WO2015034988A1 - Procédés de commande pour systèmes de moteur thermique possédant un circuit de fluide de travail configurable de façon sélective - Google Patents

Procédés de commande pour systèmes de moteur thermique possédant un circuit de fluide de travail configurable de façon sélective Download PDF

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Publication number
WO2015034988A1
WO2015034988A1 PCT/US2014/053995 US2014053995W WO2015034988A1 WO 2015034988 A1 WO2015034988 A1 WO 2015034988A1 US 2014053995 W US2014053995 W US 2014053995W WO 2015034988 A1 WO2015034988 A1 WO 2015034988A1
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WO
WIPO (PCT)
Prior art keywords
working fluid
pressure side
fluid circuit
engine system
heat engine
Prior art date
Application number
PCT/US2014/053995
Other languages
English (en)
Inventor
Joshua GIEGEL
Timothy Held
Brett A. BOWAN
Cameron CLOSE
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
Priority claimed from US14/475,640 external-priority patent/US9874112B2/en
Application filed by Echogen Power Systems, L.L.C. filed Critical Echogen Power Systems, L.L.C.
Priority to EP14841902.1A priority Critical patent/EP3042049B1/fr
Priority to KR1020167008673A priority patent/KR102281175B1/ko
Priority to EP16199227.6A priority patent/EP3163029B1/fr
Publication of WO2015034988A1 publication Critical patent/WO2015034988A1/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
    • F01K23/10—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

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 may be converted into useful energy by a variety of turbine generator or heat engine systems that employ thermodynamic methods, such as Rankine cycles or other power cycles.
  • thermodynamic methods such as Rankine cycles or other power cycles.
  • Rankine and similar thermodynamic cycles 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, a pump, or other device.
  • a heat engine system includes a pump configured to pressurize and circulate a working fluid through a working fluid circuit having a high pressure side and a low pressure side.
  • a first expander is configured to receive the working fluid from the high pressure side and to convert a pressure drop in the working fluid to mechanical energy.
  • a plurality of waste heat exchangers are disposed in series along a flow path of a heat source stream and each is configured to transfer thermal energy from the heat source stream to the working fluid.
  • a method for controlling a heat engine system includes initiating flow of a working fluid through a working fluid circuit having a high pressure side and a low pressure side by controlling a pump to pressurize and circulate the working fluid through the working fluid circuit, determining a configuration of the working fluid circuit by determining which of a plurality of waste heat exchangers and which of a plurality of recuperators to position in the high pressure side of the working fluid circuit, and determining, based on the determined configuration of the working fluid circuit, which of a plurality of valves to position in a closed position to isolate a portion of the working fluid from the working fluid flowing through the working fluid circuit.
  • a method for controlling a heat engine system includes initiating flow of a working fluid through a working fluid circuit having a high pressure side and a low pressure side by controlling a pump to pressurize and circulate the working fluid through the working fluid circuit, determining a configuration of the working fluid circuit by determining which of a plurality of waste heat exchangers and which of a plurality of recuperators to position in the high pressure side of the working fluid circuit, determining, based on the determined configuration of the working fluid circuit, for each of a plurality of valves, whether to position each respective valve in an opened position, a closed position, or a partially opened position, and actuating each of the plurality of valves to the determined opened position, closed position, or partially opened position.
  • Figure 2 illustrates a heat engine system having a selectively configurable working fluid circuit, according to one or more embodiments disclosed herein.
  • Figure 6 is a flow chart illustrating a method for controlling the heat engine system illustrated in Figure 2 to optimize the power output, according to one or more embodiments disclosed herein.
  • Figure 1 is a block diagram of exemplary components of one embodiment of an electronic control system 80 that may control the operation of a heat engine system 100 depicted in Figure 2.
  • the electronic control system 80 includes a valve system 82 that may be used to selectively configure a working fluid circuit such that a working fluid may be routed through a selected quantity and type of fluid handling or processing components, which may depend on the given application.
  • valve system 82 may be used to selectively configure the working fluid circuit 102 shown in Figure 2 such that a flow path of a working fluid may be established through any desired combination of one or more waste heat exchangers 120a, 120b, 1 20c, and 120d, and one or more recuperators 1 30a, 130b, and 1 30c, turbines or expanders 1 60a and 160b, one or more pumps 150a, 150b, and 150c, one or more condensers 1 40a, 140b, and 1 40c.
  • valve system 82 may include bypass valves 1 16a, 1 16b, 1 1 6c, and 1 1 6d, stop or control valves 1 1 8a, 1 18b, 1 18c, and 1 18d, stop or control valves 1 28a, 128b, and 1 28c, and stop or throttle valves 1 58a and 1 58b, each of which may be utilized in opened positions, closed positions, and partially opened or closed positions to selectively allow the working fluid to flow through the circuit 1 02.
  • a valve controller 84 may provide the infrastructure for receiving data from a processor 86 to selectively control the position of each of the valves in the valve system 82.
  • the valve controller 84 may include control logic for processing control commands from the processor 86 to produce one or more changes in the positions of each of the valves in the valve system 82. Once the control logic is processed, the valve controller 84 may selectively actuate each of the valves in the valve system 82 to position each of the valves in an opened position, a closed position, or a partially opened or closed position.
  • the valve controller 84 may also include one or more integrated circuits and associated components, such as resistors, potentiometers, voltage regulators, drivers, and so forth. However, in other embodiments, the valve controller 84 may be integrated with the processor 86.
  • the valve controller 84 may also be responsive to data received from one or more process condition sensors 88.
  • the process condition sensors 88 may include temperature sensors, pressure sensors, flow rate sensors, or any other sensors configured to measure a parameter of the working fluid circuit 102, the working fluid flowing therethrough, or parameters from other components in the system 1 00, such as temperatures, pressures, rotation speed, frequency, voltage, etc.
  • the valve controller 84 may continually respond to the process conditions measured by the process condition sensors 88 throughout operation to maximize the power output of the heat engine system 1 00.
  • valve controller 84 may repeatedly adjust the position of each of the valves of the valve system 82 in response to the data from the process condition sensors 88 and/or data from the processor 86 to obtain the maximum possible power output of the heat engine system 1 00 given the current process conditions.
  • the valve controller 84 may be configured to periodically adjust the position of valve system 82 to maximize working fluid flow and heat transfer in the heat exchangers and recuperators of system 1 00 under varying process conditions.
  • the electronic control system 80 may also include one or more input/output (I/O) ports 90 that enable the electronic control system 80 to couple to one or more external devices (e.g., external data sources).
  • I/O controller 92 may provide the infrastructure for exchanging data between the processor 86 and I/O devices connected through the I/O ports 90 and/or for receiving user input through one or more input devices 94.
  • a storage device 96 may store information, such as one or more programs and/or instructions, used by the processor 86, the valve controller 84, the I/O controller 92, or a combination thereof.
  • the storage device 96 may store firmware for the electronic control system 80, programs, applications, or routines executed by the electronic control system 80, processor functions, etc.
  • the storage device 96 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), 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 processer 86 to operate the logic or portions of the logic presented in the methods disclosed herein.
  • FIG. 2 illustrates an embodiment of the heat engine system 100 having the working fluid circuit 1 02 that may be selectively configured by the electronic control system 80 such that a flow path of a working fluid is directed through any desired combination of the plurality of waste heat exchangers 120a, 1 20b, 120c, and 1 20d, the plurality of recuperators 130a, 1 30b, and 1 30c, the turbines or expanders 160a and 160b, the pumps 1 50a, 1 50b, and 150c, and the condensers 1 40a, 1 40b, and 1 40c.
  • bypass valves 1 16a, 1 1 6b, 1 1 6c, and 1 16d, the stop or control valves 1 1 8a, 1 18b, 1 1 8c, and 1 18d, the stop or control valves 1 28a, 128b, and 128c, and the stop or throttle valves 158a and 158b may also each be selectively positioned in an opened position, a closed position, or a partially opened or closed position to enable the routing of the working fluid through the desired components.
  • the working fluid circuit 102 generally has a high pressure side and a low pressure side and is configured to flow the working fluid through the high pressure side and the low pressure side.
  • the high pressure side may extend along the flow path of the working fluid from the pump 1 50c to the expander 160a and/or the expander 1 60b, depending on which of the expanders 160a and 160b are included in the working fluid circuit 1 02
  • the low pressure side may extend along the flow path of the working fluid from the expander 160a and/or the expander 160b to the pump 1 50a.
  • working fluid may be transferred from the low pressure side to the high pressure side via a pump bypass valve 1 41 .
  • the working fluid circuit 1 02 may be configured such that the available components (e.g., the waste heat exchangers 120a, 1 20b, 120c, and 1 20d and the recuperators 1 30a, 1 30b, and 1 30c) are each selectively positioned in (e.g., fluidly coupled to) or isolated from (e.g., not fluidly coupled to) the high pressure side and the low pressure side of the working fluid circuit.
  • the electronic control system 80 may utilize the processor 86 to implement the control logic shown in a method 250 illustrated in Figure 3.
  • the processor 86 may receive data corresponding to one or more implementation-specific optimization parameters (block 252).
  • the processor 86 may further determine which of the waste heat exchangers 1 20a, 1 20b, 1 20c, and 1 20d to position in the high pressure side (block 254), which of the recuperators 1 30a, 1 30b, and 1 30c to position in the high pressure side (block 256), and which of the recuperators 1 30a, 1 30b, and 130c to position in the low pressure side (block 258).
  • the processor 86 may make such determinations, for example, by referencing programs, lookup tables, references, sensor inputs, information stored on the storage device 96, or any combination of the above .
  • the processor 86 may determine whether the valve should be placed in an opened position, a closed position, or a partially opened or closed position (block 260). The processor 86 may further selectively open or close each of the valves in the valve system 82 to achieve the desired working fluid circuit configuration for the given implementation (block 262). In addition to the valve system 82 selecting the fluid circuit configuration, the valve system may also select the volume of fluid or flow rate through each leg or branch of the selected configuration, e.g. , the valve system 82 may regulate the working fluid flow through selected elements of the selected configuration.
  • a turbopump may be formed by a shaft 1 62 coupling the second expander 160b and the pump 1 50c, such that the second expander 160b may drive the pump 1 50c with the mechanical energy generated by the second expander 1 60b.
  • the working fluid flow path from the pump 1 50c to the second expander 160b may be established by selectively fluidly coupling the recuperators 1 30c and 1 30b and the waste heat exchanger 1 20b to the high pressure side by positioning valves 1 16d, 1 28c, 128b, 1 16b, 1 18b, 1 1 6a, and 1 58b in an opened position.
  • the working fluid flow path may be established from the pump 150c to the first expander 1 60a by fluidly coupling the recuperator 130c, the waste heat exchanger 120c, the recuperator 1 30a, and the waste heat exchanger 120a to the high pressure side.
  • the working fluid flow path through the high pressure side extends from the pump 150c, through the valve 1 16d, through the valve 128c, through the recuperator 1 30c, through the valve bypass 1 16c, through the stop or control valve 1 1 8c, through the waste heat exchanger 1 20c, through the bypass valve 1 16b, through the valve 1 28a, through the recuperator 130a, through the bypass valve 1 1 6a, through the stop or control valve 1 1 8a, through the waste heat exchanger 1 20a, through the stop or throttle valve 1 58a, and to the first expander 1 60a.
  • the working fluid flow path through the low pressure side in this embodiment may extend from the first expander 160a, through the turbine discharge line 1 70a, through the recuperators 130a, 130b, and 130c and to the condensers 140a, 1 40b, and 140c and the pumps 150a, 1 50b, and 150c.
  • presently contemplated embodiments may include any number of waste heat exchangers, any number of recuperators, any number of valves, any number of pumps, any number of condensers, and any number of expanders, not limited to those shown in Figure 2.
  • the quantity of such components in the illustrated embodiment of Figure 2 is merely an example, and any suitable quantity of these components may be provided in other embodiments.
  • the plurality of recuperators 130a-130c may include three or more recuperators, such as the first recuperator 130a, the second recuperator 1 30b, and the third recuperator 1 30c.
  • Each of the recuperators 1 30a-130c may be selectively fluidly coupled to the working fluid circuit 102 and configured to transfer thermal energy between the high pressure side and the low pressure side of the working fluid circuit 1 02 when fluidly coupled to the working fluid circuit 102.
  • the recuperators 1 30a-1 30c may be disposed in series on the high pressure side of the working fluid circuit 1 02 upstream of the second expander 1 60b.
  • the second recuperator 1 30b may be disposed upstream of the first recuperator 130a
  • the third recuperator 1 30c may be disposed upstream of the second recuperator 130b on the high pressure side.
  • the first recuperator 1 30a, the second recuperator 1 30b, and the third recuperator 1 30c may be disposed in series on the low pressure side of the working fluid circuit 1 02, such that the second recuperator 130b may be disposed downstream of the first recuperator 130a, and the third recuperator 130c may be disposed downstream of the second recuperator 1 30b on the low pressure side.
  • the first recuperator 1 30a may be disposed downstream of the first expander 1 60a on the low pressure side
  • the second recuperator 1 30b may be disposed downstream of the second expander 160b on the low pressure side.
  • the heat source stream 1 10 may be a waste heat stream such as, but not limited to, a gas turbine exhaust stream, an industrial process exhaust stream, or other types of combustion product exhaust streams, such as furnace or boiler exhaust streams, coming from or derived from the heat source 108.
  • the heat source 1 08 may be a gas turbine, such as a gas turbine power/electricity generator or a gas turbine jet engine, and the heat source stream 1 10 may be the exhaust stream from the gas turbine.
  • 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 1 0 may derive thermal energy from renewable sources of thermal energy, such as solar or geothermal sources.
  • the third pump 1 50a is replaced with a first stage compressor
  • the second pump 150b is replaced with a second stage compressor
  • the first pump 1 50c is a third stage pump.
  • the second condenser 1 40b may be disposed upstream of the first condenser 140c and downstream of the third condenser 140a along the flow direction of working fluid through the working fluid circuit 102.
  • the heat engine system 1 00 includes three stages of pumps and condensers, such as first, second, and third pump/condenser stages.
  • the first pump/condenser stage may include the third condenser 140a fluidly coupled to the working fluid circuit 102 upstream of the third pump 1 50a
  • the second pump/condenser stage may include the second condenser 140b fluidly coupled to the working fluid circuit 102 upstream of the second pump 1 50b
  • the third pump/condenser stage may include the first condenser 1 40c fluidly coupled to the working fluid circuit 1 02 upstream of the first pump 150c.
  • the heat engine system 1 00 may include a variable frequency drive coupled to the first pump 150c, the second pump 150b, and/or the third pump 150a.
  • the variable frequency drive may be configured to control mass flow rate, pressure, or temperature of the working fluid within the working fluid circuit 1 02.
  • the heat engine system 1 00 may include a drive turbine coupled to the first pump 150c, the second pump 1 50b, or the third pump 150a.
  • the drive turbine may be configured to control mass flow rate, pressure, or temperature of the working fluid within the working fluid circuit 1 02.
  • the drive turbine may be the first expander 1 60a, the second expander 1 60b, another expander or turbine, or combinations thereof.
  • the heat engine system 1 00 may include a process heating system 230 fluidly coupled to and in thermal communication with the low pressure side of the working fluid circuit 1 02.
  • the process heating system 230 may include a process heat exchanger 236 and a control valve 234 operatively disposed on a fluid line 232 coupled to the low pressure side and under control of the control system 101 .
  • the process heat exchanger 236 may be configured to transfer thermal energy from the working fluid on the low pressure side of the working fluid circuit 1 02 to a heat-transfer fluid flowing through the process heat exchanger 236.
  • the process heat exchanger 236 may be configured to transfer thermal energy from the working fluid on the low pressure side of the working fluid circuit 1 02 to methane during a preheating step to form a heated methane fluid.
  • the thermal energy may be directly transferred or indirectly transferred (e.g., via a heat-transfer fluid) to the methane fluid.
  • the heat source stream 1 10 may be derived from the heat source 108 configured to combust the heated methane fluid, such as a gas turbine electricity generator.
  • the heat engine system 1 00 may include a recuperator bus system 220 fluidly coupled to and in thermal communication with the low pressure side of the working fluid circuit 1 02.
  • the recuperator bus system 220 may include turbine discharge lines 170a, 170b, control valves 1 68a, 168b, bypass line 210 and bypass valve 21 2, fluid lines 222, 224, and other lines and valves fluidly coupled to the working fluid circuit 1 02 downstream of the first expander 1 60a and/or the second expander 160b and upstream of the condenser 1 40a.
  • one end of a fluid line 224 may be fluidly coupled to the turbine discharge line 170b, the fluid line 222, or the process heating line 232, and the other end of the fluid line 224 may be fluidly coupled to a point on the working fluid circuit 1 02 disposed downstream of the recuperator 1 30b and upstream of the recuperator 130c on the low pressure side.
  • the working fluid circulated, flowed, or otherwise utilized in the working fluid circuit 102 of the heat engine system 100, 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 1 02 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 typically 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. Due in part to a relatively high working pressure of carbon dioxide, a carbon dioxide system may be much more compact than systems using other working fluids.
  • carbon dioxide CO2
  • SC-CO2 supercritical carbon dioxide
  • sub-CCb subcritical carbon dioxide
  • the working fluid in the working fluid circuit 102 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-C02 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 102 generally has a high pressure side and a low pressure side and contains a working fluid circulated within the working fluid circuit 102.
  • 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 1 00 or thermodynamic cycle.
  • the working fluid is in a supercritical state over certain portions of the working fluid circuit 1 02 of the heat engine system 100 (e.g.
  • thermodynamic cycle may be operated such that the working fluid is maintained in a supercritical state throughout the entire working fluid circuit 102 of the heat engine system 100.
  • the pumps 1 50a and 1 50b may be replaced with compressors, the pump 150c is a pump, and the high pressure side of the working fluid circuit 102 may start downstream of the pump 1 50c, such as at the discharge outlet of the pump 150c, and end at any of the expanders 160a or 1 60b, and the low pressure side of the working fluid circuit 1 02 may start downstream of any of the expanders 160a or 1 60b and end upstream of the pump 1 50c, such as at the inlet of the pump 1 50c.
  • the low pressure side of the working fluid circuit 102 includes the working fluid (e.g., CO2 or sub-CC ) at a pressure of less than 1 5 MPa, such as about 12 MPa or less, or about 10 MPa or less.
  • the low pressure side of the working fluid circuit 102 may have a pressure within a range from about 1 MPa to about 10 MPa, more narrowly within a range from about 2 MPa to about 8 MPa, and more narrowly within a range from about 4 MPa to about 6 MPa, such as about 5 MPa.
  • the heat engine system 1 00 further includes the expander 1 60a, the expander 1 60b, and the shaft 162.
  • Each of the expanders 160a, 160b may be fluidly coupled to the working fluid circuit 102 and disposed between the high and low pressure sides and configured to convert a pressure drop in the working fluid to mechanical energy.
  • the driveshaft 162 may be coupled to the expander 1 60a, the expander 1 60b, or both of the expanders 160a, 1 60b.
  • the shaft 162 may be configured to drive one or more devices, such as a generator or alternator (e.g., the generator 1 64), a motor, a generator/motor unit, a pump or compressor (e.g. , the pumps 1 50a-150c), and/or other devices, with the generated mechanical energy.
  • the generator 1 64 may be a generator, an alternator (e.g., permanent magnet alternator), or another device for generating electrical energy, such as by transforming mechanical energy from the shaft 162 and one or more of the expanders 160a, 1 60b to electrical energy.
  • a power outlet (not shown) may be electrically coupled to the generator 1 64 and configured to transfer the generated electrical energy from the generator 164 to an electrical grid 166.
  • the electrical grid 166 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 1 66 generally contains at least one alternating current bus, alternating current grid, alternating current circuit, or combinations thereof.
  • the heat engine system 1 00 further includes at least one pump/compressor and at least one condenser/cooler, but certain embodiments generally include a plurality of condensers 1 40a-1 40c (e.g., condenser or cooler) and pumps 150a-150c (e.g., pump or replaced with compressor).
  • Each of the condensers 140a-140c may independently be a condenser or a cooler and may independently be gas-cooled (e.g. , air, nitrogen, or carbon dioxide) or liquid-cooled (e.g., water, solvent, or a mixture thereof).
  • Each of the pumps 1 50a-1 50c may independently be a pump or may be replaced with a compressor and may independently be fluidly coupled to the working fluid circuit 1 02 between the low pressure side and the high pressure side of the working fluid circuit 102. Also, each of the pumps 1 50a-1 50c may be configured to circulate and/or pressurize the working fluid within the working fluid circuit 102.
  • the condensers 140a-1 40c may be in thermal communication with the working fluid in the working fluid circuit 1 02 and configured to remove thermal energy from the working fluid on the low pressure side of the working fluid circuit 1 02.
  • valves may provide control and adjustability to the temperature of the working fluid entering the expander 160a and/or the expander 1 60b.
  • the valves may be controllable, fixed (orifice), diverter valves, 3-way valves, or even eliminated in some embodiments.
  • each of the additional components e.g. , additional waste heat exchangers and recuperators may be used or eliminated in certain embodiments).
  • recuperator 1 30b may not be utilized in certain applications.
  • the common shaft or driveshaft 162 may be employed or, in other embodiments, two or more shafts may be used together or independently with the pumps 1 50a-1 50c, the expanders 1 60a, 160b, the generator 164, and/or other components.
  • the expander 160b and the pump 150c share a common shaft
  • the expander 160a and the generator 1 64 share another common shaft.
  • the expanders 1 60a, 1 60b, the pump 1 50c, and the generator 1 64 share a common shaft, such as the driveshaft 1 62.
  • the other pumps may be integrated with the shaft as well.
  • the process heating system 230 may be a loop to provide thermal energy to heat source fuel, for example, a gas turbine with preheat fuel (e.g. , methane), process steam, or other fluids.
  • preheat fuel e.g. , methane
  • the respective shafts 1 62 may be individual shafts attached (generally bolted together) for concomitant rotation at the same speed.
  • FIG. 4 illustrates an embodiment of a method 264 that may be utilized by processor 86, or any other suitable processor or controller, to control the heat engine system 1 00 during startup or shutdown.
  • the illustrated method 264 includes an inquiry as to whether startup or shutdown has been initiated (block 266). If startup or shutdown has not been initiated, then the method 264 includes implementing normal operation control logic (block 268). However, if startup or shutdown has been initiated, the method 264 proceeds to an isolation phase 270.
  • the processor 86 determines a quantity of working fluid to isolate from the high pressure side (block 272), which waste heat exchangers of a plurality of waste heat exchangers 120a-d to isolate from the high pressure side (block 274), and which valves of a plurality of valves to position in a closed position to isolate the desired waste heat exchangers from the high pressure side (block 276). Based on such determinations, the processor 86 may selectively open or close each of the plurality of valves (block 278).
  • the processor 86 determines which portion of the working fluid circuit 1 02, which includes the working fluid, to isolate from the flow path of the working fluid flowing through the high and low pressure sides of the selectively configured working fluid circuit 1 02. In doing so, the processor 86 may effectively isolate piping of the working fluid circuit 1 02 that contains working fluid at different process conditions (e.g., temperatures, pressures, etc.) than the working fluid flowing through the high and low pressure sides. In some embodiments, the isolated working fluid may subsequently be utilized as a working fluid supply source that is internal to the working fluid circuit 1 02. By providing an internal working fluid supply source in this way, certain embodiments may reduce or eliminate the need for a storage tank that is external to the working fluid circuit 1 02.
  • the temperature and/or pressure of the working fluid may be estimated based on flow parameters, comparison to data acquired from previous operations, and so forth.
  • the blocks shown in the analysis phase 280 are meant to illustrate, but not limit, presently contemplated embodiments.
  • the valves that were selectively closed in block 278 are maintained in a closed position (block 286) to maintain a portion of the working fluid isolated from the flow path of the working fluid flowing through the high and low pressure sides.
  • the method 264 proceeds to a mitigation phase 288 in which one or more of the closed valves are selectively opened to fluidly couple some or all of the isolated working fluid to the high pressure side (block 290). Once the selected valves are opened, some or all of the isolated working fluid is mixed with the working fluid flowing through the high and low pressure sides.
  • the selective opening of the valves in block 290 may enable a reduction in the temperature of the working fluid flowing through the working fluid circuit 1 02 without the need to access an external source.
  • the method 264 may further include determining the delta between the thresholds and the measured temperature and/or pressure and, based on the magnitude of the delta, determining the quantity of the valves to open. For instance, if the measured temperature and/or pressure are slightly above the threshold, then fewer valves may be opened than if the measured values are greatly above the thresholds.
  • the volume of the working fluid in the waste heat exchangers 1 20a, 120b, 120c, and 1 20d and the associated piping may be approximately 50% to approximately 70% of the total volume of working fluid in the working fluid circuit 1 02 in some embodiments.
  • the waste heat exchangers 1 20b, 120c, and 1 20d are isolated, approximately 30% of the total volume of the working fluid in the working fluid circuit 102 may be isolated from the flow path of the working fluid through the high and low pressure sides.
  • the average pressure in the heat engine system 100 may be about 10 MPa
  • the average temperature in the heat engine system 1 00 may be about 100°C
  • the average density in the heat engine system 1 00 may be about 188.5 kg/m 3 .
  • the average pressure may rise to approximately 1 9.7 MPa in an isochoric heat addition process (e.g., from 325.7MJ of heat addition). If the waste heat exchanger 120b is then removed from isolation and fluidly coupled to the working fluid flowing through the high and low pressure sides, an additional approximately 10% of working fluid volume may be added to the working fluid flowing through the high and low pressure sides without a mass increase, and the average density would thus become approximately 1 65 kg/m 3 .
  • the foregoing volume addition may reduce the average pressure from approximately 1 9.7 MPa to approximately 1 7 MPa without removing working fluid mass from the working fluid circuit 1 02 and pumping it to an external storage tank.
  • the waste heat exchanger 1 20d may correspond to the recuperator 130c
  • the waste heat exchanger 120c may correspond to the recuperator 1 30b
  • the waste heat exchanger 1 20b may correspond to the recuperator 130a.
  • the method 292 further includes inquiring as to whether the difference between the temperature of the working fluid proximate the outlet of the N th waste heat exchanger and the temperature of the working fluid proximate the outlet of the N th recuperator is within a predetermined allowable range (block 298). If the temperature differential is within the predetermined allowable range, then the method 292 proceeds by checking the temperature differentials for each set of corresponding waste heat exchangers and recuperators.
  • Figure 6 illustrates an embodiment of a method 302 for controlling the working fluid circuit 102 to maximize power generated by the heat engine system 100.
  • the processor 86, the valve controller 84, or any other suitable controller may employ a continuous power maximizing strategy in accordance with the logic of the method 302. More specifically, in such embodiments, the processor 86 may be continuously seeking a higher power output, not limited to a particular set point, throughout operation to maximize the power output of the heat engine system 100 as one or more conditions change during operation.
  • the method 302 may include receiving data corresponding to one or more process conditions (block 304).
  • the one or more process conditions may include pressures, temperatures, flow rates, and so forth, or any combination thereof.
  • the data may be received, for example, by the valve controller 84 from the process condition sensors 88 and transferred to the processor 86 for calculation of the Jacobian (i.e., the derivatives of the control variables) subject to one or more constraints (block 306).
  • the method 302 also includes adjusting, by a fraction of the Jacobian, each of a plurality of valves that control working fluid flow (block 308).
  • the valves 1 16a, 1 18a, 1 16b, 1 18b, and 128a may be selected as the plurality of valves to be utilized as the control points for the method 302.
  • the processor 86 may identify to what degree each of the valves 1 1 6a, 1 18a, 1 1 6b, 1 18b, and 1 28a should be partially opened or closed in an attempt to achieve the maximum power output in the quickest manner. Once identified, the processor 86 may communicate the valve adjustments to the valve controller 84, which implements the valve adjustments by selectively actuating each of the valves 1 1 6a, 1 1 8a, 1 1 6b, 1 18b, and 1 28a to achieve the desired valve positioning.
  • the method 302 includes idling (block 310) and inquiring as to whether the power output of the heat engine system 100 has reached a steady state (block 312). If the power output of the heat engine system 1 00 has not reached a steady state, then the method 302 remains in the idle state (block 31 0). However, once the power output of the heat engine system 1 00 reaches steady state, the method 302 is repeated to attempt to further increase the power output of the heat engine system 100. In this way, the method 302 may be continuously utilized throughout operation of the heat engine system 1 00 to maximize the power output as one or more process conditions change during operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne des systèmes et procédés pour commander un système de moteur thermique. Un procédé comprend l'amorçage d'un écoulement d'un fluide de travail à travers un circuit de fluide de travail possédant un côté haute pression et un côté basse pression en commandant une pompe pour mettre sous pression et faire circuler le fluide de travail à travers le circuit de fluide de travail et en déterminant une configuration du circuit de fluide de travail en déterminant lequel parmi une pluralité d'échangeurs de chaleur résiduelle et lequel parmi une pluralité de récupérateurs il faut positionner dans le côté haute pression du circuit de fluide de travail. Le procédé comprend également la détermination, sur base de la configuration déterminée du circuit de fluide de travail, pour chacune d'une pluralité de vannes, de s'il faut positionner chaque vanne respective dans une position ouverte, une position fermée ou une position partiellement ouverte et actionner chacune parmi la pluralité de vannes à la position ouverte, position fermée ou position partiellement ouverte déterminée.
PCT/US2014/053995 2013-09-05 2014-09-04 Procédés de commande pour systèmes de moteur thermique possédant un circuit de fluide de travail configurable de façon sélective WO2015034988A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14841902.1A EP3042049B1 (fr) 2013-09-05 2014-09-04 Système de moteur thermique et procédé de commande pour systèmes de moteur thermique possédant un circuit de fluide de travail configurable de façon sélective
KR1020167008673A KR102281175B1 (ko) 2013-09-05 2014-09-04 선택적으로 구성 가능한 작동 유체 회로를 갖는 열 기관 시스템의 제어 방법
EP16199227.6A EP3163029B1 (fr) 2013-09-05 2014-09-04 Procédé de commande pour systèmes de moteur thermique possédant un circuit de fluide de travail sélectivement configurable

Applications Claiming Priority (10)

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US201361874321P 2013-09-05 2013-09-05
US61/874,321 2013-09-05
US201462010706P 2014-06-11 2014-06-11
US201462010731P 2014-06-11 2014-06-11
US62/010,731 2014-06-11
US62/010,706 2014-06-11
US14/475,640 US9874112B2 (en) 2013-09-05 2014-09-03 Heat engine system having a selectively configurable working fluid circuit
US14/475,678 2014-09-03
US14/475,678 US9926811B2 (en) 2013-09-05 2014-09-03 Control methods for heat engine systems having a selectively configurable working fluid circuit
US14/475,640 2014-09-03

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