WO2010058356A2 - Vannes pour turbines à gaz et turbines à gaz à pression multiple, et turbines à gaz les accompagnant - Google Patents

Vannes pour turbines à gaz et turbines à gaz à pression multiple, et turbines à gaz les accompagnant Download PDF

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Publication number
WO2010058356A2
WO2010058356A2 PCT/IB2009/055154 IB2009055154W WO2010058356A2 WO 2010058356 A2 WO2010058356 A2 WO 2010058356A2 IB 2009055154 W IB2009055154 W IB 2009055154W WO 2010058356 A2 WO2010058356 A2 WO 2010058356A2
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WO
WIPO (PCT)
Prior art keywords
valve
inlet
outlet
port
gas
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Application number
PCT/IB2009/055154
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English (en)
Other versions
WO2010058356A3 (fr
Inventor
David Lior
Original Assignee
Etv Motors Ltd.
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Publication date
Application filed by Etv Motors Ltd. filed Critical Etv Motors Ltd.
Priority to US13/127,726 priority Critical patent/US20110262269A1/en
Publication of WO2010058356A2 publication Critical patent/WO2010058356A2/fr
Publication of WO2010058356A3 publication Critical patent/WO2010058356A3/fr
Priority to IL212740A priority patent/IL212740A0/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/08—Semi-closed cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/006—Open cycle gas-turbine in which the working fluid is expanded to a pressure below the atmospheric pressure and then compressed to atmospheric pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16—Control of working fluid flow
    • F02C9/18—Control of working fluid flow by bleeding, bypassing or acting on variable working fluid interconnections between turbines or compressors or their stages

Definitions

  • the present invention in some embodiments, relates to the field of gas-turbines, and more particularly, but not exclusively, to gas-turbines operable in both high-pressure (Brayton cycle) and low-pressure (inverse Brayton cycle) modes.
  • the present invention in some embodiments, relates to the field of gas-turbines, and more particularly, but not exclusively, to gas-turbines operable in low-pressure mode (inverse Brayton cycle).
  • Gas-turbines are known for being lightweight, reliable and requiring little maintenance compared to alternative work-producing motors, e.g. an internal combustion engine (ICE). Above all, gas-turbines are known for efficiently converting chemical energy stored in a combustible fuel to mechanical energy when working at an optimum work point. However, in spite of their potential, gas-turbines are currently not well known in applications requiring work-producing motors - for example ground vehicles such as cars and trucks - for several reasons.
  • ICE internal combustion engine
  • a given gas-turbine may generate a certain power at high efficiency for a prescribed load, but is less efficient at part load, particularly if turbine speed is maintained.
  • Many applications, vehicular applications in particular, generally have changing power demands, for instance requiring more power for rapid acceleration or climbing hills, and requiring less power when driving in traffic.
  • Turbine lag it takes a noticeably long time for a given gas-turbine to speed-up to produce more power, e.g., for acceleration. Thus, if turbine speed is reduced when power demand is low, a sudden increased power demand can be met only after a noticeable time lag.
  • a third reason is that the lifetime of gas-turbines is severely limited by startup/shutdown events. Unlike an ICE, it is not practical to shut down a gas-turbine when idling
  • a fourth reason is that the power requirements for many applications, e.g. ground vehicles, are low compared to the power gas-turbines efficiently produce. Although large gas- turbines are relatively efficient, the efficiency of a gas-turbine decreases with smaller size (less than 300 kW) for various reasons including leakage around the periphery of the turbine which is increasingly significant with smaller turbine size.
  • gas-turbines are operated according to either a high-pressure Brayton 5 cycle or a low-pressure inverse Brayton cycle.
  • a gas-turbine operating according to the inverse Brayton cycle efficiently produces less power than a similar-sized gas-turbine operating according to the Brayton cycle.
  • Figure IA a gas-turbine 2 in a typical Brayton cycle operation
  • Figure IB a gas-turbine 4 in a typical inverse Brayton cycle operation
  • Both gas-turbines 2 and 4 comprise a compressor 20 and a turbine
  • Gas-turbines such as 2 or 4 typically include gas-turbine controller 36 that monitors and controls the gas-turbine, including by regulating the amount of fuel supplied to combustor 26 by fuel- supply unit 34.
  • gas-turbines such as 2 or 4 typically include a heat- exchanger 52, such as a recuperator or regenerator.
  • Heat-exchanger 52 includes a cold- stream conduit 54 and a hot-stream conduit 56, both having inlets 58 and 60, respectively, and outlets 62 and 64, respectively.
  • Heat-exchanger 52 increases the thermal efficiency of a gas-turbine by recovering heat from hot exhaust gases passing through hot-stream conduit 56 to preheat air passing through cold-stream conduit 54 prior to entering combustor 26.
  • a heat- exchanger 52 such as a recuperator or regenerator.
  • Heat-exchanger 52 includes a cold- stream conduit 54 and a hot-stream conduit 56, both having inlets 58 and 60, respectively, and outlets 62 and 64, respectively.
  • Heat-exchanger 52 increases the thermal efficiency of a gas-turbine by recovering heat from hot exhaust gases passing through hot-stream conduit 56 to preheat air passing through cold-stream conduit 54 prior to entering combustor 26.
  • the gas-turbine In a first valving configuration the gas-turbine operates in a high-pressure mode according to a Brayton cycle. In a second valving configuration the gas-turbine operates in a low-pressure mode according to an inverse Brayton cycle.
  • the gas-turbine is toggled between the two modes by the synchronized switching of a plurality of valves between the two valving configurations changing the pressure and therefore the mass flow through the gas-turbine while maintaining a constant temperature and shaft speed, allowing two substantially equally efficient power outputs, where the power output during low-pressure mode operation is less than during high- pressure mode operation.
  • aspects of the invention relate to valves suitable for use with gas-turbines that, in some embodiments, allow switching between high-pressure and low-pressure operation modes of a gas-turbine. Aspects of the invention relate to gas-turbines that are configured to operate in both high-pressure and low-pressure modes.
  • aspects of the invention relate to valves suitable for use with gas-turbines that, in some embodiments, allow switching between high-pressure, low-pressure and intermediate- pressure operation modes of a gas-turbine.
  • aspects of the invention relate to gas-turbines that are configured to operate in high-pressure, low-pressure and intermediate-pressure modes.
  • aspects of the invention relate to valves that allow simple and efficient varying of the pressure and power output of a gas-turbine, that in some embodiments is substantially continuous.
  • aspects of the invention relate to gas-turbines that are configured to efficiently operate in different pressure modes, allowing different power outputs at substantially similar efficiencies.
  • a gas-turbine configured for operation according to both Brayton-cycle and inverse-Brayton cycle, comprising: a) a multiport valve including movable valve members and at least five ports of which at least two inlet ports and at least two outlet ports: a compressor-outlet inlet port, an ambient inlet port, a heat-exchanger cold-stream inlet outlet port, an exhaust outlet port, and a fifth port; b) a compressor-outlet of a compressor of the gas-turbine in fluid communication with the compressor-outlet inlet port; and c) a heat-exchanger cold-stream inlet of a heat-exchanger of the gas-turbine in fluid communication with the heat-exchanger cold-stream inlet outlet port; wherein during Brayton-cycle operation of the gas-turbine, a valve member blocks fluid communication between the compressor-outlet inlet port and the exhaust outlet port, and a valve member blocks fluid communication between the ambient inlet port and the heat-exchange
  • a multiport valve suitable for use with a gas-turbine and allowing switching the mode of operation of a gas-turbine between a high-pressure mode according to a Brayton cycle and a low-pressure mode according to an inverse Brayton cycle, the valve comprising: a) a valve body defining a void in the form of a plurality of fluid conduits; b) at least five ports leading to the void of which at least two inlet ports and at least two outlet ports: a compressor-outlet inlet port, an ambient inlet port, a heat-exchanger cold- stream inlet outlet port, an exhaust outlet port and a fifth port; c) a first valve member inside the valve body movable between at least two positions, a first position and a second position; and d) a second valve member inside the valve body movable between at least two positions, a first position and a second position. where the position of the first valve member and the position of the second valve member (together
  • a gas-turbine configured to switch between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, comprising a multiport valve as described herein.
  • the gas-turbine is also configured to switch to an intermediate pressure mode between the high-pressure operation mode and the low-pressure operation mode.
  • a method of operating a gas-turbine according to an inverse Brayton cycle comprising: a) providing a conduit allowing fluid communication between a compressor of the gas-turbine and a cold-stream inlet of a heat-exchanger of the gas-turbine; and b) during inverse Brayton cycle operation of the gas-turbine, directing fluid from the compressor to the heat-exchanger cold-stream inlet through the conduit so that a portion of the fluid entering the heat-exchanger cold-stream inlet is from the compressor.
  • inlet air is mixed with a portion of the oxygen-depleted exhaust from the compressor, decreasing oxygen content of the combustible mixture in the combustor, reducing the amount of NOx produced in the combustor and emitted by the gas-turbine.
  • a gas-turbine comprising, when operating according to an inverse Brayton cycle, a) an air inlet configured to direct fluid into a cold-stream conduit of a heat-exchanger through a cold- stream inlet; b) conduits to direct fluid from the cold-stream conduit to a combustor, from the combustor to a turbine, from the turbine to a hot- stream conduit of the heat-exchanger, from the hot- stream conduit to a compressor, and from the compressor to an exhaust outlet port; and c) a conduit allowing passage of fluid from the compressor into the cold-stream inlet of the heat-exchanger.
  • the gas-turbine is configured to operate only according to the inverse Brayton cycle. In some embodiments, the gas-turbine is a multi- power gas-turbine configured to operate according to both the Brayton cycle and the inverse Brayton cycle. According to an aspect of some embodiments of the invention, there is also provided a motor vehicle (e.g., an automobile, a light truck, a truck, a bus) comprising a gas-turbine substantially as described herein.
  • a motor vehicle e.g., an automobile, a light truck, a truck, a bus
  • high-pressure mode refers to operation of a gas-turbine where compressor inlet pressure is close to atmospheric ( ⁇ 1 x ambient) and compressor outlet (exhaust) pressure is superatmospheric (typically ⁇ 3 x ambient pressure).
  • low-pressure mode refers to operation of a gas-turbine where compressor inlet pressure is subatmospheric (-0.3 x ambient pressure) and compressor outlet (exhaust) pressure is close to atmospheric ( ⁇ 1 x ambient pressure).
  • intermediate pressure mode refers to operation of a gas- turbine where compressor inlet pressure is subatmospheric (between above 0.3 x ambient pressure to ⁇ 1 x ambient pressure) and compressor outlet (exhaust) pressure is higher than atmospheric (between above 1 x ambient pressure to ⁇ 3 x ambient pressure).
  • FIGS. IA and IB are schematic depictions of a Brayton cycle gas-turbine (IA) and an inverse Brayton cycle gas-turbine (IB);
  • FIGS. 2A and 2B are schematic depictions of an embodiment of a 5-port valve suitable for use with a gas-turbine in two configurations allowing the gas-turbine to operate in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIGS. 3 A and 3B are schematic depictions of an embodiment of a gas-turbine including an embodiment of a 5-port valve of Figures 2 where the valve is in two configurations so that the gas-turbine operates in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIG. 4 is of a conceptual graph qualitatively showing thermal efficiency as a function of power output of various embodiments of gas-turbines described herein;
  • FIGS. 5 A and 5B are schematic depictions of an embodiment of a gas-turbine including an embodiment of a 5-port valve where the valve is in two configurations allowing the gas-turbine to operate in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIGS. 6 A and 6B are schematic depictions of an embodiment of a 6-port valve suitable for use with a gas-turbine in two configurations allowing the gas-turbine to operate in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIGS. 7 A and 7B are schematic depictions of an embodiment of a gas-turbine including an embodiment of a 6-port valve of Figures 6 where the valve is in two configurations so that the gas-turbine operates in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIGS. 8 A and 8B are schematic depictions of an embodiment of a 6-port valve suitable for use with a gas-turbine in two configurations allowing the gas-turbine to operate in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIGS. 9A and 9B are schematic depictions of an embodiment of a gas-turbine including an embodiment of a 6-port valve of Figures 8 where the valve is in two configurations so that the gas-turbine operates in a high-pressure operation mode and in a low-pressure operation mode, respectively;
  • FIG. 10 is a schematic depiction of an embodiment of a valve suitable for use with a gas-turbine, allowing the gas-turbine to operate in at least one intermediate pressure operation mode in addition to a low-pressure operation mode and a high-pressure operation mode;
  • FIG 11 is a schematic depiction of an embodiment of a gas-turbine including an embodiment of a valve of Figure 10, where the valve is set so that the gas-turbine operates in an intermediate pressure operation mode;
  • FIG. 12 is a schematic depiction of an embodiment of a gas-turbine including an embodiment of a six -port valve similar to the valve depicted in Figure 10;
  • FIGS. 13A and 13B are schematic depictions of an embodiment of a 5-port valve useful for continuously varying the mass flow to the combustor of a gas-turbine in a high- pressure operation mode, in high and low-mass flow rate configurations, respectively;
  • FIGS. 14A and 14B are schematic depictions of an embodiment of a 5-port valve useful for continuously varying the mass flow to the combustor of a gas-turbine in a low- pressure operation mode, in high and low mass flow rate configurations, respectively;
  • FIGS. 15 A, 15B and 15C are schematic depictions of embodiments of valves useful for continuously varying the mass flow to the combustor of a gas-turbine high and low- pressure operation modes;
  • FIG. 16 is a gas-turbine including a valve suitable for switching the gas-turbine between at least two pressure level operation modes and useful for reducing NOx emissions of the gas-turbine when in low-pressure operation mode;
  • FIGS. 17 A and 17B are two embodiments of a permeable section in a multiport valve suitable for use in a gas turbine and useful for reducing NOx emissions of the gas-turbine as described herein.
  • Some embodiments of the invention relate to multiport valves that allow switching between high-pressure operation (Brayton cycle) and low-pressure operation (inverse Brayton cycle) modes of a gas-turbine.
  • Some embodiments of the invention relate to multiport valves that allow operation of a gas-turbine in high-pressure, low-pressure and intermediate pressure modes.
  • Some embodiments of the invention relate to multiport valves that allow operation of a gas-turbine at a variable power output in high-pressure modes and/or low-pressure modes at relatively high efficiency by varying the mass flow through the gas-turbine. Some embodiments of the invention relate to valves that allow simple and efficient varying of the pressure, mass flow and power output of a gas-turbine, that in some embodiments is substantially continuous. Some embodiments of the invention relate to gas-turbines operating in a low-pressure mode (inverse Brayton mode) having reduced NOx emissions as well as valves useful for such gas-turbines.
  • a low-pressure mode inverse Brayton mode
  • a gas-turbine configured to switch between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, comprising: a) a multiport valve including movable valve members and at least five ports of which at least two inlet ports and at least two outlet ports: a compressor-outlet inlet port, an ambient inlet port, a heat-exchanger cold-stream inlet outlet port, an exhaust outlet port, and a fifth port; b) a compressor outlet of a compressor of the gas-turbine in fluid communication with the compressor-outlet inlet port; and c) a heat-exchanger cold- stream inlet of a heat-exchanger of the gas-turbine in fluid communication with the heat-exchanger cold-stream inlet outlet port; wherein during Brayton-cycle operation of the gas-turbine, a valve member blocks fluid communication between the compressor-outlet inlet port and the exhaust outlet port and a valve
  • the fifth port is a compressor-inlet outlet port in fluid communication with an inlet of the compressor of the gas-turbine, and during inverse Brayton-cycle operation of the gas-turbine, a valve member blocks fluid communication between the ambient inlet port and the compressor-inlet outlet port.
  • the gas-turbine further comprises an additional valve functionally associated with the hot-stream outlet of the heat-exchanger, wherein during inverse Brayton-cycle operation of the gas-turbine, the additional valve allows fluid communication from the hot- stream outlet of the heat-exchanger to an inlet of the compressor.
  • the additional valve allows fluid communication from the hot-stream outlet of the heat-exchanger to an exhaust outlet of the gas-turbine.
  • An exemplary such embodiment is depicted in Figures 3 A and 3B.
  • the fifth port is a heat-exchanger hot-stream outlet inlet port in fluid communication with a hot- stream outlet of the heat-exchanger of the gas-turbine, and during inverse Brayton-cycle operation of the gas-turbine, a valve member blocks fluid communication between the heat-exchanger hot- stream outlet inlet port and the exhaust outlet port.
  • the gas-turbine further comprises an additional valve functionally associated with a hot-stream outlet of the heat-exchanger of the gas-turbine, and during inverse Brayton-cycle operation of the gas-turbine, the additional valve allows fluid communication from the hot- stream outlet of the heat-exchanger to an inlet of the compressor.
  • the additional valve allows fluid communication from ambient to an inlet of the compressor.
  • An exemplary such embodiment is depicted in Figures 5 A and 5B.
  • the multiport valve includes six ports, of which three are inlet ports and three are outlet ports.
  • the fifth port is a compressor-inlet outlet port in fluid communication with an inlet of the compressor, and during inverse Brayton-cycle operation of the gas-turbine a valve member blocks fluid communication between the ambient inlet port and the compressor-inlet outlet port; and the multiport valve further includes a sixth port, a heat-exchanger hot-stream outlet inlet port in fluid communication with a hot-stream outlet of the heat-exchanger of the gas-turbine.
  • the gas-turbine further comprises an additional valve functionally associated with a hot-stream outlet of the heat- exchanger of the gas-turbine, and during inverse Brayton-cycle operation of the gas-turbine, the additional valve allows fluid communication from the hot-stream outlet of the heat- exchanger of the gas-turbine to an inlet of the compressor of the gas-turbine.
  • the additional valve allows fluid communication from the hot-stream outlet of the heat-exchanger of the gas-turbine to an exhaust outlet of the gas-turbine through the heat-exchanger hot-stream outlet inlet port.
  • the gas-turbine further comprises a component functionally associated with the heat-exchanger hot-stream outlet inlet port, allowing flow of fluid from the hot-stream outlet of the heat-exchanger through the heat-exchanger hot-stream outlet inlet port and blocking flow of fluid from the multiport valve to the hot-stream outlet of the heat- exchanger through the heat-exchanger hot-stream outlet inlet port.
  • the component is a undirectional valve that is part of the multiport valve. An exemplary such embodiment is depicted in Figures 7 A and 7B.
  • the multiport valve further comprising a bypass conduit bypassing the valve void, providing fluid communication between the heat-exchanger hot-stream outlet inlet port and the compressor- inlet outlet port, wherein during Brayton-cycle operation of the gas-turbine, a valve member blocks the fluid communication between the heat-exchanger hot-stream outlet inlet port and the compressor-inlet outlet port through the bypass conduit.
  • a bypass conduit bypassing the valve void, providing fluid communication between the heat-exchanger hot-stream outlet inlet port and the compressor- inlet outlet port, wherein during Brayton-cycle operation of the gas-turbine, a valve member blocks the fluid communication between the heat-exchanger hot-stream outlet inlet port and the compressor-inlet outlet port through the bypass conduit.
  • a multiport valve suitable for use with a gas-turbine and allowing switching the mode of operation of a gas-turbine between a high-pressure mode according to a Brayton cycle and a low-pressure mode according to an inverse Brayton cycle, the valve comprising: a) a valve body defining a void in the form of a plurality of fluid conduits; b) at least five ports leading to the void of which at least two inlet ports and at least two outlet ports: a compressor-outlet inlet port, an ambient inlet port, a heat- exchanger cold- stream inlet outlet port, an exhaust outlet port and a fifth port; c) a first valve member inside the valve body movable between at least two positions, a first position and a second position; and d) a second valve member inside the valve body movable between at least two positions, a first position and a second position where the position of the first valve member and the position of the second valve member (together) define
  • first valve member and the second valve member are configured to cooperatively move between the first positions and the second positions. In some embodiments, the first valve member and the second valve member are configured to move independently between the first positions and the second positions.
  • first valve member in the first position the first valve member is in contact with a first valve seat and in the second position in contact with a second valve seat. In some embodiments, in the first position the second valve member is in contact with a third valve seat and in the second position in contact with a third valve seat.
  • a given valve member blocks fluid communication between specific ports. By blocking fluid communication is meant that the fluid communication between the ports is blocked to a sufficient degree to achieve the desired purpose (e.g., operating an associated gas-turbine in a desired mode), although there may be some leakage, for example as described below.
  • a given valve member in a first or second position a given valve member contacts a specific valve seat. By contacting a valve seat is meant contacting to a sufficient degree to achieve a desired purpose as described immediately herein above, for example, in some embodiments is meant "sealing contact”.
  • the first valve member in the first position blocks fluid communication (through the void) between the ambient inlet port and the heat-exchanger cold-stream inlet outlet port and in the second position blocks fluid communication (through the void) between the ambient inlet port and the fifth port, a compressor inlet outlet port; and the second valve member in the first position blocks fluid communication (through the void) between the compressor-outlet inlet port and the exhaust outlet port and in the second position blocks fluid communication (through the void) between the compressor-outlet inlet port and the heat-exchanger cold-stream inlet outlet port.
  • An exemplary such embodiment is valve 100 depicted in Figures 2 and 3.
  • the first valve member in the first position blocks fluid communication (through the void) between the compressor-outlet inlet port and the exhaust outlet port and in the second position blocks fluid communication (through the void) between the fifth port, a heat-exchanger hot-stream outlet inlet port, and the exhaust outlet port; and the second valve member in the first position blocks fluid communication (through the void) between the ambient inlet port and the heat-exchanger cold- stream inlet outlet port and in the second position blocks fluid communication (through the void) between the compressor- outlet inlet port and the heat-exchanger cold-stream inlet outlet port.
  • An exemplary such embodiment is depicted in Figures 5.
  • the first valve member in the first position blocks fluid communication (through the void) between the ambient inlet port and the heat-exchanger cold-stream inlet outlet port and in the second position blocks fluid communication (through the void) between the ambient inlet port and the fifth port, a compressor inlet outlet port; and the second valve member in the first position blocks fluid communication (through the void) between a sixth port, a heat-exchanger hot-stream outlet inlet port, and the heat-exchanger cold-stream inlet outlet port and in the second position blocks fluid communication (through the void) between the compressor-outlet inlet port and the heat-exchanger cold-stream inlet outlet port.
  • An exemplary such embodiment is depicted in Figures 6 and 7.
  • the valve further comprises a component functionally associated with the heat- exchanger hot- stream outlet inlet port , allowing flow of fluid into the void through the heat- exchanger hot-stream outlet inlet port and blocking flow of fluid from the void out through the heat-exchanger hot-stream outlet inlet port.
  • the component is a unidirectional valve (e.g., a check valve, in some embodiments located inside the valve body) configured to allow fluid to flow into the void of the valve body through the heat- exchanger hot- stream outlet inlet port but to block the flow of fluid from the valve body out through the heat-exchanger hot-stream outlet inlet port.
  • the valve further comprises a bypass conduit providing fluid communication bypassing the valve void between the heat-exchanger hot-stream outlet inlet port and the compressor inlet outlet port, and a third valve member inside the valve body movable between at least two positions, a first position and a second position, wherein in the first position the third valve member blocks fluid communication through the bypass conduit between the heat-exchanger hot-stream outlet inlet port and the compressor inlet outlet port through the bypass conduit and in the second position the third valve member blocks fluid communication through the void between the heat-exchanger hot-stream outlet inlet port and the exhaust outlet port.
  • the third valve member in the first position the third valve member is in contact with a fifth valve seat and in the second position the third valve member is in contact with a sixth valve seat.
  • first valve member, the second valve member and the third valve member are configured to cooperatively move between the first positions and the second positions.
  • at least one of the first valve member, the second valve member and the third valve member is configured to move between the first position and the second position independently of at least one other of the valve members.
  • At least one of the valve members is movable to at least one intermediate position between a respective first position and respective second position, thereby allowing fluid communication (through the void) between an inlet port and at least two outlet ports.
  • at least one valve member is fashioned as an airfoil having an aerodynamic profile (generally predefined aerodynamic profile) configured to direct the flow of fluid as desired through the fluid conduits of the valve body.
  • the second valve member is movable to at least one intermediate position, providing fluid communication (through the void) between the compressor-outlet inlet port and the heat-exchanger cold-stream inlet outlet port and the exhaust outlet port.
  • Exemplary such embodiments include valve 100, valve 102 and valve 103 depicted in Figures 10 and 11.
  • the second valve member is movable to a plurality of such intermediate positions, allowing variation of the relative size of the path between the compressor-outlet inlet port and the heat-exchanger cold-stream inlet outlet port to the relative size of the path between the compressor-outlet inlet port and the exhaust outlet port.
  • the first valve member is movable to an intermediate position, providing fluid communication between the ambient inlet port and the heat-exchanger cold- stream inlet outlet port and the compressor-inlet outlet port.
  • Exemplary such embodiments include valve 100, valve 102 and valve 103 depicted in Figures 10 and 11.
  • the first valve member is movable to a plurality of such intermediate positions, allowing variation of the relative size of the path between the ambient inlet port and the heat- exchanger cold-stream inlet outlet port to the relative size of the path between the ambient inlet port and the compressor inlet outlet port.
  • the third valve member is movable to an intermediate position, providing fluid communication between the heat- exchanger hot-stream outlet inlet port and the exhaust outlet port and the compressor-inlet outlet port.
  • An exemplary such embodiment is valve 103 depicted in Figures 10 and 11.
  • the third valve member is movable to a plurality of such intermediate positions, allowing variation of the relative size of the path between the heat- exchanger hot-stream outlet inlet port and the exhaust outlet port to the relative size of the path between the heat-exchanger hot-stream outlet inlet port and the compressor-inlet outlet port.
  • At least one valve member is configured to vary a size of a fluid path between an inlet port and an outlet port while the valve member in the first position and/or the second position.
  • the second valve member is configured to vary a size of a fluid path between the compressor-outlet inlet port and the heat-exchanger cold-stream inlet outlet port when in the first position.
  • the first valve member is configured to vary a size of a fluid path between the ambient inlet port and the heat-exchanger cold-stream inlet outlet port when in the second position.
  • An exemplary such embodiment is depicted in Figures 14.
  • the multiport valve further comprises an additional valve member movable inside the valve body and, the additional valve member configured to vary a size of a fluid path between the compressor-outlet inlet port and the heat-exchanger cold- stream inlet outlet port.
  • An exemplary such embodiment is depicted in Figure 15A and 15C.
  • the multiport valve further comprises an additional valve member movable inside the valve body and configured to vary a size of a fluid path between the ambient inlet port and the heat-exchanger cold-stream inlet outlet port.
  • An exemplary such embodiment is depicted in Figure 15B and 15C.
  • the valve further comprises a permeable section between a first region and a second region of the void in the valve body, providing fluid communication between the first region and the second region.
  • a permeable section may be implemented in any suitable way including a conduit, slits, pores and the like. The utility of such a permeable section is described hereinbelow.
  • the first region is in proximity of the exhaust outlet port and in some such embodiments between the second valve member and the exhaust outlet port.
  • the second region is in proximity of the heat-exchanger cold-steam inlet outlet port and in some such embodiments between the second valve member and heat-exchanger cold- stream inlet outlet port.
  • the permeable section is unidirectional, allowing passage of fluid from the first region to the second region, and blocking passage of fluid from the second region to the first region.
  • a unidirectional permeable section may be implemented in any suitable way including with the help of a unidirectional valve, a check valve (a unidirectional valve that functions automatically without an external control, e.g. variants of a swing check valve or reed valve) or a pump.
  • the permeable section is part of the second valve member.
  • a gas-turbine configured to switch between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, comprising a multiport valve as described herein.
  • the gas-turbine is also configured to switch to an intermediate pressure mode between the high-pressure operation mode and the low-pressure operation mode.
  • FIGS. 2A and 2B depict an embodiment of a valve 100, suitable for use with a gas- turbine, in side cross-section.
  • Valve 100 comprises a valve body 110 defining a single void in the form of a plurality of fluid conduits 120.
  • Valve 100 further includes two inlet ports and three outlet ports: an ambient inlet port 151, a compressor-outlet inlet port 152, a compressor- inlet outlet port 161, a heat-exchanger cold-stream inlet outlet port 162 and an exhaust outlet port 163, the five ports in fluid communication one with the other through fluid conduits 120.
  • Valve 100 further includes a first valve member 171 and a second valve member 181.
  • First valve member 171 is movable inside valve body 110 between at least two positions: a first position, depicted in Figure 2A, in contact with a first valve seat 172 in valve body 110 blocking fluid communication between ambient inlet port 151 and heat-exchanger cold- stream inlet outlet port 162 and a second position, depicted in Figure 2B, in contact with a second valve seat 173 in valve body 110 blocking fluid communication between ambient inlet port 151 and compressor- inlet outlet port 161.
  • Second movable valve member 181 is movable inside valve body 110 between at least two positions: a first position, depicted in Figure 2A, in contact with a third valve seat 182 in valve body 110 blocking fluid communication between compressor-outlet inlet port 152 and exhaust outlet port 163 and a second position, depicted in Figure 2B, in contact with a fourth valve seat 183 in valve body 110 blocking fluid communication between compressor-outlet inlet port 152 and heat- exchanger cold-stream inlet outlet port 162.
  • First movable valve member 171 is movable between the first and second positions by rotating around a first valve member axis 174.
  • Second movable valve member 181 is movable between the first and second positions by rotating around a second valve member axis 184.
  • valve 100 When valve members 171 and 181 are in the respective first position depicted in Figure 2A (configuration "1"), valve 100 allows an associated gas-turbine to operate in high- pressure operation mode, as is described further below. When valve members 171 and 181 are in the respective second position depicted in Figure 2B (configuration "2"), valve 100 allows an associated gas-turbine to operate in low-pressure operation mode.
  • valve members 171 and 181 are configured for cooperative movement, that is to say both valve members move together between the first position (Figure 2A) and the second position ( Figure 2B).
  • valve members 171 and 181 are independently operable.
  • valve member 171 may be in contact with first valve seat 172 (first position, Figure 2A), while second movable valve member 181 is in contact with fourth valve seat 183 (second position, Figure 2B).
  • valve members 171 and 181 are configured for positioning in at least one intermediate position, between the first positions and the second positions, allowing fluid from a given inlet port to flow to two outlet ports. Specifically, a portion of the fluid entering valve 100 from ambient inlet port 151 is directed to compressor-inlet outlet port 161, and another portion is directed to heat-exchanger cold-stream inlet outlet port 162. Similarly, a portion of the fluid entering through compressor-outlet inlet port 152 is directed to heat- exchanger cold- stream inlet outlet port 162 and another portion is directed to exhaust outlet port 163. The utility of some such intermediate positions is described hereinbelow.
  • FIGS 3 schematically depict an exemplary embodiment of a gas-turbine 10, comprising a valve 100 (as described above) operable in a Brayton cycle ( Figure 3A) and in an inverse Brayton cycle (Figure 3B).
  • Gas-turbine 10 further includes compressor 20 and turbine 22, together mounted on a common rotatable shaft 24 constituting a spool, combustor 26 and heat-exchanger 52.
  • Gas-turbine 10 also includes a 3-way valve 220 having an inlet 224 and two outlets, 221 and 222.
  • Valve 220 may be positioned as depicted in Figure 3A to providing fluid communication between inlet 224 and outlet 221, or as depicted in Figure 3B providing fluid communication between inlet 224 and outlet 222.
  • Valve 100 is configured to switch gas-turbine 10 between a high-pressure operation mode (Brayton cycle) depicted in Fig 3 A, and a low-pressure operation mode (inverse Brayton cycle) depicted in Fig 3B.
  • a high-pressure operation mode Brayton cycle
  • a low-pressure operation mode inverse Brayton cycle
  • valve members 171 and 181 of valve 100 are in a first position (as in Figure 2A) directing fluid entering through ambient inlet port 151 to compressor-inlet outlet port 161, and fluid entering through compressor-outlet inlet port 152 to heat-exchanger cold-stream inlet outlet port 162.
  • Ambient air is drawn through ambient inlet port 151 past compressor-inlet outlet port 161 into compressor 20, pass through compressor-outlet inlet port 152 and heat-exchanger cold- stream inlet outlet port 162 of valve 100 into cold-stream conduit 54 of heat-exchanger 52, to combust in combustor 26.
  • the combusted gases expand through turbine 22, and exit turbine 22 into hot- stream conduit 56 of heat-exchanger 52.
  • 3-way valve 220 is set so that the combusted gases exit gas-turbine 10 through exhaust outlet 30 after exiting heat-exchanger 52.
  • valve members 171 and 181 of valve 100 are in a second position (as in Figure 2B) directing fluid incoming through ambient inlet port 151 to heat-exchanger cold-stream inlet outlet port 162, and fluid coming through compressor-outlet inlet port 152 to exhaust outlet port 163.
  • Ambient air is drawn through ambient inlet port 151 past heat-exchanger cold-stream inlet outlet port 162 into cold-stream conduit 54 of heat- exchanger 52 and combusts in combustor 26.
  • the combusted gases exit turbine 22 into hot- stream conduit 56 of heat-exchanger 52.
  • 3-way valve 220 is set to directing the combusted gases into compressor 20.
  • the combusted gases exit compressor 20 and pass through compressor-outlet inlet port 152 to exit gas-turbine 10 through exhaust outlet port 163 of valve 100.
  • a gas-turbine comprises an embodiment of a valve similar to valve 100 of Figures 2A and 2B, where the valve is integrated in the gas-turbine in "reverse".
  • valve 100 includes three inlet ports and two outlet ports: an ambient 5 inlet port 151, a compressor-outlet inlet port 152, a heat-exchanger hot-stream outlet inlet port 153, a heat-exchanger cold-stream inlet outlet port 162 and an exhaust outlet port 163.
  • Figures 5 depict an exemplary embodiment of a gas-turbine 11, comprising a valve 100, and operable according to a Brayton cycle (Figure 5A) and an inverse Brayton cycle (Figure 5B).
  • Gas-turbine 11 further includes compressor 20 and turbine 22, together mounted on common
  • Gas-turbine 11 also includes a 3-way valve 225 having two inlets, 226 and 227, and an outlet 228.
  • Valve 225 may be positioned as depicted in Figure 5A providing fluid communication between inlet 226 and outlet 228, or as depicted in Figure 5B providing fluid communication between inlet 227 and outlet 228.
  • Valve 100 is configured to switch gas-turbine 11 between a high-pressure operation
  • valve members 171 and 181 of valve 100 are in a first position directing fluid from compressor-outlet inlet port 152 to heat-exchanger cold- stream inlet outlet port 162 and from heat-exchanger hot- stream outlet inlet port 153 to
  • valve members 171 and 181 of valve 100 are in a respective second position. Ambient air is drawn through ambient inlet port 151 and heat-
  • valve 102 suitable for use with a gas-turbine, in side cross-section.
  • Valve 102 comprises a valve body 110 defining a single void in the form of a plurality of fluid conduits 120.
  • Valve 102 further includes an ambient inlet port 151, a compressor-outlet inlet port 152, a heat-exchanger hot-stream outlet inlet port 153, a compressor-inlet outlet port 161, a heat-exchanger cold-stream inlet outlet port 162 and an exhaust outlet port 163, the six ports being in fluid communication one with the other through fluid conduits 120.
  • Valve 102 further includes a first valve member 171 and a second valve member 181.
  • First valve member 171 is movable inside valve body 110 having at least two positions: a first position, depicted in Figure 6A, in contact with a first valve seat 172 in valve body 110 blocking fluid communication between ambient inlet port 151 and heat-exchanger cold- stream inlet outlet port 162; and a second position, depicted in Figure 6B, in contact with a second valve seat 173 in valve body 110 blocking fluid communication between ambient inlet port 151 and compressor- inlet outlet port 161.
  • Second movable valve member 181 is movable inside valve body 110 having at least two positions: a first position, depicted in Figure 6 A, in contact with a third valve seat 182 in valve body 110 blocking fluid communication between compressor-outlet inlet port 152 and exhaust outlet port 163; and a second position, depicted in Figure 6B, in contact with a fourth valve seat 183 in valve body 110 blocking fluid communication between compressor-outlet inlet port 152 and heat- exchanger cold-stream inlet outlet port 162.
  • Valve 102 also includes a check valve 130 operable as a unidirectional valve and configured in valve body 110 to allow fluid flowing from heat-exchanger hot- stream outlet inlet port 153 to any of the outlet ports 161, 162 or 163 of valve 102, and to block fluid flowing from any of the outlet ports of valve 102 out through heat-exchanger hot-stream outlet inlet port 153.
  • valve members 171 and 181 of valve 102 are configured for cooperative movement, that is to say both valve members move together between the first position ( Figure 6A) and the second position ( Figure 6B).
  • valve members 171 and 181 are independently operable. For example, in such embodiments valve member 171 is in contact with first valve seat 172 (first position, Figure 6A), while second movable valve member 181 is in contact with fourth valve seat 183 (second position, Figure 6B).
  • valve members 171 and 181 of valve 102 are configured for positioning in at least one intermediate position, between the first positions and the second positions, thereby allowing fluid from a given inlet port to flow to two outlet ports.
  • the utility of some such intermediate positions is described hereinbelow.
  • Gas-turbine comprising 6-port valve 102
  • Figures 7 depict an exemplary embodiment of a gas-turbine 12 comprising an embodiment of valve 102, and operable in a Brayton cycle (Figure 7A) and in an inverse Brayton cycle (Figure 7B).
  • Gas-turbine 12 also includes 3-way valve 220.
  • An outlet 221 of valve 220 is connected to heat-exchanger hot-stream outlet inlet port 153 of valve 102 so that exhaust gas is discharged through exhaust outlet port 163 of valve 102.
  • Valve 102 is configured to switch gas-turbine 12 between a high-pressure operation mode depicted in Figure 7 A, and a low-pressure operation mode depicted in Figure 7B
  • valve members 171 and 181 of valve 102 are in a respective first position.
  • Ambient air is drawn through ambient inlet port 151 and compressor-inlet outlet port 161 of valve 102 into compressor 20, pass through compressor-outlet inlet port 152 and heat-exchanger cold- stream inlet outlet port 162 of valve 102 into cold- stream conduit 54 of heat-exchanger 52 to combust in combustor 26.
  • the combusted gases expand through turbine 22, and exit turbine 22 into hot-stream conduit 56 of heat-exchanger 52.
  • the combusted gases are directed by 3-way valve 220 to heat-exchanger hot- stream outlet inlet port 153 of valve 102.
  • the combusted gases pass through check valve 130 and are then discharged to the surroundings through exhaust outlet port 163.
  • valve members 171 and 181 of valve 102 are in a respective second position.
  • Ambient air is drawn through ambient inlet port 151 and through heat-exchanger cold-stream inlet outlet port 162 of valve 102 into cold-stream conduit 54 of heat-exchanger 52 to combust in combustor 26.
  • the combusted gases expand through turbine 22 into hot- stream conduit 56 of heat-exchanger 52.
  • 3-way valve 220 directs the gases into compressor 20, to exit compressor 20, and pass through compressor-outlet inlet port 152 of valve 102 and exit gas-turbine 12 through exhaust outlet port 163 of valve 102.
  • Check valve 130 blocks the exhaust gases from flowing back through heat-exchanger hot-stream outlet inlet port 153 of valve 102 towards 3-way valve 220.
  • FIGS 8A and 8B depict a valve 103, suitable for use with a gas-turbine, in side cross-section.
  • Valve 103 comprises a valve body 110 defining a single void in the form of a plurality of fluid conduits 120.
  • Valve 103 further includes an ambient inlet port 151, a compressor-outlet inlet port 152, a heat-exchanger hot-stream outlet inlet port 153, a compressor-inlet outlet port 161, a heat-exchanger cold-stream inlet outlet port 162 and an exhaust outlet port 163, the six ports being in fluid communication one with the other through fluid conduits 120.
  • Valve 103 further comprises a bypass conduit providing fluid communication between heat-exchanger hot- stream outlet inlet port and compressor-inlet outlet port.
  • Valve 103 further includes three valve members, 171, 181 and 191.
  • First valve member 171 is movable inside valve body 110 having at least two positions: a first position as depicted in Figure 8 A in contact with a first valve seat 172 in valve body 110, and a second position, depicted in Figure 8B, in contact with a second valve seat 173 in valve body 110.
  • first valve member 171 in said first position blocks fluid communication between ambient inlet port 151 and heat-exchanger cold-stream inlet outlet port 162 and in the second position (Figure 8B) blocks fluid communication between ambient inlet port 151 and compressor inlet outlet port 161.
  • Second valve member 181 is movable inside valve body 110 having at least two positions: a first position, depicted in Figure 8 A, in contact with a third valve seat 182 in valve body 110, and a second position, depicted in Figure 8B, in contact with a fourth valve seat 183 in valve body 110.
  • first position depicted in Figure 8A
  • second valve member 181 blocks fluid communication between heat-exchanger hot-stream outlet inlet port 153, and heat-exchanger cold-stream inlet outlet port 162
  • in the second position (Figure 8B) blocks fluid communication between compressor-outlet inlet port 152 and heat-exchanger cold-stream inlet outlet port 162.
  • Third valve member 191 is movable inside valve body 110 having at least two positions: a first position, depicted in Figure 8 A, in contact with a fifth valve seat 192 in valve body 110, and a second position, depicted in Figure 8B, in contact with a sixth valve seat 193 in valve body 110.
  • first position depicted in Figure 8A
  • second position depicted in Figure 8B
  • third valve member 191 blocks fluid communication between heat-exchanger hot-stream outlet inlet port 153 and exhaust outlet port 163.
  • valve members 171, 181 and 191 are configured for cooperative movement.
  • one or more valve members 171, 181 and 191 are independently operable.
  • Gas-turbine comprising 6-port valve 103
  • Figures 9 depict an exemplary embodiment of a gas-turbine 13 comprising an embodiment of a valve 103, operable according to a Brayton cycle (Figure 9A) and according to an inverse Brayton cycle (Figure 9B)
  • Valve 103 is configured to switch gas-turbine 13 between a high-pressure operation mode depicted in Figure 9 A, and a low-pressure operation mode depicted in Figure 9B.
  • valve members 171, 181 and 191 of valve 103 are in a respective first position.
  • Ambient air is drawn through ambient inlet port 151 and compressor-inlet outlet port 161 of valve 103 into compressor 20, and pass through compressor-outlet inlet port 152 and heat-exchanger cold- stream inlet outlet port 162 of valve 103 into cold- stream conduit 54 of heat-exchanger 52 to combust in combustor 26.
  • the combusted gases expand through turbine 22 and exit through hot-stream conduit 56 of heat-exchanger 52 and through heat- exchanger hot-stream outlet inlet port 153, to be discharged through exhaust outlet port 163 to the surroundings.
  • valve members 171, 181 and 191 of valve 103 are in a respective second position.
  • Ambient air is drawn through ambient inlet port 151 and heat-exchanger cold-stream inlet outlet port 162 of valve 103 into cold-stream conduit 54 of heat-exchanger 52 to combust in combustor 26.
  • the combusted gases enter turbine 22 and exit turbine 22 into hot-stream conduit 56 of heat-exchanger 52.
  • hot-stream conduit 56 Exiting hot-stream conduit 56, the combusted gases are drawn through heat-exchanger hot-stream outlet inlet port 153, through the bypass conduit to compressor-inlet outlet port 161 of valve 103 into compressor 20.
  • a gas-turbine such as 13 is switched between a high-pressure operation mode and a low-pressure operation mode as is described above, using a six -port valve, having three inlet ports designated “X" (ambient inlet port 151), “Y” (compressor-outlet inlet port 152) and “Z” (heat-exchanger hot-stream outlet inlet port 153), and three outlet ports designated “x” (compressor- inlet outlet port 161), “y” (heat-exchanger cold-stream inlet outlet port 162) and “z” (exhaust outlet port 163).
  • the valve In a first configuration, the valve provides fluid communication exclusively between inlet port “X” and outlet port “x”, between inlet port “Y” and outlet port “y” and between inlet port “Z” and outlet port “z”. In a second configuration, the valve provides fluid communication exclusively between inlet port “X” and outlet port “y”, between inlet port “Y” and outlet port “z” and between inlet port “Z” and outlet port “x”. Providing flow communication exclusively between the specified pairs of inlet and outlet ports means that only fluid communication which is explicitly described between the specified ports is provided, and there is no fluid communication between the ports which is not explicitly described.
  • a valve is configured and operable to be in at least one intermediate configuration, in addition to the high-pressure (Brayton cycle) configuration " 1 " and low-pressure (inverse Brayton cycle) configuration "2" discussed above, for example in Figures 8A and 8B.
  • Such an intermediate configuration allows a gas-turbine to work in a pressure mode intermediate between the high and low-pressure operation modes.
  • Figure 10 depicts an embodiment of a valve 103 in an exemplary intermediate configuration, valve members 171, 181 and 191 being in an intermediate position, between the respective first position and second position.
  • fluid from a given inlet port is directed to flow to two outlet ports. Specifically, a portion of the fluid entering valve 103 from ambient inlet port 151 is directed to compressor-inlet outlet port 161, and another portion to heat-exchanger cold-stream inlet outlet port 162. Similarly, a portion of the fluid entering through compressor-outlet inlet port 152 is directed to heat- exchanger cold- stream inlet outlet port 162 and another portion is directed to exhaust outlet port 163. A portion of the fluid entering valve 103 from heat-exchanger hot-stream outlet inlet port 153 is directed to exhaust outlet port 163 and another portion is directed to compressor-inlet outlet port 161.
  • a mixing region 126 within fluid conduits 120 is configured to function as jet pump ejector.
  • such configuration includes fashioning at least one of valve members 171, 181 as an airfoil having a pre-defined aerodynamic profile.
  • FIG 11 depicts an exemplary embodiment of a gas-turbine 13, configured with a valve 103 and operable in an intermediate pressure operation mode in addition to a high- pressure operation mode (configuration "1", Figure 8A) and a low-pressure operation mode (configuration "2", Figure 8B).
  • compressors 171, 181 and 191 are positioned as depicted in Figure 10
  • compressors 171, 181 and 191 are positioned as depicted in Figure 10.
  • 10 20 generates a low-pressure region around compressor-inlet outlet port 161 of valve 103, so a portion of ambient air is drawn from ambient inlet port 151 into compressor-inlet outlet port 161. Additionally, a portion of the gas coming from heat-exchanger 52 into heat-exchanger hot-stream outlet inlet port 153 is drawn into compressor 20 through compressor-inlet outlet port 161.
  • Compressed fluid coming from compressor 20 flows into compressor-outlet inlet port
  • valve member 152 at high-pressure and is directed to both heat-exchanger cold-stream inlet outlet port 162 and to exhaust outlet port 163, the exact ratio dependent, inter alia, on the position of valve member 181.
  • valve members 171, 181 and 191 when one or more of valve members 171, 181 and 191 are arranged.
  • a gas-turbine 13 is operable in a mode where the pressure is between the highest and lowest pressures and consequently the power output is between the highest and lowest power outputs.
  • the thermal efficiency of the gas-turbine is relatively high (see curve 414 in Figure 4).
  • an intermediate pressure operation mode of a gas-turbine such as 13 is obtained by positioning only one valve member 171, 181 or 191 in a respective intermediate position while the other two valve members are positioned in either a first or second position.
  • an intermediate pressure operation mode of gas- turbine 13 is obtained by positioning two valve members in a respective intermediate
  • valve 30 position, while the remaining valve member is positioned in either a first or a second position.
  • a gas-turbine such as gas-turbine 13 comprising a valve with three valve members as described herein such as valve 103, is switched to an intermediate pressure operation mode by positioning a first valve member 171 and a second valve member 181 in an intermediate position, substantially as is described above, and positioning a third valve member 191 in a first position or in a second position.
  • a gas-turbine such as gas-turbine 10 of Figures 3 or gas-turbine 11 of Figures 5, comprising a valve with two valve members as described herein, such as valve 100, is switched to an intermediate pressure operation mode by positioning a first valve member 171 and a second valve member 181 of the valve in an intermediate position.
  • a gas-turbine such as gas-turbine 12 of Figures 7 is switched to an intermediate pressure operation mode by positioning a first valve member 171 and a second valve member 181 of a valve such as valve 102 in an intermediate position.
  • a mixing region analogue to mixing region 126 of valve 103 is formed in the respective two-valve member valve (e.g., 100 or 102) to function as jet pump ejector.
  • a continuity of intermediate pressure operation modes is obtained by positioning valve members 171 and 181 of respective valves such as 100 and 102 in a continuity of positions.
  • the position of at least one valve member is not continuously variable. That is to say, one or a series of intermediate pressure operation modes of gas- turbine 13 is obtained by maintaining at least one valve member in a fixed position while varying the position of the remaining valve members.
  • valve members 171, 181 and 191 are moveable between two endpoints, and may be maintained at a specific intermediate position between the endpoints.
  • valve 103 has at least three configurations, and gas-turbine 13 comprising valve 103 may be efficiently operated in at least three different pressure operation modes.
  • curve 410 corresponds to a single spool gas-turbine operating in the low-pressure operation mode (as is described in Figure 9B)
  • curve 412 corresponds to gas-turbine 13 operating in a high-pressure operation mode (as is described in Figure 9A)
  • curve 414 corresponds to gas-turbine 13 operating in one exemplary intermediate pressure operation mode as described above in Figure 11, where mixing region 126 is configured as a jet pump ejector.
  • a valving system allows high-pressure operation mode and/or low-pressure operation mode of a gas-turbine (including, inter alia, a combustor and a heat-exchanger) at a continuously varying power output at relative high efficiency.
  • a gas-turbine including, inter alia, a combustor and a heat-exchanger
  • Such a valving system operates by reducing the mass flow of fluid to the combustor through the heat-exchanger.
  • mass flow reduction is similar to the achieved by inlet throttling, for example with the use of variable inlet guide vanes.
  • variable inlet guide vanes are often used with large gas-turbines. Such guide
  • the guide vanes are unsuitable for use with small turbines due to high expense and technical complexity at small sized. Further, as there is a need for matching between the whirl caused by the guide vanes and the compressor blades, the guide vanes can be varied only by about 15% which allows a change of about 20% in power output at reasonable efficiencies.
  • Figures 13 show an embodiment of a valve 104, suitable for use with a gas-turbine
  • valve member 181 is configured to have a continuity of positions when in the first position in contact with valve seat 182, allowing a gas-turbine including valve 104 and operating in a high-pressure operation mode to operate in a continuity of output power levels.
  • valve member 181 is relatively thick and valve seat 182 appropriately configured so that valve member 181 has a range of
  • valve seat 182 thereby blocking fluid communication through valve seat 182.
  • the varying bulk of valve member 181 located in the fluid path between compressor-outlet inlet port 152 and heat-exchanger cold-stream inlet outlet port 162 allows the size of the fluid path to be controllably varied.
  • Figures 13A and 13B show two exemplary such positions where valve member 181 is in the first position 1 in contact with valve seat 182, but the exact position of valve member 181 varies the size of a fluid path 127 inside valve 104, between compressor-outlet inlet port 152 and heat-exchanger cold-stream inlet outlet port 162, thereby varying the gas-turbine output power level.
  • valve member 181 is in position as depicted in Figure
  • fluid path 127 is wide, allowing for a high flow rate of fluid from compressor-outlet inlet port 152 to heat-exchanger cold-stream inlet outlet port 162 so that the gas-turbine generates a relatively high output power level; and when valve member 181 is in a position as depicted in Figure 13B, fluid path 127 is narrow, allowing for a low flow-rate of fluid, so that the gas-turbine generates a relatively low output power level.
  • valve 104 allows a gas-turbine to operate in a high-pressure operation mode in a continuity of configurations as described above, since valve member 181 is continuously in contact with valve seat 182, in the described continuity of positions, substantially blocking flow of fluid from compressor-outlet inlet port 152 to exhaust outlet port 163. Further, when valve 104 is in a high-pressure mode configuration as described above, valve member 171 is maintained in contact with valve seat 172, substantially blocking flow from ambient inlet port 151 to heat-exchanger cold-stream inlet outlet port 162.
  • valve 104 further allows an associated gas-turbine to operate in a low-pressure operation mode when valve members 171 and 181 are in a second position (not shown). Specifically, valve 104 is in a low-pressure mode configuration when valve members 171 and 181 are in contact with valve seats 173 and 183, respectively.
  • valve 104 is operable to switch a gas-turbine between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, and in addition to varying the gas-turbine output power level in the high-pressure operation mode.
  • multiport valve 104 is operable to switch the gas-turbine between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, and in addition to varying the gas-turbine output power level in the high-pressure operation mode.
  • Figures 14A and 14B depict an embodiment of a valve 105, suitable for use with a gas-turbine, schematically depicted in side cross-section.
  • valve member 171 is configured to have a continuity of positions when in the second position in contact with valve seat 173, allowing a gas-turbine including valve 105 and operating in a low-pressure operation mode, to operate in a continuity of output power levels.
  • valve member 171 is relatively thick and valve seat 173 is appropriately configured so that valve member 171 has a range of motion defining a continuity of positions in continuous contact with valve seat 173 thereby blocking fluid communication through valve seat 173.
  • the varying bulk of valve member 171 located in the fluid path between ambient inlet port 151 and heat-exchanger cold-stream inlet outlet port 162 allows the size of the fluid path to be controllably varied.
  • Figures 14A and 14B depict two exemplary such positions where valve member 171 is in the second position in contact with valve seat 173, but the exact position of valve member 171 effects the gas-turbine output power level by varying the size of path 128 inside valve 105, between ambient inlet port 151 and heat-exchanger cold-stream inlet outlet port 162.
  • valve member 171 when valve member 171 is in position as depicted in Figure 14A, fluid path 128 is wide, allowing for a high flow rate of air from ambient inlet port 151 to heat- exchanger cold-stream inlet outlet port 162, thereby generating a high output power level; and when valve member 171 is in position as depicted in Figure 14B, fluid path 128 is narrow allowing for a low flow rate of fluid so that the gas-turbine generates a low output power level.
  • valve 105 allows a gas-turbine to operate in a low-pressure operation mode in a continuity of configurations as described above, since valve member 171 5 is continuously in contact with valve seat 173 in the described continuity of positions, substantially blocking flow of fluid from ambient inlet port 151 to compressor-inlet outlet port 161. Further, when valve 105 is in such a low-pressure mode configuration as described above, valve member 181 is maintained in contact with valve seat 183, substantially blocking flow from compressor-outlet inlet port 152 to heat-exchanger cold-stream inlet outlet port
  • valve 105 further allows an associated gas-turbine to operate in a high-pressure operation mode when valve members 171 and 181 are in a first position (not shown). Specifically, valve 105 is in a high-pressure mode configuration when valve members 171 and 181 are in contact with valve seats 172 and 182,
  • valve 105 is operable to switch a gas-turbine between a high-pressure operation mode according to a
  • a valve includes two separate valve members that allow both
  • valves 106, 107 and 108 are schematically depicted. Valves 106, 107 and 108 are suitable for use with a gas-turbine and configured for switching a gas-turbine comprising valves 106, 107 or 108 between a high-pressure and a
  • Valves 106, 107 and 108 are also configured for continuously varying output power level of an associated gas-turbine by allowing a continuous varying of the size of the fluid path to the heat-exchanger.
  • valve 106 depicted in Figure 15 A a movable valve member 281 is rotatably moveable around valve member axis 184, sharing an axis of rotation with valve member 181.
  • valve member 281 is moveable through a continuity of positions allowing variation of the size of fluid path 127, thereby varying the output power level of the associated gas-turbine.
  • valve 106 is operable to switch a gas-turbine between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, and in addition to varying the gas-turbine output power level in the high-pressure operation mode.
  • valve member 271 is movable around valve member axis 174 thereby operable to vary the size of fluid path 128 from ambient inlet port 151 to the heat-exchanger (not shown) through heat-exchanger cold-stream inlet outlet port
  • valve 107 is operable to switch a gas-turbine between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, and in addition to varying the gas-turbine output
  • valve 108 depicted in Fig 15C two valve members, 171 and 271, both movable around first valve member axis 174, and two valve members 181 and 281, both movable around second valve member axis 184, allow the size of fluid paths 127 and 128, respectively, to be continuously varied while valve 108 is set in high-pressure configuration
  • valve 108 is operable to switch a gas-turbine between a high-pressure operation mode according to a Brayton cycle and a low-pressure operation mode according to an inverse Brayton cycle, and in addition to varying the gas-turbine output power level in the low-pressure operation mode and in the high-pressure operation mode.
  • a similar variation in the size of the fluid path is
  • Curve 412 corresponds to a gas-turbine operating in the high-pressure operation mode, for example with a valve 100 of Figures 2A, while curve 416 corresponds to
  • valve 410 corresponds to a gas-turbine operating in the low-pressure operation mode, for example with a valve 100 of Figures 2B
  • curve 418 corresponds to the gas- turbine operating in low-pressure operation mode with a valve of Figures 14A, 14B 15B or 15C.
  • the valve members are substantially plates configured to rotatably move between the different positions around a single axis close to or at an edge of the valve member.
  • valve members used include suitably-configured butterfly valves (especially tricentric butterfly valves), ball valves or rotary valves.
  • Gas-turbines using valves as described herein may be of any desired power capacity. That said, in some embodiments, a gas-turbine is configured for producing up to about 100 kW. In some embodiments, a gas-turbine is configured for producing from about 14 kW to about 40 kW of power. In some embodiments, a gas-turbine is configured for producing from about 7 kW to about 36 kW of power. Such low powers are useful, for example, for powering a small motor vehicle, such as a light truck or an automobile.
  • Reduced NOx emission inverse-Brayton cycle gas-turbine Aspects of the invention relate to gas-turbines operating in a low-pressure operation mode according to an inverse Brayton cycle that have reduced NOx emissions. Due to poor mixing and vaporization at low power operation which create local high temperature zones, gas-turbine NOx emissions are higher under partial load.
  • inlet air is mixed with a portion of exhaust and is directed into the combustor, thereby decreasing the oxygen content of the combustible mixture in the combustor, and as a result, reducing the amount of NOx emissions.
  • a method of operating a gas-turbine according to an inverse Brayton cycle comprising: a) providing a conduit allowing fluid communication between a compressor of the gas-turbine and a cold-stream inlet of a heat-exchanger of the gas-turbine; and b) during inverse Brayton cycle operation of the gas-turbine, directing fluid from the compressor to the heat-exchanger cold-stream inlet through the conduit so that a portion of the fluid entering the heat-exchanger cold-stream inlet is from the compressor.
  • the method further comprises: adjusting a size of the conduit so as to control an amount of fluid entering the cold-stream inlet from the compressor.
  • a gas-turbine comprising, when operating according to an inverse Brayton cycle, a) an air inlet configured to direct fluid into a cold-stream conduit of a heat-exchanger through a cold- stream inlet; b) conduits to direct fluid from the cold-stream conduit to a combustor, from the combustor to a turbine, from the turbine to a hot- stream conduit of the heat-exchanger, from the hot-stream conduit to a compressor, and from the compressor to an exhaust outlet; and c) a conduit allowing passage of fluid from the compressor into the cold-stream inlet of the heat-exchanger.
  • the gas-turbine is configured to operate only according to an inverse Brayton cycle.
  • the gas-turbine is configured to optionally operate according to a Brayton cycle, for example as described herein. In some such embodiments, the gas-turbine is configured so that during operation according to a Brayton cycle, the conduit is substantially blocked preventing passage of fluid between the compressor and the cold- stream inlet.
  • the conduit allowing passage of fluid from the compressor into the cold-stream inlet is of fixed size. In some embodiments, the size of the conduit allowing passage of fluid from the compressor into the cold-stream inlet is adjustable, for example allowing varying an amount of fluid passing from the compressor into the cold-stream inlet.
  • the conduit allowing passage of fluid from the compressor into the cold- stream inlet is configured so that during operation according to an inverse Brayton cycle between about 30% and about 70% (in some embodiments, between about 40% and about 60%, in some embodiments 45% and about 55%) by mass of the fluid entering the heat-exchanger cold-stream inlet is from the compressor.
  • the conduit allowing passage of fluid from the compressor into the cold- stream inlet of the heat-exchanger is passive, that is to say, occurs due to the pressure differential between the two regions without investment of any additional work.
  • the conduit is active, that is to say, comprises a component such as a pump that performs work to direct fluid from the compressor to the cold-stream inlet of the heat-exchanger.
  • Figure 16 depicts an exemplary embodiment of a gas-turbine 19 including a valve 109 suitable for use with a gas-turbine and useful for reducing the amount of NOx emissions of the gas-turbine in low-pressure operation mode.
  • valve 109 comprises five ports and two valve members in a configuration similar to valve 5 100 depicted in Figures 2.
  • valve 109 further comprises a permeable section 140 of valve body 110 between regions 121 and 122 of fluid conduits 120, allowing passage of fluid from region 121 to region 122.
  • region 121 is up-stream from valve member 181, between valve member 181 and exhaust outlet port 163 while region 122 is up-stream
  • Permeable section 140 is unidirectional, only allowing passage of fluid from region 121 to region 122 if the pressure in region 121 is higher than the pressure in region 122 (e.g., during inverse Brayton cycle operation of gas-turbine 19), but blocking passage of fluid from region 122 into region 121 (e.g., during Brayton cycle operation of gas-turbine
  • gas-turbine 19 may be set in configurations analagous to the configurations depicted in for gas-turbine 10 in Figures 3A and 3B.
  • gas-turbine 19 is depicted in a configuration analogous to configuration "2" ( Figure 2B), consequently operating in a low-pressure operation mode according to an
  • the pressure in region 121 is higher than the pressure in region 122 so a portion of the exhaust gas passes from region 121 through permeable section 140 into region 122.
  • the portion of exhaust gas that passes through permeable section 140 to region 122 mixes with the ambient air coming into gas-turbine 19, reducing oxygen content in the fluid entering the combustor and consequently reducing NO'x content in the combusted
  • Some such embodiments are superficially similar to reversed circulation methods implemented in internal combustion engines, where a significant amount of power is invested in recompressing exhaust into a high-pressure combustion chamber, reducing thermal efficiency but reducing NOx emissions.
  • a significant amount of power is invested in recompressing exhaust into a high-pressure combustion chamber, reducing thermal efficiency but reducing NOx emissions.
  • some embodiments of the invention are superficially similar to reversed circulation methods implemented in internal combustion engines, where a significant amount of power is invested in recompressing exhaust into a high-pressure combustion chamber, reducing thermal efficiency but reducing NOx emissions.
  • FIG. 30 depicts an exemplary embodiment of permeable section 140 in valve 109, including a check valve 141, operable as a unidirectional valve (e.g., a reed valve) and configured to allow fluid passage from region 121 to region 122 of fluid conduits 120 of valve 109, and to block passage of fluid in the opposite direction from region 122 to region
  • a check valve 141 operable as a unidirectional valve (e.g., a reed valve) and configured to allow fluid passage from region 121 to region 122 of fluid conduits 120 of valve 109, and to block passage of fluid in the opposite direction from region 122 to region
  • Figure 17B depicts another exemplary embodiment of permeable section 140 of valve 109 integrated in valve member 181.
  • Valve member 181 includes a unidirectional valve 186 (e.g., a reed valve) allowing fluid passage from region 121 to region 122 and to block fluid passage from region 121 to
  • a unidirectional valve 186 e.g., a reed valve
  • valve member 181 comprises conduit 185 providing fluid communication from a face 188 to a face 189 of valve member 181.
  • Unidirectional valve 186 is disposed inside conduit 185.
  • valve 186 is closed, sealing conduit 185.
  • fluid e.g., exhaust gas
  • compressor-outlet inlet port 152 to pass from region 121 to region 122.
  • the size of holes 185 determines the amount of exhaust gas mixed and therefore the oxygen content of the gas entering a combustor 26.
  • the amount of exhaust gas mixed can be controlled, for example, by changing the number or size of holes.
  • permeable section 140 are not limited to the 20 examples described above and permeable section 140 can comprise holes, slits, pores and the like, allowing passage of fluid from region 121 to region 122 of fluid conduits 120 valve 109.
  • the combustor of a gas-turbine is part of or associated with a valve as described herein that allows operation of a gas-turbine in both high and low-pressure modes.
  • any of the valves of the invention described herein can be utilized to reduce NOx emission by permitting a portion of the oxygen-depleted exhaust gas to mix with incoming ambient air in low-pressure operation mode of a gas- 30 turbine, by positioning valve member 181 close to, but not in contact with, valve seat 183, when operating the gas-turbine in low-pressure operation mode.
  • valve member 181 allows for fluid passage between compressor-outlet inlet port 152 and heat-exchanger cold-stream inlet outlet port 162 in low-pressure operation mode, exhaust gas is forced into the flow of incoming ambient air, where the amount of such exhaust passage is controlled by the exact positioning of valve member 181 with respect to valve seat 183.
  • a gas-turbine configured for multipressure operation e.g., such as described in US patents 6,526,757 and 6,606,864, includes an additional valve (or an existing valve is modified) that allows passage of exhaust from the compressor outlet to mix with air entering the combustor during low-pressure (inverse Brayton) operation, thereby reducing NOx emissions.
  • a gas-turbine configured for multipressure operation includes an additional valve (not associated with the valve that allows switching between high and low-pressure operation) defining a conduit that allows passage of exhaust from the compressor outlet to mix with air entering the combustor during low-pressure (inverse Brayton) operation, thereby reducing NOx emissions.
  • an extra valve has two configurations: closed (blocking passage of exhaust) and open (allowing passage of exhaust) defining a fixed conduit size.
  • the valve is adjustable, allowing the size of the conduit to be adjusted to allow varying the amount of exhaust passing to mix with the air entering the combustor.
  • a gas-turbine configured for low-pressure (inverse Brayton cycle) operation includes a valve defining a conduit that allows passage of exhaust from the compressor outlet to mix with air entering the combustor, thereby reducing NOx emissions.
  • a valve has two configurations: closed (blocking passage of exhaust) and open (allowing passage of exhaust).
  • the valve is adjustable, allowing variation of the amount of exhaust passing to mix with the air entering the combustor.
  • oxygen-depleted exhaust is mixed with ambient air prior to entering the heat-exchanger of the gas-turbine.
  • the exhaust is mixed with the air after exiting the heat-exchanger cold-stream outlet and prior to entering the combustor.
  • such embodiments are usually considered less advantageous as lowering combustor inlet temperature reduces thermal efficiency of the gas-turbine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne des vannes pouvant être utilisées avec une turbine à gaz, des turbines à gaz, et des méthodes de fonctionnement d'une turbine à gaz. L'invention concerne aussi des véhicules motorisés tels que des automobiles comportant une turbine à gaz.
PCT/IB2009/055154 2008-11-20 2009-11-18 Vannes pour turbines à gaz et turbines à gaz à pression multiple, et turbines à gaz les accompagnant WO2010058356A2 (fr)

Priority Applications (2)

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US13/127,726 US20110262269A1 (en) 2008-11-20 2009-11-18 Valves for gas-turbines and multipressure gas-turbines, and gas-turbines therewith
IL212740A IL212740A0 (en) 2008-11-20 2011-05-05 Valves for gas-turbines and multipressure gas-turbines, and gas-turbines therewith

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US11639408P 2008-11-20 2008-11-20
US61/116,394 2008-11-20

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