 224.
  • the heat engine system 90 contains a turbo pump bypass valve 256 fluidly coupled to the working fluid circuit 202 by a turbo pump bypass line 226 and disposed downstream of a pump outlet on the pump portion 262 of the turbo pump 260.
  • An inlet pressure at a pump inlet on the pump portion 262 of the turbo pump 260 is monitored by the process control system 204 operatively connected to the working fluid circuit 202.
  • a primary governing loop controller configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating the turbo pump bypass valve 256 to adjust the flow of the working fluid passing through the turbo pump bypass line 226.
  • An undesirable value of the inlet pressure at the pump inlet on the pump portion 262 is less than a predetermined threshold value of the inlet pressure.
  • a secondary governing loop controller is activated and the primary governing loop controller is deactivated.
  • the first and secondary governing loop controllers for the turbo pump bypass valve 256 are independently embedded in the process control system 204.
  • the secondary governing loop controller is configured to increase the inlet pressure at the pump inlet on the pump portion 262 by modulating the turbo pump bypass valve 256 to adjust the flow of the working fluid through the turbo pump bypass line 226.
  • the heat engine system 90 further contains a waste heat system 100 and a power generation system 220 coupled to and in thermal communication with each other via a working fluid circuit 202.
  • the working fluid circuit 202 contains the working fluid (e.g., sc-C0 2 ) and has a high pressure side and a low pressure side.
  • a heat source stream 1 10 flows through heat exchangers 120, 130, and/or 150 disposed within the waste heat system 100.
  • the heat exchangers 120, 130, and/or 150 may be fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202, configured to be fluidly coupled to and in thermal communication with a heat source stream 1 10, and configured to transfer thermal energy from the heat source stream 1 10 to the working fluid.
  • Thermal energy is absorbed by the working fluid within the working fluid circuit 202, and the heated working fluid is circulated through a power turbine 228 within the power generation system 220.
  • the power turbine 228 is disposed between the high pressure side and the low pressure side of the working fluid circuit 202 and fluidly coupled to and in thermal communication with the working fluid.
  • the power turbine 228 is configured to convert thermal energy to mechanical energy by a pressure drop in the working fluid flowing between the high and the low pressure sides of the working fluid circuit 202.
  • a power generator 240 is coupled to the power turbine 228 and configured to convert the mechanical energy into electrical energy.
  • a power outlet 242 may be electrically coupled to the power generator 240 and configured to transfer the electrical energy from the power generator 240 to an electrical grid 244.
  • the power generation system 220 generally contains a driveshaft 230 and a gearbox 232 coupled between the power turbine 228 and the power generator 240.
  • the heat engine system 90 generally contains several pumps, such as the turbo pump 260 and the start pump 280, disposed within the working fluid circuit 202 and fluidly coupled between the low pressure side and the high pressure side of the working fluid circuit 202.
  • the turbo pump 260 and the start pump 280 are operative to circulate the working fluid throughout the working fluid circuit 202.
  • the start pump 280 has a pump portion 282 and a motor-drive portion 284.
  • the start pump 280 is generally an electric motorized pump or a mechanical motorized pump, and may be a variable frequency driven pump.
  • the turbo pump 260 has a pump portion 262 and a drive turbine 264.
  • the pump portion 262 of the turbo pump 260 may be disposed between the high pressure side and the low pressure side of the working fluid circuit 202.
  • the pump inlet on the pump portion 262 is generally disposed in the low pressure side and the pump outlet on the pump portion 262 is generally disposed in the high pressure side.
  • the drive turbine 264 of the turbo pump 260 may be fluidly coupled to the working fluid circuit 202 downstream of the heat exchanger 150 and the pump portion 262 of the turbo pump 260 may be fluidly coupled to the working fluid circuit 202 upstream of the heat exchanger 120.
  • a secondary heat exchanger such as heat exchanger 150, may be fluidly coupled to and in thermal communication with the heat source stream 1 10 and independently fluidly coupled to and in thermal communication with the working fluid in the working fluid circuit 202.
  • the heated working fluid may be utilized to move or otherwise power the drive turbine 264.
  • the process control system 204 contains a control algorithm embedded in a computer system 206 and the control algorithm contains the primary governing loop controller and the secondary governing loop controller.
  • the primary governing loop controller may be configured to maintain a desirable value of the inlet pressure at or greater than a predetermined threshold value by modulating, adjusting, or otherwise controlling the turbo pump throttle valve 263, the start pump bypass valve 254, and/or the turbo pump bypass valve 256.
  • the secondary governing loop controller may be configured to increase an undesirable value of the inlet pressure at the pump inlet to a desirable value by modulating , adjusting, or otherwise controlling the turbo pump throttle valve 263, the start pump bypass valve 254, and/or the turbo pump bypass valve 256.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a feed forward mode controller, a sliding mode controller, a pressure mode controller, a multi-mode controller, derivatives thereof, or combinations thereof.
  • the process control system 204 may include one or more non-transitory, tangible, machine-readable media, such as read-only memory (ROM) , random access memory (RAM), solid state memory (e .g. , flash memory), floppy diskettes, CD-ROMs, hard drives, universal serial bus (USB) drives, any other computer readable storage medium, or any combination thereof.
  • the storage media may store encoded instructions, such as firmware, that may be executed by the process control system 204 or any of the other controllers disclosed herein (e.g., the primary loop governing controller, the secondary loop governing controller, etc.) to operate the logic or portions of the logic presented in the methods disclosed herein.
  • the heat engine system 90 may include computer code disposed on a computer-readable storage medium or a process controller that includes such a computer-readable storage medium.
  • the computer code may include instructions for initiating a control function to alternate the position of one or more of the turbo pump throttle valve 263, the turbo pump bypass valve 256, and the start pump bypass valve 254.
  • a power turbine throttle valve 250 and a power turbine trim valve 252 may be fluidly coupled to the working fluid circuit 202 and configured to control the inlet pressure by adjusting the flow of the working fluid within the working fluid circuit 202.
  • the power turbine throttle valve 250 may be fluidly coupled to the bypass line 246 and the power turbine trim valve 252 may be fluidly coupled to the bypass line 248.
  • the turbo pump bypass valve 256 is configured to modulate the flow of the working fluid relative to anticipated adjustments of the power turbine throttle valve 250, the power turbine trim valve 252, and the turbo pump throttle valve 263.
  • the turbo pump bypass valve 256 may be modulated, adjusted, or otherwise controlled by the primary governing loop controller and/or the secondary governing loop controller utilizing a feed forward mode controller.
  • Figure 2 depicts an exemplary heat engine system 200 that contains the process system 210 and the power generation system 220 fluidly coupled to and in thermal communication with the waste heat system 100 via the working fluid circuit 202, as described in one of more embodiments herein.
  • the heat engine system 200 may be referred to as a thermal engine system, an electrical generation system, a waste heat or other heat recovery system, and/or a thermal to electrical energy system, as described in one of more embodiments herein.
  • the heat engine system 200 is generally configured to encompass one or more elements of a Rankine cycle, a derivative of a Rankine cycle, or another thermodynamic cycle for generating electrical energy from a wide range of thermal sources.
  • the heat engine system 200 depicted in Figure 2 and the heat engine system 90 of Figure 1 share many common components. It should be noted that like numerals shown in the Figures and discussed herein represent like components throughout the multiple embodiments disclosed herein.
  • a method 20 for generating electricity with the heat engine system 90 or 200 includes controlling and circulating the working fluid within the working fluid circuit 202 by a turbo pump 260 (block 22), wherein the working fluid circuit 202 has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state.
  • the method 20 also includes transferring thermal energy from a heat source stream 1 10 to the working fluid by the heat exchanger 120 fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202 (block 24).
  • the method 20 further includes flowing the working fluid into and through the power turbine 228 and converting the thermal energy from the working fluid to mechanical energy of the power turbine 228 (block 26) and converting the mechanical energy into electrical energy by a power generator 240 coupled to the power turbine 228 (block 28).
  • the method 20 also includes monitoring an inlet pressure at a pump inlet on a pump portion 262 of the turbo pump 260 via a process control system 204 operatively connected to the working fluid circuit 202 (block 30) and controlling a turbo pump throttle valve 263 by a primary governing loop controller embedded in the process control system 204 (block 32).
  • the turbo pump throttle valve 263 may be fluidly coupled to the high pressure side of the working fluid circuit 202 and disposed upstream of a turbine inlet on a drive turbine 264 of the turbo pump 260, and the primary governing loop controller may be configured to control the inlet pressure and the speed of the turbo pump 260 by modulating the turbo pump throttle valve 263 to adjust the flow of the working fluid to the turbine inlet.
  • the method 20 further includes detecting an undesirable value of the inlet pressure via the process control system 204 (block 34) and subsequently activating a secondary governing loop controller embedded in the process control system 204 (block 36) and deactivating the primary governing loop controller (block 38).
  • the undesirable value is less than a predetermined threshold value of the inlet pressure
  • the secondary governing loop controller is configured to increase the inlet pressure at the pump inlet by modulating the turbo pump throttle valve 263 to adjust the flow of the working fluid through the turbine inlet for controlling the speed of the turbo pump 260.
  • the method 20 includes controlling the turbo pump throttle valve 263 by the secondary governing loop controller (block 40) while circulating the working fluid within the working fluid circuit 202, detecting a desirable value of the inlet pressure via the process control system 204 (block 42), and subsequently activating the primary governing loop controller (block 44) and deactivating the secondary governing loop controller (block 46) once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • FIG. 4 depicts a schematic diagram of a system controller 300 configured to operate the turbo pump throttle valve 263, according to one or more embodiments disclosed herein.
  • the process control system 204 contains a control algorithm embedded in the computer system 206, and the control algorithm contains the primary governing loop controller and the secondary governing loop controller configured to operate the turbo pump throttle valve 263.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a sliding mode controller, a pressure mode controller, a multi- mode controller, derivatives thereof, or combinations thereof.
  • the secondary governing loop controller in a deactivated or overridden mode overrides the primary governing loop controller in an activate mode upon detecting the undesirable value of the inlet pressure via the process control system 204.
  • the inlet pressure is monitored at the pump inlet by the primary governing loop controller in a deactivated or overridden mode as the secondary governing loop controller is in an activate mode.
  • the primary governing loop controller in a deactivated or overridden mode overrides the secondary governing loop controller in an activate mode upon detecting the desirable value of the inlet pressure via the process control system 204.
  • the method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in an activate mode, as the secondary governing loop controller is in a deactivated or overridden mode.
  • an inlet pressure (R) at the pump inlet on the pump portion 262 of the turbo pump 260 is generally less than 15 MPa, for example, about 10 MPa or less, such as within a range from about 5.2 MPa to about 8 MPa, more narrowly within a range from about 5.2 MPa to about 6.5 MPa, more narrowly within a range from about 5.2 MPa to about 6 MPa, and more narrowly within a range from about 5.5 MPa to about 6 MPa.
  • the desirable value of the inlet pressure at the pump inlet on the pump portion 262 of the turbo pump 260 may be about 5.2 MPa or greater, such as within a range from about 5.2 MPa to about 6.5 MPa, more narrowly within a range from about 5.5 MPa to about 6.0 MPa.
  • the undesirable value of the inlet pressure at the pump inlet on the pump portion 262 of the turbo pump 260 may be less than about 5.2 MPa, such as within a range from about 4 MPa to less than about 5.2 MPa.
  • An outlet pressure (P 0 ) at the pump outlet on the pump portion 262 of the turbo pump 260 is generally greater than 15 MPa, for example, about 20 MPa or greater, such as within a range from about 20 MPa to about 25 MPa, more narrowly within a range from about 21 MPa to about 24.5 MPa, and more narrowly within a range from about 23 MPa to about 24 MPa, such as about 23.5 MPa.
  • an inlet pressure at the turbine inlet on the drive turbine 264 of the turbo pump 260 is generally greater than 15 MPa, for example, about 20 MPa or greater, such as within a range from about 20 MPa to about 25 MPa, more narrowly within a range from about 21 MPa to about 24 MPa, and more narrowly within a range from about 22 MPa to about 23 MPa, such as about 22.5 MPa.
  • An outlet pressure at the turbine outlet on the drive turbine 264 of the turbo pump 260 is generally less than 15 MPa, for example, about 10 MPa or less, such as within a range from about 2 MPa to about 10 MPa, more narrowly within a range from about 4 MPa to about 8 MPa, and more narrowly within a range from about 5 MPa to about 7 MPa, such as about 6 MPa.
  • a method 50 for generating electricity with the heat engine system 90 or 200 includes controlling and circulating a working fluid within a working fluid circuit 202 by a start pump 280 (block 52), wherein the working fluid circuit 202 has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state, and transferring thermal energy from a heat source stream 1 10 to the working fluid by the heat exchanger 120 fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202 (block 54).
  • the method 50 further includes flowing the working fluid into and through the power turbine 228 and converting the thermal energy from the working fluid to mechanical energy of the power turbine 228 (block 56) and converting the mechanical energy into electrical energy by a power generator 240 coupled to the power turbine 228 (block 58).
  • the method 50 also includes monitoring an inlet pressure at a pump inlet on a pump portion 282 of the start pump 280 via a process control system 204 operatively connected to the working fluid circuit 202 (block 60) and controlling a start pump bypass valve 254 by a primary governing loop controller embedded in the process control system 204 (block 62).
  • the start pump bypass valve 254 may be fluidly coupled to a start pump bypass line 224 and disposed downstream of a pump outlet on the pump portion 282 of the start pump 280.
  • the start pump bypass line 224 is generally configured to recirculate the working fluid through the condenser 274 while avoiding the heat exchanger 150 and/or the power turbine 228.
  • a first end of the start pump bypass line 224 may be fluidly coupled to the high pressure side of the working fluid circuit 202 at a point downstream of the pump outlet on the pump portion 282 of the start pump 280.
  • the first end of the start pump bypass line 224 may be fluidly coupled to the working fluid circuit 202 between the pump portion 282 and the recuperator 218.
  • the other end of the start pump bypass line 224 may be fluidly coupled to the low pressure side of the working fluid circuit 202 at a point downstream of a turbine outlet on the power turbine 228.
  • the second end of the start pump bypass line 224 may be fluidly coupled to the working fluid circuit 202 upstream of the condenser 274, such as at a point on the fluid line 229 extending between the recuperator 218 and the condenser 274.
  • the primary governing loop controller may be configured to control the inlet pressure and other pressures within the working fluid circuit 202 by modulating the start pump bypass valve 254 to adjust the flow of the working fluid.
  • the method 50 includes detecting an undesirable value of the inlet pressure via the process control system 204 (block 64) and subsequently activating a secondary governing loop controller embedded in the process control system 204 (block 66) and deactivating the primary governing loop controller (block 68).
  • the undesirable value is generally less than a predetermined threshold value of the inlet pressure and the secondary governing loop controller may be configured to increase the inlet pressure at the pump inlet by adjusting the start pump bypass valve 254 and the flow of the working fluid.
  • the method 50 also includes controlling the start pump bypass valve 254 by the secondary governing loop controller while circulating the working fluid within the working fluid circuit 202 (block 70), detecting a desirable value of the inlet pressure via the process control system 204 (block 72), and subsequently activating the primary governing loop controller (block 74) and deactivating the secondary governing loop controller (block 76) once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • FIG. 6 depicts a schematic diagram of a system controller 400 configured to operate the start pump bypass valve 254, according to one or more embodiments disclosed herein.
  • the process control system 204 contains a control algorithm embedded in the computer system 206, and the control algorithm contains the primary governing loop controller and the secondary governing loop controller configured to operate the start pump bypass valve 254.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a sliding mode controller, a pressure mode controller, a multi- mode controller, derivatives thereof, or combinations thereof.
  • the secondary governing loop controller in a deactivated or overridden mode overrides the primary governing loop controller in an activate mode upon detecting the undesirable value of the inlet pressure via the process control system 204.
  • the method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in a deactivated or overridden mode as the secondary governing loop controller is in an activate mode.
  • the primary governing loop controller in a deactivated or overridden mode overrides the secondary governing loop controller in an activate mode upon detecting the desirable value of the inlet pressure via the process control system 204.
  • the method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in an activate mode as the secondary governing loop controller is in an inactivate mode.
  • the desirable value of the inlet pressure ( ) at the pump inlet on the pump portion 282 of the start pump is generally less than 15 MPa, for example, about 10 MPa or less, such as within a range from about 5.2 MPa to about 8 MPa, more narrowly within a range from about 5.2 MPa to about 6.5 MPa, more narrowly within a range from about 5.2 MPa to about 6 MPa, and more narrowly within a range from about 5.5 MPa to about 6 MPa.
  • the desirable value of the inlet pressure at the pump inlet on the pump portion 282 of the start pump 280 may be about 5.2 MPa or greater, such as within a range from about 5.2 MPa to about 6.5 MPa, more narrowly within a range from about 5.5 MPa to about 6.0 MPa.
  • the undesirable value of the inlet pressure at the pump inlet on the pump portion 282 of the start pump 280 may be less than about 5.2 MPa, such as within a range from about 4 MPa to less than about 5.2 MPa.
  • An outlet pressure (P 0 ) at the pump outlet on the pump portion 282 of the start pump 280 is generally greater than 15 MPa, for example, about 20 MPa or greater, such as within a range from about 20 MPa to about 25 MPa, more narrowly within a range from about 21 MPa to about 24.5 MPa, and more narrowly within a range from about 23 MPa to about 24 MPa, such as about 23.5 MPa.
  • a method 80 for generating electricity with the heat engine system 90 or 200 includes controlling and circulating a working fluid within a working fluid circuit 202 by a turbo pump (block 82), wherein the working fluid circuit 202 has a high pressure side and a low pressure side and at least a portion of the working fluid is in a supercritical state.
  • the method 80 also includes transferring thermal energy from a heat source stream 1 10 to the working fluid by the heat exchanger 120 fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202 (block 84).
  • the method 80 also includes flowing the working fluid into and through the power turbine 228 and converting the thermal energy from the working fluid to mechanical energy of the power turbine 228 (block 86) and converting the mechanical energy into electrical energy by a power generator 240 coupled to the power turbine 228 (block 88).
  • the method 80 further includes monitoring an inlet pressure at a pump inlet on a pump portion 262 of the turbo pump 260 via a process control system 204 operatively connected to the working fluid circuit 202 (block 89) and controlling a turbo pump bypass valve 256 by a primary governing loop controller embedded in the process control system 204 (block 91).
  • the turbo pump bypass valve 256 may be fluidly coupled to a turbo pump bypass line 226 and disposed downstream of a pump outlet on the pump portion 262 of the turbo pump 260.
  • the turbo pump bypass line 226 is generally configured to recirculate the working fluid through the condenser 274 while avoiding the heat exchanger 150 and/or the power turbine 228.
  • a first end of the turbo pump bypass line 226 may be fluidly coupled to the high pressure side of the working fluid circuit 202 at a point downstream of the pump outlet on the pump portion 262 of the turbo pump 260.
  • the first end of the turbo pump bypass line 226 may be fluidly coupled to the working fluid circuit 202 between the pump portion 262 and the recuperator 218.
  • the other end of the turbo pump bypass line 226 may be fluidly coupled to the low pressure side of the working fluid circuit 202 at a point downstream of a turbine outlet on the power turbine 228.
  • the second end of the turbo pump bypass line 226 may be fluidly coupled to the working fluid circuit 202 upstream of the condenser 274, such as a point on the fluid line 229 extending between the recuperator 218 and the condenser 274.
  • the primary governing loop controller may be configured to control the inlet pressure and/or other pressures within the working fluid circuit 202, as well as to control the speed of the turbo pump 260 by modulating the turbo pump bypass valve 256 to adjust the flow of the working fluid.
  • the method 80 also includes detecting an undesirable value of the inlet pressure via the process control system 204 (block 92), subsequently activating a secondary governing loop controller embedded in the process control system 204 (block 93) and deactivating the primary governing loop controller (block 94).
  • the undesirable value may be less than a predetermined threshold value of the inlet pressure.
  • the secondary governing loop controller may be configured to increase the inlet pressure at the pump inlet by modulating the turbo pump bypass valve 256 to adjust the flow of the working fluid through the turbine inlet for controlling the speed of the turbo pump 260.
  • the method 80 further includes controlling the turbo pump bypass valve 256 by the secondary governing loop controller while circulating the working fluid within the working fluid circuit 202 (block 95), detecting a desirable value of the inlet pressure via the process control system 204 (block 96), and subsequently activating the primary governing loop controller (block 97) and deactivating the secondary governing loop controller (block 98) once the desirable value is at or greater than the predetermined threshold value of the inlet pressure.
  • FIG. 8 depicts a schematic diagram of a system controller 500 configured to operate the turbo pump bypass valve 256, according to one or more embodiments disclosed herein.
  • the process control system 204 contains a control algorithm embedded in the computer system 206 and the control algorithm contains the primary governing loop controller and the secondary governing loop controller configured to operate the turbo pump bypass valve 256.
  • the primary governing loop controller and the secondary governing loop controller may independently be a system controller selected from a feed forward mode controller, a sliding mode controller, a pressure mode controller, a multi-mode controller, derivatives thereof, or combinations thereof.
  • the secondary governing loop controller in a deactivated or overridden mode overrides the primary governing loop controller in an activate mode upon detecting the undesirable value of the inlet pressure via the process control system 204.
  • a method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in a deactivated or overridden mode as the secondary governing loop controller is in an activate mode.
  • the primary governing loop controller in a deactivated or overridden mode overrides the secondary governing loop controller in an activate mode upon detecting the desirable value of the inlet pressure via the process control system 204.
  • the method includes monitoring the inlet pressure at the pump inlet by the primary governing loop controller in an activate mode as the secondary governing loop controller is in a deactivated or overridden mode.
  • Figure 2 depicts the working fluid circuit 202 containing the working fluid and having a high pressure side and a low pressure side, wherein at least a portion of the working fluid contains carbon dioxide in a supercritical state.
  • the working fluid contains carbon dioxide and at least a portion of the carbon dioxide is in a supercritical state.
  • the heat engine system 200 also has the heat exchanger 120 fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202, configured to be fluidly coupled to and in thermal communication with the heat source stream 1 10, and configured to transfer thermal energy from the heat source stream 1 10 to the working fluid within the working fluid circuit 202.
  • the heat exchanger 120 may be fluidly coupled to the working fluid circuit 202 upstream of the power turbine 228 and downstream of the recuperator 216.
  • the heat engine system 200 further contains the power turbine 228 disposed between the high pressure side and the low pressure side of the working fluid circuit 202, fluidly coupled to and in thermal communication with the working fluid, and configured to convert thermal energy to mechanical energy by a pressure drop in the working fluid flowing between the high and the low pressure sides of the working fluid circuit 202.
  • the heat engine system 200 also contains a power generator 240 coupled to the power turbine 228 and configured to convert the mechanical energy into electrical energy.
  • a power outlet 242 electrically coupled to the power generator 240 and configured to transfer the electrical energy from the power generator 240 to the electrical grid 244.
  • the heat engine system 200 further contains a turbo pump 260 that has a drive turbine 264 and a pump portion 262.
  • the pump portion 262 of the turbo pump 260 may be fluidly coupled to the low pressure side of the working fluid circuit 202 by an inlet configured to receive the working fluid from the low pressure side of the working fluid circuit 202, fluidly coupled to the high pressure side of the working fluid circuit 202 by an outlet configured to release the working fluid into the high pressure side of the working fluid circuit 202, and configured to circulate the working fluid within the working fluid circuit 202.
  • the drive turbine 264 of the turbo pump 260 may be fluidly coupled to the high pressure side of the working fluid circuit 202 by an inlet configured to receive the working fluid from the high pressure side of the working fluid circuit 202, fluidly coupled to the low pressure side of the working fluid circuit 202 by an outlet configured to release the working fluid into the low pressure side of the working fluid circuit 202, and configured to rotate the pump portion 262 of the turbo pump 260.
  • the heat engine system 200 further contains the heat exchanger 150 which is generally fluidly coupled to and in thermal communication with the heat source stream 1 10 and independently fluidly coupled to and in thermal communication with the high pressure side of the working fluid circuit 202, such that thermal energy may be transferred from the heat source stream 1 10 to the working fluid.
  • the heat exchanger 150 may be fluidly coupled to the working fluid circuit 202 downstream of the outlet of the pump portion 262 of the turbo pump 260 and upstream of the inlet of the drive turbine 264 of the turbo pump 260.
  • the turbo pump throttle valve 263 may be fluidly coupled to the working fluid circuit 202 downstream of the heat exchanger 150 and upstream of the inlet of the drive turbine 264 of the turbo pump 260.
  • turbo pump throttle valve 263 may be utilized to control the flowrate of the heated working fluid flowing from the heat exchanger 150 to the drive turbine 264 of the turbo pump 260.
  • the recuperator 216 may be fluidly coupled to the working fluid circuit 202 and configured to transfer thermal energy from the working fluid within the low pressure side to the working fluid within the high pressure side of the working fluid circuit 202.
  • a recuperator 218 may be fluidly coupled to the working fluid circuit 202 downstream of the outlet of the pump portion 262 of the turbo pump 260 and upstream of the heat exchanger 150 and configured to transfer thermal energy from the working fluid within the low pressure side to the working fluid within the high pressure side of the working fluid circuit 202.
  • FIG. 2 further depicts that the waste heat system 100 of the heat engine system 200 contains three heat exchangers (e.g. , the heat exchangers 120, 130, and 150) fluidly coupled to the high pressure side of the working fluid circuit 202 and in thermal communication with the heat source stream 1 10. Such thermal communication provides the transfer of thermal energy from the heat source stream 1 10 to the working fluid flowing throughout the working fluid circuit 202.
  • three heat exchangers e.g. , the heat exchangers 120, 130, and 150
  • two, three, or more heat exchangers may be fluidly coupled to and in thermal communication with the working fluid circuit 202, such as a primary heat exchanger, a secondary heat exchanger, a tertiary heat exchanger, respectively, the heat exchangers 120, 150, and 130, and/or an optional quaternary heat exchanger (not shown).
  • the heat exchanger 120 may be the primary heat exchanger fluidly coupled to the working fluid circuit 202 upstream of an inlet of the power turbine 228, the heat exchanger 150 may be the secondary heat exchanger fluidly coupled to the working fluid circuit 202 upstream of an inlet of the drive turbine 264 of the turbine pump 260, and the heat exchanger 130 may be the tertiary heat exchanger fluidly coupled to the working fluid circuit 202 upstream of an inlet of the heat exchanger 120.
  • the waste heat system 100 also contains an inlet 104 for receiving the heat source stream 1 10 and an outlet 106 for passing the heat source stream 1 10 out of the waste heat system 100.
  • the heat source stream 1 10 flows through and from the inlet 104, through the heat exchanger 120, through one or more additional heat exchangers, if fluidly coupled to the heat source stream 1 10, and to and through the outlet 106.
  • the heat source stream 1 10 flows through and from the inlet 104, through the heat exchangers 120, 150, and 130, respectively, and to and through the outlet 106.
  • the heat source stream 1 10 may be routed to flow through the heat exchangers 120, 130, 150, and/or additional heat exchangers in other desired orders.
  • the heat source stream 1 10 may be a waste heat stream such as, but not limited to, gas turbine exhaust stream, industrial process exhaust stream, or other combustion product exhaust streams, such as furnace or boiler exhaust streams.
  • the heat source stream 1 10 may be at a temperature within a range from about 100°C to about 1 ,000°C, or greater than 1 ,000°C, and in some examples, within a range from about 200°C to about 800°C, more narrowly within a range from about 300°C to about 600°C.
  • the heat source stream 1 10 may contain air, carbon dioxide, carbon monoxide, water or steam, nitrogen, oxygen, argon, derivatives thereof, or mixtures thereof.
  • the heat source stream 1 10 may derive thermal energy from renewable sources of thermal energy, such as solar or geothermal sources.
  • the types of working fluid that may be circulated, flowed, or otherwise utilized in the working fluid circuit 202 of the heat engine system 200 include carbon oxides, hydrocarbons, alcohols, ketones, halogenated hydrocarbons, ammonia, amines, aqueous, or combinations thereof.
  • Exemplary working fluids that may be utilized in the heat engine system 200 include carbon dioxide, ammonia, methane, ethane, propane, butane, ethylene, propylene, butylene, acetylene, methanol, ethanol, acetone, methyl ethyl ketone, water, derivatives thereof, or mixtures thereof.
  • Halogenated hydrocarbons may include hydrochlorofluorocarbons (HCFCs), hydrofluorocarbons (H FCs) (e.g. , 1 ,1 , 1 ,3,3- pentafluoropropane (R245fa)) , fluorocarbons, derivatives thereof, or mixtures thereof.
  • HCFCs hydrochlorofluorocarbons
  • H FCs hydrofluorocarbons
  • R245fa pentafluoropropane
  • the working fluid the working fluid circulated, flowed, or otherwise utilized in the working fluid circuit 202 of the heat engine system 200, and the other exemplary circuits disclosed herein may be or may contain carbon dioxide (CO2) and mixtures containing carbon dioxide.
  • CO2 carbon dioxide
  • the working fluid circuit 202 contains the working fluid in a supercritical state (e.g., SC-CO2).
  • Carbon dioxide utilized as the working fluid or contained in the working fluid for power generation cycles has many advantages over other compounds typical used as working fluids, since carbon dioxide has the properties of being non-toxic and non-flammable and is also easily available and relatively inexpensive.
  • a carbon dioxide system may be much more compact than systems using other working fluids.
  • the high density and volumetric heat capacity of carbon dioxide with respect to other working fluids makes carbon dioxide more "energy dense” meaning that the size of all system components can be considerably reduced without losing performance.
  • carbon dioxide C0 2
  • SC-CO2 supercritical carbon dioxide
  • sub-CC>2 subcritical carbon dioxide
  • use of the terms carbon dioxide (C0 2 ) , supercritical carbon dioxide (SC-CO2), or subcritical carbon dioxide (sub-CC>2) is not intended to be limited to carbon dioxide of any particular type, source, purity, or grade.
  • industrial grade carbon dioxide may be contained in and/or used as the working fluid without departing from the scope of the disclosure.
  • the working fluid in the working fluid circuit 202 may be a binary, ternary, or other working fluid blend.
  • the working fluid blend or combination can be selected for the unique attributes possessed by the fluid combination within a heat recovery system, as described herein.
  • one such fluid combination includes a liquid absorbent and carbon dioxide mixture enabling the combined fluid to be pumped in a liquid state to high pressure with less energy input than required to compress carbon dioxide.
  • the working fluid may be a combination of carbon dioxide (e.g., sub- CO2 or SC-CO2) and one or more other miscible fluids or chemical compounds.
  • the working fluid may be a combination of carbon dioxide and propane, or carbon dioxide and ammonia, without departing from the scope of the disclosure.
  • the working fluid circuit 202 generally has a high pressure side and a low pressure side and contains a working fluid circulated within the working fluid circuit 202.
  • the use of the term "working fluid" is not intended to limit the state or phase of matter of the working fluid.
  • the working fluid or portions of the working fluid may be in a liquid phase, a gas phase, a fluid phase, a subcritical state, a supercritical state , or any other phase or state at any one or more points within the heat engine system 200 or thermodynamic cycle.
  • the working fluid is in a supercritical state over certain portions of the working fluid circuit 202 of the heat engine system 200 (e.g. , a high pressure side) and in a subcritical state over other portions of the working fluid circuit 202 of the heat engine system 200 (e.g., a low pressure side).
  • Figure 2 depicts the high and low pressure sides of the working fluid circuit
  • thermodynamic cycle may be operated such that the working fluid is maintained in either a supercritical or subcritical state throughout the entire working fluid circuit 202 of the heat engine system 200.
  • the high pressure side of the working fluid circuit 202 contains the working fluid (e.g., sc-C0 2 ) at a pressure of about 15 MPa or greater, such as about 17 MPa or greater or about 20 MPa or greater.
  • the high pressure side of the working fluid circuit 202 may have a pressure within a range from about 15 MPa to about 30 MPa, more narrowly within a range from about 16 MPa to about 26 MPa, more narrowly within a range from about 17 MPa to about 25 MPa, and more narrowly within a range from about 17 MPa to about 24 MPa, such as about 23.3 MPa.
  • the high pressure side of the working fluid circuit 202 may have a pressure within a range from about 20 MPa to about 30 MPa, more narrowly within a range from about 21 MPa to about 25 MPa, and more narrowly within a range from about 22 MPa to about 24 MPa, such as about 23 MPa.
  • the low pressure side of the working fluid circuit 202 contains the working fluid (e.g., C0 2 or sub-C0 2 ) at a pressure of less than 15 MPa, such as about 12 MPa or less or about 10 MPa or less.
  • the low pressure side of the working fluid circuit 202 may have a pressure within a range from about 4 MPa to about 14 MPa, more narrowly within a range from about 6 MPa to about 13 MPa, more narrowly within a range from about 8 MPa to about 12 MPa, and more narrowly within a range from about 10 MPa to about 1 1 MPa, such as about 10.3 MPa.
  • the low pressure side of the working fluid circuit 202 may have a pressure within a range from about 2 MPa to about 10 MPa, more narrowly within a range from about 4 MPa to about 8 MPa, and more narrowly within a range from about 5 MPa to about 7 MPa, such as about 6 MPa.
  • the high pressure side of the working fluid circuit 202 may have a pressure within a range from about 17 MPa to about 23.5 MPa, and more narrowly within a range from about 23 MPa to about 23.3 MPa while the low pressure side of the working fluid circuit 202 may have a pressure within a range from about 8 MPa to about 1 1 MPa, and more narrowly within a range from about 10.3 MPa to about 1 1 MPa.
  • the heat engine system 200 further contains the power turbine 228 disposed between the high pressure side and the low pressure side of the working fluid circuit 202, disposed downstream of the heat exchanger 120, and fluidly coupled to and in thermal communication with the working fluid .
  • the power turbine 228 is configured to convert a pressure drop in the working fluid to mechanical energy whereby the absorbed thermal energy of the working fluid is transformed to mechanical energy of the power turbine 228. Therefore, the power turbine 228 is an expansion device capable of transforming a pressurized fluid into mechanical energy, generally, transforming high temperature and pressure fluid into mechanical energy, such as rotating a shaft.
  • the power turbine 228 may contain or be a turbine, a turbo, an expander, or another device for receiving and expanding the working fluid discharged from the heat exchanger 120.
  • the power turbine 228 may have an axial construction or radial construction and may be a single-staged device or a multi-staged device.
  • Exemplary turbines that may be utilized in power turbine 228 include an expansion device, a geroler, a gerotor, a valve, other types of positive displacement devices such as a pressure swing, a turbine, a turbo, or any other device capable of transforming a pressure or pressure/enthalpy drop in a working fluid into mechanical energy.
  • a variety of expanding devices are capable of working within the inventive system and achieving different performance properties that may be utilized as the power turbine 228.
  • the power turbine 228 is generally coupled to the power generator 240 by the driveshaft 230.
  • a gearbox 232 is generally disposed between the power turbine 228 and the power generator 240 and adjacent or encompassing the driveshaft 230.
  • the driveshaft 230 may be a single piece or contain two or more pieces coupled together. In one example, a first segment of the driveshaft 230 extends from the power turbine 228 to the gearbox 232, a second segment of the driveshaft 230 extends from the gearbox 232 to the power generator 240, and multiple gears are disposed between and coupled to the two segments of the driveshaft 230 within the gearbox 232.
  • the heat engine system 200 also provides for the delivery of a portion of the working fluid, seal gas, bearing gas, air, or other gas into a chamber or housing , such as a housing 238 within the power generation system 220 for purposes of cooling one or more parts of the power turbine 228.
  • the driveshaft 230 includes a seal assembly (not shown) designed to prevent or capture any working fluid leakage from the power turbine 228.
  • a working fluid recycle system may be implemented along with the seal assembly to recycle seal gas back into the working fluid circuit 202 of the heat engine system 200.
  • the power generator 240 may be a generator, an alternator (e.g., permanent magnet alternator), or other device for generating electrical energy, such as transforming mechanical energy from the driveshaft 230 and the power turbine 228 to electrical energy.
  • a power outlet 242 is electrically coupled to the power generator 240 and configured to transfer the generated electrical energy from the power generator 240 and to an electrical grid 244.
  • the electrical grid 244 may be or include an electrical grid, an electrical bus (e.g. , plant bus) , power electronics, other electric circuits, or combinations thereof.
  • the electrical grid 244 generally contains at least one alternating current bus, alternating current grid, alternating current circuit, or combinations thereof.
  • the power generator 240 is a generator and is electrically and operably connected to the electrical grid 244 via the power outlet 242. In another example, the power generator 240 is an alternator and is electrically and operably connected to power electronics (not shown) via the power outlet 242. In another example, the power generator 240 is electrically connected to power electronics which are electrically connected to the power outlet 242.
  • the power electronics may be configured to convert the electrical power into desirable forms of electricity by modifying electrical properties, such as voltage, current, or frequency.
  • the power electronics may include converters or rectifiers, inverters, transformers, regulators, controllers, switches, resistors, storage devices, and other power electronic components and devices.
  • the power generator 240 may contain, be coupled with, or be other types of load receiving equipment, such as other types of electrical generation equipment, rotating equipment, a gearbox (e.g. , gearbox 232) , or other device configured to modify or convert the shaft work created by the power turbine 228.
  • the power generator 240 is in fluid communication with a cooling loop having a radiator and a pump for circulating a cooling fluid, such as water, thermal oils, and/or other suitable refrigerants.
  • the cooling loop may be configured to regulate the temperature of the power generator 240 and power electronics by circulating the cooling fluid to draw away generated heat.
  • the heat engine system 200 also provides for the delivery of a portion of the working fluid into a chamber or housing of the power turbine 228 for purposes of cooling one or more parts of the power turbine 228.
  • the selection of the site within the heat engine system 200 from which to obtain a portion of the working fluid is critical because introduction of this portion of the working fluid into the power generator 240 should respect or not disturb the pressure balance and stability of the power generator 240 during operation. Therefore, the pressure of the working fluid delivered into the power generator 240 for purposes of cooling is the same or substantially the same as the pressure of the working fluid at an inlet of the power turbine 228.
  • the working fluid is conditioned to be at a desired temperature and pressure prior to being introduced into the power turbine 228.
  • the recuperators 216 and 218 may be fluidly coupled to the working fluid circuit 202 in series with each other.
  • the recuperators 216 and 218 are operative to transfer thermal energy between the high pressure side and the low pressure side of the working fluid circuit 202.
  • the recuperator 216 may be fluidly coupled to the low pressure side of the working fluid circuit 202, disposed downstream of a working fluid outlet on the power turbine 228, and disposed upstream of the recuperator 218 and/or the condenser 274.
  • the recuperator 216 is configured to remove at least a portion of thermal energy from the working fluid discharged from the power turbine 228.
  • the recuperator 216 is also fluidly coupled to the high pressure side of the working fluid circuit 202, disposed upstream of the heat exchanger 120 and/or a working fluid inlet on the power turbine 228, and disposed downstream of the heat exchanger 130.
  • the recuperator 216 is configured to increase the amount of thermal energy in the working fluid prior to flowing into the heat exchanger 120 and/or the power turbine 228. Therefore, the recuperator 216 is operative to transfer thermal energy between the high pressure side and the low pressure side of the working fluid circuit 202.
  • the recuperator 216 may be a heat exchanger configured to cool the low pressurized working fluid discharged or downstream of the power turbine 228 while heating the high pressurized working fluid entering into or upstream of the heat exchanger 120 and/or the power turbine 228.
  • the recuperator 218 may be fluidly coupled to the low pressure side of the working fluid circuit 202, disposed downstream of a working fluid outlet on the power turbine 228 and/or the recuperator 216, and disposed upstream of the condenser 274.
  • the recuperator 218 is configured to remove at least a portion of thermal energy from the working fluid discharged from the power turbine 228 and/or the recuperator 216.
  • the recuperator 218 is also fluidly coupled to the high pressure side of the working fluid circuit 202, disposed upstream of the heat exchanger 150 and/or a working fluid inlet on a drive turbine 264 of turbo pump 260, and disposed downstream of a working fluid outlet on a pump portion 262 of turbo pump 260.
  • the recuperator 218 is configured to increase the amount of thermal energy in the working fluid prior to flowing into the heat exchanger 150 and/or the drive turbine 264. Therefore, the recuperator 218 is operative to transfer thermal energy between the high pressure side and the low pressure side of the working fluid circuit 202.
  • the recuperator 218 may be a heat exchanger configured to cool the low pressurized working fluid discharged or downstream of the power turbine 228 and/or the recuperator 216 while heating the high pressurized working fluid entering into or upstream of the heat exchanger 150 and/or the drive turbine 264.
  • a cooler or a condenser 274 may be fluidly coupled to and in thermal communication with the low pressure side of the working fluid circuit 202 and may be configured or operative to control a temperature of the working fluid in the low pressure side of the working fluid circuit 202.
  • the condenser 274 may be disposed downstream of the recuperators 216 and 218 and upstream of the start pump 280 and the turbopump 260.
  • the condenser 274 receives the cooled working fluid from the recuperator 218 and further cools and/or condenses the working fluid which may be recirculated throughout the working fluid circuit 202.
  • the condenser 274 is a cooler and may be configured to control a temperature of the working fluid in the low pressure side of the working fluid circuit 202 by transferring thermal energy from the working fluid in the low pressure side to a cooling loop or system outside of the working fluid circuit 202.
  • a cooling media or fluid is generally utilized in the cooling loop or system by the condenser 274 for cooling the working fluid and removing thermal energy outside of the working fluid circuit 202.
  • the cooling media or fluid flows through, over, or around while in thermal communication with the condenser 274. Thermal energy in the working fluid is transferred to the cooling fluid via the condenser 274. Therefore, the cooling fluid is in thermal communication with the working fluid circuit 202, but not fluidly coupled to the working fluid circuit 202.
  • the condenser 274 may be fluidly coupled to the working fluid circuit 202 and independently fluidly coupled to the cooling fluid.
  • the cooling fluid may contain one or multiple compounds and may be in one or multiple states of matter.
  • the cooling fluid may be a media or fluid in a gaseous state, a liquid state, a subcritical state, a supercritical state, a suspension, a solution, derivatives thereof, or combinations thereof.
  • the condenser 274 is generally fluidly coupled to a cooling loop or system (not shown) that receives the cooling fluid from a cooling fluid return 278a and returns the warmed cooling fluid to the cooling loop or system via a cooling fluid supply 278b.
  • the cooling fluid may be water, carbon dioxide, or other aqueous and/or organic fluids (e.g., alcohols and/or glycols), air or other gases, or various mixtures thereof that is maintained at a lower temperature than the temperature of the working fluid.
  • the cooling media or fluid contains air or another gas exposed to the condenser 274, such as an air steam blown by a motorized fan or blower.
  • a filter 276 may be disposed along and in fluid communication with the cooling fluid line at a point downstream of the cooling fluid supply 278b and upstream of the condenser 274. In some examples, the filter 276 may be fluidly coupled to the cooling fluid line within the process system 210.
  • the heat engine system 200 further contains several pumps, such as a turbo pump 260 and a start pump 280, disposed within the working fluid circuit 202 and fluidly coupled between the low pressure side and the high pressure side of the working fluid circuit 202.
  • the turbo pump 260 and the start pump 280 are operative to circulate the working fluid throughout the working fluid circuit 202.
  • the start pump 280 is generally a motorized pump and may be utilized to initially pressurize and circulate the working fluid in the working fluid circuit 202. Once a predetermined pressure, temperature, and/or flowrate of the working fluid is obtained within the working fluid circuit 202, the start pump 280 may be taken off line, idled, or turned off and the turbo pump 260 is utilize to circulate the working fluid during the electricity generation process.
  • the working fluid enters each of the turbo pump 260 and the start pump 280 from the low pressure side of the working fluid circuit 202 and exits each of the turbo pump 260 and the start pump 280 from the high pressure side of the working fluid circuit 202.
  • the start pump 280 may be a motorized pump, such as an electric motorized pump, a mechanical motorized pump, or other type of pump.
  • the start pump 280 may be a variable frequency motorized drive pump and contains a pump portion 282 and a motor-drive portion 284.
  • the motor-drive portion 284 of the start pump 280 contains a motor and a drive including a driveshaft and gears.
  • the motor-drive portion 284 has a variable frequency drive, such that the speed of the motor may be regulated by the drive.
  • the pump portion 282 of the start pump 280 is driven by the motor-drive portion 284 coupled thereto.
  • the pump portion 282 has an inlet for receiving the working fluid from the low pressure side of the working fluid circuit 202, such as from the condenser 274 and/or the working fluid storage system 290.
  • the pump portion 282 has an outlet for releasing the working fluid into the high pressure side of the working fluid circuit 202.
  • Start pump inlet valve 283 and start pump outlet valve 285 may be utilized to control the flow of the working fluid passing through the start pump 280.
  • Start pump inlet valve 283 may be fluidly coupled to the low pressure side of the working fluid circuit 202 upstream of the pump portion 282 of the start pump 280 and may be utilized to control the flowrate of the working fluid entering the inlet of the pump portion 282.
  • Start pump outlet valve 285 may be fluidly coupled to the high pressure side of the working fluid circuit 202 downstream of the pump portion 282 of the start pump 280 and may be utilized to control the flowrate of the working fluid exiting the outlet of the pump portion 282.
  • the turbo pump 260 is generally a turbo-drive pump or a turbine-drive pump and utilized to pressurize and circulate the working fluid throughout the working fluid circuit 202.
  • the turbo pump 260 contains a pump portion 262 and a drive turbine 264 coupled together by a driveshaft 267 and an optional gearbox (not shown).
  • the drive turbine 264 is configured to rotate the pump portion 262 and the pump portion 262 is configured to circulate the working fluid within the working fluid circuit 202.
  • the driveshaft 267 may be a single piece or contain two or more pieces coupled together.
  • a first segment of the driveshaft 267 extends from the drive turbine 264 to the gearbox
  • a second segment of the driveshaft 230 extends from the gearbox to the pump portion 262
  • multiple gears are disposed between and coupled to the two segments of the driveshaft 267 within the gearbox.
  • the drive turbine 264 of the turbo pump 260 is driven by heated working fluid, such as the working fluid flowing from the heat exchanger 150.
  • the drive turbine 264 may be fluidly coupled to the high pressure side of the working fluid circuit 202 by an inlet configured to receive the working fluid from the high pressure side of the working fluid circuit 202, such as flowing from the heat exchanger 150.
  • the drive turbine 264 may be fluidly coupled to the low pressure side of the working fluid circuit 202 by an outlet configured to release the working fluid into the low pressure side of the working fluid circuit 202.
  • the pump portion 262 of the turbo pump 260 is driven by the driveshaft 267 coupled to the drive turbine 264.
  • the pump portion 262 of the turbo pump 260 may be fluidly coupled to the low pressure side of the working fluid circuit 202 by an inlet configured to receive the working fluid from the low pressure side of the working fluid circuit 202.
  • the inlet of the pump portion 262 is configured to receive the working fluid from the low pressure side of the working fluid circuit 202, such as from the condenser 274 and/or the working fluid storage system 290.
  • the pump portion 262 may be fluidly coupled to the high pressure side of the working fluid circuit 202 by an outlet configured to release the working fluid into the high pressure side of the working fluid circuit 202 and circulate the working fluid within the working fluid circuit 202.
  • the working fluid released from the outlet on the drive turbine 264 is returned into the working fluid circuit 202 downstream of the recuperator 216 and upstream of the recuperator 218.
  • the turbo pump 260 including piping and valves, is optionally disposed on a turbo pump skid 266, as depicted in Figure 2.
  • the turbo pump skid 266 may be disposed on or adjacent to the main process skid 212.
  • a drive turbine bypass valve 265 is generally coupled between and in fluid communication with a fluid line extending from the inlet on the drive turbine 264 with a fluid line extending from the outlet on the drive turbine 264.
  • the drive turbine bypass valve 265 is generally opened to bypass the turbo pump 260 while using the start pump 280 during the initial stages of generating electricity with the heat engine system 200. Once a predetermined pressure and temperature of the working fluid is obtained within the working fluid circuit 202, the drive turbine bypass valve 265 is closed and the heated working fluid is flowed through the drive turbine 264 to start the turbo pump 260.
  • a turbo pump throttle valve 263 may be coupled between and in fluid communication with a fluid line extending from the heat exchanger 150 to the inlet on the drive turbine 264 of the turbo pump 260.
  • the turbo pump throttle valve 263 is configured to modulate the flow of the heated working fluid into the drive turbine 264 which in turn - may be utilized to adjust the flow of the working fluid throughout the working fluid circuit 202.
  • valve 293 may be utilized to provide back pressure for the drive turbine 264 of the turbo pump 260.
  • a turbo pump attemperator valve 295 may be fluidly coupled to the working fluid circuit 202 via a bypass line 291 disposed between the outlet on the pump portion 262 of the turbo pump 260 and the inlet on the drive turbine 264 and/or disposed between the outlet on the pump portion 282 of the start pump 280 and the inlet on the drive turbine 264.
  • the bypass line 291 and the turbo pump attemperator valve 295 may be configured to flow the working fluid from the pump portion 262 or 282, around and avoid the recuperator 218 and the heat exchanger 150, and to the drive turbine 264, such as during a warm-up or cool-down step of the turbo pump 260.
  • the bypass line 291 and the turbo pump attemperator valve 295 may be utilized to warm the working fluid with the drive turbine 264 while avoiding the thermal heat from the heat source stream 1 10 via the heat exchangers, such as the heat exchanger 150.
  • a control valve 261 may be disposed downstream of the outlet of the pump portion 262 of the turbopump 260 and the control valve 281 may be disposed downstream of the outlet of the pump portion 282 of the start pump 280.
  • Control valves 261 and 281 are flow control safety valves and are generally utilized to regulate the directional flow or to prohibit backflow of the working fluid within the working fluid circuit 202.
  • Control valve 261 may be configured to prevent the working fluid from flowing upstream towards or into the outlet of the pump portion 262 of the turbopump 260.
  • control valve 281 may be configured to prevent the working fluid from flowing upstream towards or into the outlet of the pump portion 282 of the start pump 280.
  • the turbo pump throttle valve 263 may be fluidly coupled to the working fluid circuit 202 upstream of the inlet of the drive turbine 264 of the turbo pump 260 and configured to control a flow of the working fluid flowing into the drive turbine 264.
  • the power turbine bypass valve 219 may be fluidly coupled to the power turbine bypass line 208 and configured to modulate, adjust, or otherwise control the working fluid flowing through the power turbine bypass line 208 for controlling the flowrate of the working fluid entering the power turbine 228.
  • the power turbine bypass line 208 may be fluidly coupled to the working fluid circuit 202 at a point upstream of an inlet of the power turbine 228 and at a point downstream of an outlet of the power turbine 228.
  • the power turbine bypass line 208 is configured to flow the working fluid around and avoid the power turbine 228 when the power turbine bypass valve 219 is in an opened position.
  • the flowrate and the pressure of the working fluid flowing into the power turbine 228 may be reduced or stopped by adjusting the power turbine bypass valve 219 to the opened position.
  • the flowrate and the pressure of the working fluid flowing into the power turbine 228 may be increased or started by adjusting the power turbine bypass valve 219 to the closed position due to the backpressure formed through the power turbine bypass line 208.
  • the power turbine bypass valve 219 and the turbo pump throttle valve 263 may be independently controlled by the process control system 204 that is communicably connected, wired and/or wirelessly, with the power turbine bypass valve 219, the turbo pump throttle valve 263, and other parts of the heat engine system 200.
  • the process control system 204 is operatively connected to the working fluid circuit 202 and a mass management system 270 and is enabled to monitor and control multiple process operation parameters of the heat engine system 200.
  • the working fluid circuit 202 provides a bypass flowpath for the start pump 280 via the start pump bypass line 224 and a start pump bypass valve 254, as well as a bypass flowpath for the turbo pump 260 via the turbo pump bypass line 226 and a turbo pump bypass valve 256.
  • One end of the start pump bypass line 224 may be fluidly coupled to an outlet of the pump portion 282 of the start pump 280 and the other end of the start pump bypass line 224 may be fluidly coupled to a fluid line 229.
  • one end of a turbo pump bypass line 226 may be fluidly coupled to an outlet of the pump portion 262 of the turbo pump 260 and the other end of the turbo pump bypass line 226 is coupled to the start pump bypass line 224.
  • the start pump bypass line 224 and the turbo pump bypass line 226 merge together as a single line upstream of coupling to a fluid line 229.
  • the fluid line 229 extends between and may be fluidly coupled to the recuperator 218 and the condenser 274.
  • the start pump bypass valve 254 is disposed along the start pump bypass line 224 and fluidly coupled between the low pressure side and the high pressure side of the working fluid circuit 202 when in a closed position.
  • the turbo pump bypass valve 256 is disposed along the turbo pump bypass line 226 and fluidly coupled between the low pressure side and the high pressure side of the working fluid circuit 202 when in a closed position.
  • Figure 2 further depicts a power turbine throttle valve 250 fluidly coupled to a bypass line 246 on the high pressure side of the working fluid circuit 202 and upstream of the heat exchanger 120, as disclosed by at least one embodiment described herein.
  • the power turbine throttle valve 250 may be fluidly coupled to the bypass line 246 and configured to modulate, adjust, or otherwise control the working fluid flowing through the bypass line 246 for controlling a general coarse flowrate of the working fluid within the working fluid circuit 202.
  • the bypass line 246 may be fluidly coupled to the working fluid circuit 202 at a point upstream of the valve 293 and at a point downstream of the pump portion 282 of the start pump 280 and/or the pump portion 262 of the turbo pump 260.
  • a power turbine trim valve 252 may be fluidly coupled to a bypass line 248 on the high pressure side of the working fluid circuit 202 and upstream of the heat exchanger 150, as disclosed by another embodiment described herein.
  • the power turbine trim valve 252 may be fluidly coupled to the bypass line 248 and configured to modulate, adjust, or otherwise control the working fluid flowing through the bypass line 248 for controlling a fine flowrate of the working fluid within the working fluid circuit 202.
  • the bypass line 248 may be fluidly coupled to the bypass line 246 at a point upstream of the power turbine throttle valve 250 and at a point downstream of the power turbine throttle valve 250.
  • the heat engine system 200 further contains a turbo pump throttle valve 263 fluidly coupled to the working fluid circuit 202 upstream of the inlet of the drive turbine 264 of the turbo pump 260 and configured to modulate a flow of the working fluid flowing into the drive turbine 264, a power turbine bypass line 208 fluidly coupled to the working fluid circuit 202 upstream of an inlet of the power turbine 228, fluidly coupled to the working fluid circuit 202 downstream of an outlet of the power turbine 228, and configured to flow the working fluid around and avoid the power turbine 228, a power turbine bypass valve 219 fluidly coupled to the power turbine bypass line 208 and configured to modulate a flow of the working fluid flowing through the power turbine bypass line 208 for controlling the flowrate of the working fluid entering the power turbine 228, and a process control system 204 operatively connected to the heat engine system 90 or 200, wherein the process control system 204 is configured to adjust the turbo pump throttle valve 263 and the power turbine bypass valve 219.
  • a bypass line 160 may be fluidly coupled to a fluid line 131 of the working fluid circuit 202 upstream of the heat exchangers 120, 130, and/or 150 by a bypass valve 162, as illustrated in Figure 2.
  • the bypass valve 162 may be a solenoid valve, a hydraulic valve, an electric valve, a manual valve, or derivatives thereof.
  • the bypass valve 162 is a solenoid valve and configured to be controlled by the process control system 204.
  • the working fluid circuit 202 provides release valves 213a, 213b, 213c, and 213d, as well as release outlets 214a, 214b, 214c, and 214d, respectively in fluid communication with each other.
  • the release valves 213a, 213b, 213c, and 213d remain closed during the electricity generation process, but may be configured to automatically open to release an over-pressure at a predetermined value within the working fluid. Once the working fluid flows through the valve 213a, 213b, 213c, or 213d, the working fluid is vented through the respective release outlet 214a, 214b, 214c, or 214d.
  • the release outlets 214a, 214b, 214c, and 214d may provide passage of the working fluid into the ambient surrounding atmosphere.
  • the release outlets 214a, 214b, 214c, and 214d may provide passage of the working fluid into a recycling or reclamation step that generally includes capturing, condensing, and storing the working fluid.
  • the release valve 213a and the release outlet 214a may be fluidly coupled to the working fluid circuit 202 at a point disposed between the heat exchanger 120 and the power turbine 228.
  • the release valve 213b and the release outlet 214b may be fluidly coupled to the working fluid circuit 202 at a point disposed between the heat exchanger 150 and the drive turbine 264 of the turbo pump 260.
  • the release valve 213c and the release outlet 214c may be fluidly coupled to the working fluid circuit 202 via a bypass line that extends from a point between the valve 293 and the pump portion 262 of the turbo pump 260 to a point on the turbo pump bypass line 226 between the turbo pump bypass valve 256 and the fluid line 229.
  • the release valve 213d and the release outlet 214d may be fluidly coupled to the working fluid circuit 202 at a point disposed between the recuperator 218 and the condenser 274.
  • a computer system 206 contains a multi- controller algorithm utilized to control the turbo pump throttle valve 263, the power turbine bypass valve 219, the bypass valve 162, the power turbine throttle valve 250, the power turbine trim valve 252, as well as other valves, pumps, and sensors within the heat engine system 200.
  • the process control system 204 is enabled to move, adjust, manipulate, or otherwise control the bypass valve 162, the power turbine throttle valve 250, and/or the power turbine trim valve 252 for adjusting or controlling the flow of the working fluid throughout the working fluid circuit 202.
  • the process control system 204 is also operable to regulate the temperatures and pressures throughout the working fluid circuit 202.
  • the overall efficiency of the heat engine system 200 and the amount of power ultimately generated can be influenced by the inlet or suction pressure at the pump when the working fluid contains supercritical carbon dioxide.
  • the heat engine system 200 may incorporate the use of a mass management system ("MMS") 270.
  • MMS mass management system
  • the mass management system 270 controls the inlet pressure of the start pump 280 by regulating the amount of working fluid entering and/or exiting the heat engine system 200 at strategic locations in the working fluid circuit 202, such as at tie-in points, inlets/outlets, valves, or conduits throughout the heat engine system 200. Consequently, the heat engine system 200 becomes more efficient by increasing the pressure ratio for the start pump 280 to a maximum possible extent.
  • the mass management system 270 contains at least one vessel or tank, such as a storage vessel (e.g. , working fluid storage vessel 292), a fill vessel, and/or a mass control tank (e.g., mass control tank 286), fluidly coupled to the low pressure side of the working fluid circuit 202 via one or more valves, such as the valve 287.
  • the valve 287 is a fluid (e.g., C0 2 ) transfer pump inlet valve.
  • the valves are moveable - as being partially opened, fully opened, and/or closed - to either remove working fluid from the working fluid circuit 202 or add working fluid to the working fluid circuit 202.
  • the mass management system 270 may include a plurality of valves and/or connection points, each in fluid communication with the mass control tank 286.
  • the valves may be characterized as termination points where the mass management system 270 is operatively connected to the heat engine system 200.
  • the connection points and valves may be configured to provide the mass management system 270 with an outlet for flaring excess working fluid or pressure, or to provide the mass management system 270 with additional/supplemental working fluid from an external source, such as a fluid fill system.
  • the mass control tank 286 may be configured as a localized storage tank for additional/supplemental working fluid that may be added to the heat engine system 200 when needed in order to regulate the pressure or temperature of the working fluid within the working fluid circuit 202 or otherwise supplement escaped working fluid.
  • the mass management system 270 adds and/or removes working fluid mass to/from the heat engine system 200 with or without the need of a pump, thereby reducing system cost, complexity, and maintenance.
  • a working fluid storage vessel 292 is part of a working fluid storage system 290 and may be fluidly coupled to the working fluid circuit 202. At least one connection point, such as a working fluid feed 288, may be a fluid fill port for the working fluid storage vessel 292 of the working fluid storage system 290 and/or the mass management system 270. Additional or supplemental working fluid may be added to the mass management system 270 from an external source, such as a fluid fill system via the working fluid feed 288. Exemplary fluid fill systems are described and illustrated in U.S. Pat. No. 8,281 ,593, the contents of which are incorporated herein by reference to the extent consistent with the present disclosure.
  • bearing gas and seal gas may be supplied to the turbo pump 260 or other devices contained within and/or utilized along with the heat engine system 200.
  • One or multiple streams of bearing gas and/or seal gas may be derived from the working fluid within the working fluid circuit 202 and contain carbon dioxide in a gaseous, subcritical, or supercritical state.
  • the bearing gas or fluid is flowed by the start pump 280, from a bearing gas supply 296a and/or a bearing gas supply 296b, into the working fluid circuit 202, through a bearing gas supply line (not shown), and to the bearings within the power generation system 220.
  • the bearing gas or fluid is flowed by the start pump 280, from the working fluid circuit 202, through a bearing gas supply line (not shown), and to the bearings within the turbo pump 260.
  • the seal gas supply 298 is a connection point or valve that feeds into a seal gas system.
  • a gas return 294 is generally coupled to a discharge, recapture, or return of bearing gas, seal gas, and other gases. The gas return 294 provides a feed stream into the working fluid circuit 202 of recycled, recaptured, or otherwise returned gases - generally derived from the working fluid.
  • the gas return is generally fluidly coupled to the working fluid circuit 202 upstream of the condenser 274 and downstream of the recuperator 218.
  • the heat engine system 200 contains a process control system 204 communicably connected, wired and/or wirelessly, with numerous sets of sensors, valves, and pumps, in order to process the measured and reported temperatures, pressures, and mass flowrates of the working fluid at the designated points within the working fluid circuit 202.
  • the process control system 204 may be operable to selectively adjust the valves in accordance with a control program or algorithm, thereby maximizing operation of the heat engine system 200.
  • the process control system 204 may operate with the heat engine system 200 semi- passively with the aid of several sets of sensors.
  • the first set of sensors is arranged at or adjacent the suction inlet of the turbo pump 260 and the start pump 280 and the second set of sensors is arranged at or adjacent the outlet of the turbo pump 260 and the start pump 280.
  • the first and second sets of sensors monitor and report the pressure, temperature, mass flowrate, or other properties of the working fluid within the low and high pressure sides of the working fluid circuit 202 adjacent the turbo pump 260 and the start pump 280.
  • the third set of sensors is arranged either inside or adjacent the working fluid storage vessel 292 of the working fluid storage system 290 to measure and report the pressure, temperature, mass flowrate, or other properties of the working fluid within the working fluid storage vessel 292.
  • an instrument air supply (not shown) may be coupled to sensors, devices, or other instruments within the heat engine system 200 including the mass management system 270 and/or other system components that may utilize a gaseous supply, such as nitrogen or air.
  • the waste heat system 100 is disposed on or in a waste heat skid 102 fluidly coupled to the working fluid circuit 202, as well as other portions, sub-systems, or devices of the heat engine system 200.
  • the waste heat skid 102 may be fluidly coupled to a source of and an exhaust for the heat source stream 1 10, a main process skid 212, a power generation skid 222, and/or other portions, sub-systems, or devices of the heat engine system 200.
  • the waste heat system 100 disposed on or in the waste heat skid 102 generally contains inlets 122, 132, and 152 and outlets 124, 134, and 154 fluidly coupled to and in thermal communication with the working fluid within the working fluid circuit 202.
  • the inlet 122 is disposed upstream of the heat exchanger 120 and the outlet 124 is disposed downstream of the heat exchanger 120.
  • the working fluid circuit 202 is configured to flow the working fluid from the inlet 122, through the heat exchanger 120, and to the outlet 124 while transferring thermal energy from the heat source stream 1 10 to the working fluid by the heat exchanger 120.
  • the inlet 152 is disposed upstream of the heat exchanger 150 and the outlet 154 is disposed downstream of the heat exchanger 150.
  • the working fluid circuit 202 is configured to flow the working fluid from the inlet 152, through the heat exchanger 150, and to the outlet 154 while transferring thermal energy from the heat source stream 1 10 to the working fluid by the heat exchanger 150.
  • the inlet 132 is disposed upstream of the heat exchanger 130 and the outlet 134 is disposed downstream of the heat exchanger 130.
  • the working fluid circuit 202 is configured to flow the working fluid from the inlet 132, through the heat exchanger 130, and to the outlet 134 while transferring thermal energy from the heat source stream 1 10 to the working fluid by the heat exchanger 130.
  • the power generation system 220 is disposed on or in the power generation skid 222 generally contains inlets 225a, 225b and an outlet 227 fluidly coupled to and in thermal communication with the working fluid within the working fluid circuit 202.
  • the inlets 225a, 225b are upstream of the power turbine 228 within the high pressure side of the working fluid circuit 202 and are configured to receive the heated and high pressure working fluid.
  • the inlet 225a may be fluidly coupled to the outlet 124 of the waste heat system 100 and configured to receive the working fluid flowing from the heat exchanger 120 and the inlet 225b may be fluidly coupled to the outlet 241 of the process system
  • the outlet 227 is disposed downstream of the power turbine 228 within the low pressure side of the working fluid circuit 202 and is configured to provide the low pressure working fluid.
  • the outlet 227 may be fluidly coupled to the inlet 239 of the process system 210 and configured to flow the working fluid to the recuperator 216.
  • a filter 215a may be disposed along and in fluid communication with the fluid line at a point downstream of the heat exchanger 120 and upstream of the power turbine 228. In some examples, the filter 215a may be fluidly coupled to the working fluid circuit 202 between the outlet 124 of the waste heat system 100 and the inlet 225a of the process system 210.
  • a power turbine stop valve 217 may be fluidly coupled to the working fluid circuit 202 between the inlet 225a and the power turbine 228.
  • the power turbine stop valve 217 is configured to control the working fluid flowing from the heat exchanger 120, through the inlet 225a, and into the power turbine 228 while in an opened position.
  • the power turbine stop valve 217 may be configured to cease the flow of working fluid from entering into the power turbine 228 while in a closed position.
  • a power turbine attemperator valve 223 may be fluidly coupled to the working fluid circuit 202 via a bypass line 21 1 disposed between the outlet on the pump portion 262 of the turbo pump 260 and the inlet on the power turbine 228 and/or disposed between the outlet on the pump portion 282 of the start pump 280 and the inlet on the power turbine 228.
  • the bypass line 21 1 disposed between the outlet on the pump portion 262 of the turbo pump 260 and the inlet on the power turbine 228 and/or disposed between the outlet on the pump portion 282 of the start pump 280 and the inlet on the power turbine 228.
  • the bypass line 21 1 and the power turbine attemperator valve 223 may be utilized to warm the working fluid with heat coming from the power turbine 228 while avoiding the thermal heat from the heat source stream 1 10 flowing through the heat exchangers, such as the heat exchangers 120 and 130.
  • the power turbine attemperator valve 223 may be fluidly coupled to the working fluid circuit 202 between the inlet 225b and the power turbine stop valve 217 upstream of a point on the fluid line that intersects the incoming stream from the inlet 225a.
  • the power turbine attemperator valve 223 may be configured to control the working fluid flowing from the start pump 280 and/or the turbo pump 260, through the inlet 225b, and to a power turbine stop valve 217, the power turbine bypass valve 219, and/or the power turbine 228.
  • the power turbine bypass valve 219 may be fluidly coupled to a turbine bypass line that extends from a point of the working fluid circuit 202 upstream of the power turbine stop valve 217 and downstream of the power turbine 228. Therefore, the bypass line and the power turbine bypass valve 219 are configured to direct the working fluid around and avoid the power turbine 228. If the power turbine stop valve 217 is in a closed position, the power turbine bypass valve 219 may be configured to flow the working fluid around and avoid the power turbine 228 while in an opened position. In one embodiment, the power turbine bypass valve 219 may be utilized while warming up the working fluid during a start-up operation of the electricity generating process.
  • An outlet valve 221 may be fluidly coupled to the working fluid circuit 202 between the outlet on the power turbine 228 and the outlet 227 of the power generation system 220.
  • the process system 210 is disposed on or in the main process skid 212 generally contains inlets 235, 239, and 255 and outlets 231 , 237, 241 , 251 , and 253 fluidly coupled to and in thermal communication with the working fluid within the working fluid circuit 202.
  • the inlet 235 is upstream of the recuperator 216 and the outlet 154 is downstream of the recuperator 216.
  • the working fluid circuit 202 is configured to flow the working fluid from the inlet 235, through the recuperator 216, and to the outlet 237 while transferring thermal energy from the working fluid in the low pressure side of the working fluid circuit 202 to the working fluid in the high pressure side of the working fluid circuit 202 by the recuperator 216.
  • the outlet 241 of the process system 210 is downstream of the turbo pump 260 and/or the start pump 280, upstream of the power turbine 228, and configured to provide a flow of the high pressure working fluid to the power generation system 220, such as to the power turbine 228.
  • the inlet 239 is upstream of the recuperator 216, downstream of the power turbine 228, and configured to receive the low pressure working fluid flowing from the power generation system 220, such as to the power turbine 228.
  • the outlet 251 of the process system 210 is downstream of the recuperator 218, upstream of the heat exchanger 150, and configured to provide a flow of working fluid to the heat exchanger 150.
  • the inlet 255 is downstream of the heat exchanger 150, upstream of the drive turbine 264 of the turbo pump 260, and configured to provide the heated high pressure working fluid flowing from the heat exchanger 150 to the drive turbine 264 of the turbo pump 260.
  • the outlet 253 of the process system 210 is downstream of the pump portion 262 of the turbo pump 260 and/or the pump portion 282 of the start pump 280, couples a bypass line disposed downstream of the heat exchanger 150 and upstream of the drive turbine 264 of the turbo pump 260, and configured to provide a flow of working fluid to the drive turbine 264 of the turbo pump 260.
  • a filter 215c may be disposed along and in fluid communication with the fluid line at a point downstream of the heat exchanger 150 and upstream of the drive turbine 264 of the turbo pump 260.
  • the filter 215c may be fluidly coupled to the working fluid circuit 202 between the outlet 154 of the waste heat system 100 and the inlet 255 of the process system 210.
  • the heat engine system 200 contains the process system 210 disposed on or in a main process skid 212, the power generation system 220 disposed on or in a power generation skid 222, the waste heat system 100 disposed on or in a waste heat skid 102.
  • the working fluid circuit 202 extends throughout the inside, the outside, and between the main process skid 212, the power generation skid 222, the waste heat skid 102, as well as other systems and portions of the heat engine system 200.
  • the heat engine system 200 contains the bypass line 160 and the bypass valve 162 disposed between the waste heat skid 102 and the main process skid 212.
  • a filter 215b may be disposed along and in fluid communication with the fluid line 135 at a point downstream of the heat exchanger 130 and upstream of the recuperator 216. In some examples, the filter 215b may be fluidly coupled to the working fluid circuit 202 between the outlet 134 of the waste heat system 100 and the inlet 235 of the process system 210.
  • the control strategy utilizes sliding mode control to "balance" the competing effects of the increasing outlet pressure (P 0 ) of the turbo pump 260 and decreasing inlet pressure (P,) of the turbo pump 260.
  • the inlet pressure (Pi) is within the low pressure side of the working fluid circuit 202 and the outlet pressure (P 0 ) is within the high pressure side of the working fluid circuit 202.
  • the outlet pressure (P 0 ) of the turbo pump 260 may increase and adversely affects the inlet pressure (R) which could potentially damage the turbo pump 260.
  • a second "governing loop” may continually operate “in the background” while implementing an advanced control theory technique of "sliding mode” control, such that the turbo pump throttle valve 263 may be configured to control the speed of the turbo pump 260 to operate within an "envelope" of a control range that may change dynamically as the entire system increases in power or pressure within the working fluid circuit 202.
  • the second governing loop In the event that the inlet pressure (R) to the turbo pump 260 approaches a defined setpoint that is determined to be “detrimental” to the turbo pump 260, the second governing loop "takes control” or overrides of the turbo pump throttle valve 263 and “forces” the turbo pump 260 back into “safe operating conditions”. Once the inlet pressure (R) conditions of the turbo pump 260 are achieved, the valve goes back to the primary governing loop which controls the turbo pump throttle valve 263 based on a speed ramp setpoint.
  • a "sliding mode" may be utilized for controlling the process pressures to move between mutually conflicting process variables (outlet pressure (P 0 ) and inlet pressure (R)) to achieve optimal performance of the turbo pump 260.
  • the control of the start pump bypass valve 254 utilizes a sliding mode control technique used to ensure the inlet pressure (R) does not fall into an unacceptable pressure range while the outlet pressure (P.) is increased or maximized.
  • a secondary controller monitors system inlet pressure and may constantly be "running in the background" - upon detection in a decrease or loss of the inlet pressure (P,), the secondary controller overrides the primary controller which is controlling values for the outlet pressure (P 0 ) and reduces the output to the start pump bypass valve 254 to regain system inlet pressure (R). Upon achieving an acceptable margin or desirable value of the inlet pressure (P,), the primary controller regains control and starts to increase the outlet pressure (P 0 ).
  • sliding mode control techniques are used to maximize the outlet pressure (P 0 ) and maintain an acceptable or desirable value of the inlet pressure (P,).
  • the control of a start pump bypass valve 254 balances these conflicting variables and maximizes the outlet pressure (P 0 ) while maintaining an acceptable value of the inlet pressure (P,) within margin so as not to be detrimental to the process or equipment.
  • control of a turbo pump bypass valve 256 utilizes advanced control concepts of "feed forward" and sliding mode control to anticipate the effects of other valves on the outlet pressure (P 0 ) and maintaining the inlet pressure (P,) within an acceptable range.
  • Other process valves including the power turbine throttle valve 250, the power turbine trim valve 252, and the turbo pump throttle valve 263, may be configured to affect the outlet pressure (P 0 ) as they independently control respective "process variables”.
  • the control of a turbo pump bypass valve 256 balances the effects of other valves (e.g.
  • the power turbine throttle valve 250, the power turbine trim valve 252 , and the turbo pump throttle valve 263) maximizing the outlet pressure (P 0 ) and maintaining the inlet pressure (P,) within acceptable limits as to maintain the SC-CO2 cycle and not cavitate the turbo pump 260, such as the pump portion 262.
  • valves including the power turbine throttle valve 250, the power turbine trim valve 252, the turbo pump throttle valve 263, and the turbo pump bypass valve 256 affect the inlet pressure (P,). If the inlet pressure (P,) falls below a certain limit, either the entire process (e.g. , sc-C0 2 loop) loses energy and come to a halt or potential damage to the critical pumps (e.g., start pump 280 or turbo pump 260) could result. Therefore, a sliding mode control strategy may be implemented using a secondary controller running "in the background" that overrides the primary feed forward controller in the event that the inlet pressure (P,) starts to "fall off” and approach an unacceptable pressure level. Advanced control techniques of feed forward to anticipate the effects of conflicting control valves in addition to sliding mode control to maintain an acceptable system inlet pressure.
  • first and second features are formed in direct contact
  • additional features may be formed interposing the first and second features, such that the first and second features may not be in direct contact.
  • exemplary embodiments described herein may be combined in any combination of ways, i.e., any element from one exemplary embodiment may be used in any other exemplary embodiment without departing from the scope of the disclosure.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)

Abstract

L'invention concerne un système de moteur thermique et un procédé de génération d'électricité. Le système de moteur thermique comporte une soupape d'étranglement de pompe turbo accouplée de manière fluidique à un circuit de fluide de travail et placée en amont d'un orifice d'admission de turbine sur une turbine d'entraînement d'une pompe turbo, un contrôleur de boucle de régulation primaire conçu pour maintenir une valeur désirable de la pression d'admission par modulation de la soupape d'étranglement de la pompe turbo, et un contrôleur de boucle de régulation secondaire conçu pour détecter une valeur indésirable de la pression d'admission et pour augmenter la pression d'admission par modulation de la soupape d'étranglement de la pompe turbo. Une soupape de dérivation de pompe de démarrage peut être accouplée de manière fluidique à une conduite de dérivation et placée en aval d'un orifice d'évacuation de pompe sur une pompe de démarrage et/ou une soupape de dérivation de pompe turbo peut être accouplée de manière fluidique à la conduite de dérivation et placée en aval de la pompe turbo.
PCT/US2014/023026 2013-03-11 2014-03-11 Système de pompe et de soupape pour commander un circuit de fluide de travail supercritique dans un système de moteur thermique WO2014164620A1 (fr)

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US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
WO2018217969A1 (fr) * 2017-05-26 2018-11-29 Echogen Power Systems Llc Systèmes et procédés de commande de la pression d'un fluide de travail au niveau d'une entrée d'un dispositif de pressurisation d'un système de moteur thermique
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EP3734027A1 (fr) * 2019-05-02 2020-11-04 Siemens Aktiengesellschaft Regazéification de gaz naturel liquéfié
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