Gas turbine exhaust gas treatment system and method

Abstract

A system and method for treating turbine exhaust gases includes an exhaust gas discharge structure, a catalytic exhaust gas treatment device, at least two heat exchangers, and a district heating system. The catalytic exhaust gas treatment device is at least partially located within the exhaust gas discharge structure. A first heat exchanger is located at least partially within the exhaust gas discharge structure and upstream of the catalytic exhaust gas treatment device, and removes heat from the exhaust gas by transferring heat to a working fluid. A second heat exchanger is located at least partially within the exhaust gas discharge structure and downstream of the catalytic exhaust gas treatment device, and removes heat from the exhaust gas that has passed through the device by transferring heat to a working fluid. A pump drives the working fluid between the first heat exchanger, the district heating system, and the second heat exchanger.

Description

Technical Field

[0001] [Cross - Reference to Related Applications] This application is a continuation - in - part of U.S. Patent Application No. 17 / 487,887, filed on September 28, 2021, which claims the priority of U.S. Provisional Patent Application No. 63 / 084,290, filed on September 28, 2020, and both of these applications are incorporated herein by reference in their entirety.

[0002] [Statement Regarding Federally Sponsored Research or Development] Not applicable

Background Art

[0003] Exhaust gases resulting from various processes and / or the combustion of various fuels generally contain one or more harmful substances such as carbon monoxide and / or nitrogen oxides. For example, the combustion of natural gas or other fossil fuels in a power plant produces a high - temperature exhaust gas stream containing carbon monoxide, nitrogen oxides, and / or other exhaust gases. Similarly, in the manufacture of chemical products, hydrocarbon cracking, steel manufacturing, and other processes, high - temperature exhaust gas streams containing harmful substances are produced. Usually, the exhaust gas stream is treated with one or more catalysts (e.g., a catalyst bed) to reduce carbon monoxide, nitrogen dioxide, and / or other substances. For example, the catalyst can convert nitrogen dioxide and / or carbon monoxide into one or more of water, diatomic nitrogen, carbon dioxide, and / or other less harmful compounds. To treat nitrogen oxides using a catalyst, generally, reactants such as anhydrous ammonia or an aqueous solution of ammonia are introduced upstream of a selective catalytic reaction (SCR) catalyst.

[0004] Each catalyst and / or reactant has an operating temperature range that optimizes the desired reaction for reducing exhaust gas components. Furthermore, if the exhaust gas temperature exceeds the mechanical / chemical design limits of the catalyst or housing, the catalyst or reactant itself and / or the housing containing the catalyst and / or reactant (e.g., SCR) or material may be damaged. Therefore, it may be advantageous to control the temperature of the exhaust gas before it passes through the catalyst material in order to keep it within a temperature range that can optimally treat specific components in the exhaust gas.

[0005] Many conventional exhaust gas cooling and exhaust gas treatment systems suffer from problems such as poor performance, lifespan, and efficiency due to the limitations of the cooling system and the requirements of the exhaust gas treatment system mentioned above. [Overview of the Initiative]

[0006] The cooling system described herein offers several advantages over typical gas turbine exhaust gas treatment systems. By cooling the gas turbine exhaust gas using the disclosed system, the temperature of the turbine exhaust gas can be controlled to be within a range suitable for treatment by one or more catalysts (e.g., catalytic treatment of carbon monoxide, selective catalytic reduction (SCR), treatment of nitrogen oxides, etc.). Cooling the turbine exhaust gas eliminates the need for equipment typically used in treatment, such as forced draft fans, induced draft fans, and direct water injection. Exhaust fans are generally energy inefficient, and water injection incurs costs associated with a certain level of chemical treatment, as well as the potential for unwanted aerosol formation, premature corrosion of components, and degradation of exhaust catalyst performance. Pretreatment to lower the temperature of turbine exhaust gas using the type of system described herein is generally more energy efficient than using forced draft fans or induced draft fans, because the energy consumption of liquid circulation (e.g., using pumps) is even lower than the power consumption of moving air (e.g., using blowers, fans, compressors, etc.). The disclosed system also eliminates the need for direct water injection into the exhaust gas, thereby eliminating the potential adverse effects associated with water injection as described above. By using a working fluid as described herein to cool the turbine exhaust gas before catalytic treatment, it becomes possible to more precisely control the temperature of the turbine exhaust gas at one or more locations. For example, the working fluid can be used to control the temperature of the turbine exhaust gas within a first temperature range before carbon monoxide treatment at a first location, and within a second different temperature range before nitrogen oxide treatment at a second location. Such controllability enables optimal temperatures for different catalytic reactions.

[0007] Therefore, the controllability provided by using a working fluid to cool the turbine exhaust gas allows for a reduction in energy consumption compared to the use of other techniques (e.g., forced induction fans), and the controllable cooling use by the working fluid allows for the optimization of the catalytic reaction used to treat the turbine exhaust gas. The advantages of the turbine exhaust gas treatment systems currently described herein are these advantages and / or other advantages. The use of a working fluid to cool the turbine exhaust gas offers advantages in that the heat of the turbine exhaust gas is removed and captured by the working fluid. The energy removed from the turbine exhaust gas can be recovered directly by mechanical connection to a device such as a pump (e.g., a pump driven by the working fluid), indirectly by expansion through a suitable device connected to a generator (e.g., a working fluid driving an energy recovery turbine coupled to a generator), or the heat recovered by the working fluid may be used to heat another process fluid (e.g., using a heat exchanger to transfer heat from the working fluid to another process fluid).

[0008] In further embodiments of the present disclosure, in the gas turbine exhaust gas treatment system described herein, a first heat exchanger is located on the exhaust gas flow path from the gas turbine and before a catalytic converter such as a selective catalytic reducer (SCR). The first heat exchanger is operable to control the temperature of the turbine exhaust gas and cools the turbine exhaust gas temperature within a range for treatment by one or more catalysts in the SCR. The working fluid circulating through the first heat exchanger cools the turbine exhaust gas, allowing for more precise control of the turbine exhaust gas temperature before it is catalytically treated as it passes through the SCR.

[0009] The working fluid, heated by turbine exhaust gas passing through the first heat exchanger, is a system that distributes heat from the first heat exchanger to the working fluid, which can be transmitted, for example, to a general-purpose district heating or heating network.

[0010] The working fluid from the district heating system is pumped to a second heat exchanger located in the flow path of the turbine exhaust gas discharged from the SCR. The second heat exchanger recovers some of the remaining final heat from the turbine exhaust gas discharged from the SCR, further cools the exhaust gas, and then returns the working fluid to the first heat exchanger.

[0011] Other advantages and features of the cooling system of this disclosure will become apparent from the following disclosures. [Brief explanation of the drawing]

[0012] [Figure 1] An enlarged view of the mass inventory management system is shown in the lower left section. This is a schematic diagram of a gas turbine exhaust gas treatment system, including a catalyst treatment device and a carbon dioxide cooling system for cooling turbine exhaust gas. [Figure 2] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 1, in which thermal oil is used as the working fluid. [Figure 3] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 1, in which water is used as the working fluid. [Figure 4] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 1, which includes a heat exchanger located between the pump and the expansion nozzle. [Figure 5] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 4, in which hot oil is used as the working fluid. [Figure 6] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 4, in which water is used as the working fluid. [Figure 7] This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 1, in which split cooling is used to cool the turbine exhaust gas before the first catalytic converter and to further cool the turbine exhaust gas after the first catalytic converter and before the second catalytic converter. [Figure 8]This is a schematic diagram of an alternative embodiment of the turbine exhaust gas treatment system shown in Figure 7, which includes a heat exchanger located between the pump and the expansion nozzle. [Figure 9A] This is a schematic diagram of an alternative embodiment of a turbine exhaust gas treatment system having an independent cooling loop. [Figure 9B] This is a schematic diagram of an alternative embodiment of a turbine exhaust gas treatment system having an independent cooling loop and a common mass inventory system. [Figure 9C] This is a schematic diagram of an alternative embodiment of a turbine exhaust gas treatment system having three or more independent cooling loops. [Figure 10] This is a schematic diagram of another embodiment of a turbine exhaust gas treatment system, including a district heating system located downstream of the first heat exchanger and a second heat exchanger located downstream of the district heating system. [Figure 11] Figure 10 shows the system with a primary heat exchanger added to the district heating loop along with the district heating network.

[0013] Corresponding reference letters and symbols indicate the corresponding parts throughout multiple drawings of the drawing. [Modes for carrying out the invention]

[0014] The following detailed description, which is illustrative and not limiting, describes the disclosed gas turbine exhaust gas treatment system and related methods. This description will enable a person skilled in the art to manufacture and use the turbine exhaust gas treatment system. This detailed description includes what is considered to be the best mode for realizing the currently claimed turbine exhaust gas treatment system and related methods, and describes various embodiments, adaptations, modifications, alternatives, and applications of the turbine exhaust gas treatment system. Furthermore, it should be understood that the disclosed turbine exhaust gas treatment system is not limited to the structural details and arrangement of components shown in the following description or drawings. This disclosure has other embodiments and can be implemented or carried out in various ways. It should also be understood that the expressions and terms used herein are for illustrative purposes only and should not be construed as limiting.

[0015] Referring to Figures 1-8, a turbine exhaust gas treatment system uses a working fluid to treat turbine exhaust gas. While exhaust gas treatment systems can be considered for any process requiring emission reduction, one of its applications relates to simple cycle gas turbine equipment. However, exhaust gas resulting from combustion in simple cycle gas turbine equipment is only one example of exhaust gas. As used herein, the terms “turbine exhaust gas” and “process turbine exhaust gas” should be understood as gas from or involved in any process such as combustion (e.g., related to power production), chemical manufacturing, oil cracking, steelmaking, or other processes that use or produce turbine exhaust gas as a byproduct. Referring again to simple cycle turbine equipment, such equipment uses only a single thermodynamic cycle (e.g., a Brayton cycle) so that high-temperature exhaust gas is discharged directly from the gas turbine into the atmosphere. When emission reduction is required in simple cycle power plants, large forced-draft fans are often used to mix a large amount of ambient air with the gas turbine exhaust gas to achieve the required catalyst operating temperature. Such fans have high procurement costs and generally high operating costs (e.g., high power consumption).

[0016] The exhaust gas treatment system cools the high-temperature turbine exhaust gas within an optimal temperature range to promote the desired chemical reactions that occur in processing the exhaust gas components, while protecting against mechanical damage due to overheating of the catalyst system. This is achieved without using large forced draft fans or induced draft fans. There is no need to add additional air or other gases to the turbine exhaust gas for the purpose of cooling the turbine exhaust gas before it is processed in one or more catalyst processes. In some embodiments, additional air or other gases are indirectly added to the turbine exhaust gas, but this is not for cooling the turbine exhaust gas, but rather for facilitating the treatment of the turbine exhaust gas. For example, ammonia may be used when treating nitrogen oxides in the turbine exhaust gas stream. In this case, ammonia may be in an aqueous solution, whereby ammonia is mixed with air in a mixing tank, and the water-soluble ammonia is flashed in the mixing tank and diluted with air before being injected into the turbine exhaust gas.

[0017] The heat transfer coil upstream of the catalyst system is used in the turbine exhaust gas treatment to reduce the high gas temperature to the target range for safer and more efficient operation of the catalyst. The heat recovered from the high-temperature turbine exhaust gas is dissipated to the surroundings through air-cooled and / or water-cooled heat exchangers. Alternatively, the removed heat may be used to heat an external process stream (e.g., using a heat exchanger), recovered by mechanical application (e.g., driving a pump with the removed heat), or recovered by direct expansion of a heat operating fluid using a device connected to an electric generator (e.g., the heat fluid expands to drive a turbine, and that turbine drives an electric generator). By placing additional heat exchange coils within the gas stream, it is possible to achieve different turbine exhaust gas temperatures at different points within the turbine exhaust gas stream.

[0018] Such temperature control enables improved treatment of turbine exhaust gas. For example, generally, the target optimal temperature range of a catalyst for treating carbon monoxide does not overlap with the optimal temperature range for the nitrogen oxide treatment reaction. The temperature for treating carbon monoxide is higher than the temperature for treating nitrogen oxides. As a result, the carbon monoxide treatment catalyst can operate in a high-temperature range below the upper limit temperature compared to the SCR catalyst. By using a plurality of cooling coils (e.g., heat exchangers), the temperature of the turbine exhaust gas stream can be controlled, and the efficiency of the catalyst treatment can be improved.

[0019] In some embodiments of the turbine exhaust gas treatment system, the system uses supercritical carbon dioxide as the working fluid. This offers certain advantages in that supercritical carbon dioxide has a high fluid density, is easily pumped by a closed cooling loop, and has a high heat capacity, allowing the amount of fluid passing through the heat exchanger coil to be reduced for the same degree of temperature reduction for high-temperature turbine exhaust gas. In other embodiments of the turbine exhaust gas treatment system, other suitable heat transfer working fluids including, but not limited to, hot oil and / or water can be used. The system uses a cooling loop to cool the turbine exhaust gas stream to be treated. As used herein, "cooling loop" should be understood to refer to the equipment used in a cooling cycle that provides a working fluid cooled by a heat exchanger to cool the turbine exhaust gas or any other gas to be treated. For example, the cooling loop may include piping, conduits, etc. that enable the transfer of the working fluid; a condenser; a pump; an expansion nozzle; an evaporator; and / or other components (e.g., a shared or dedicated mass inventory system) for providing a refrigeration cycle to cool the turbine exhaust gas to be treated. The piping, conduits, etc. provide fluid communication of the working fluid between the other components of the cooling loop.

[0020] Referring to Figure 1, one embodiment of a turbine exhaust gas treatment system 100 using a carbon dioxide working fluid is shown. The exhaust gas to be treated (e.g., exhaust gas from a gas turbine or other process) is received by a turbine exhaust gas discharge structure 102. The turbine exhaust gas discharge structure 102 is configured to receive turbine exhaust gas from a source (e.g., a gas turbine) and to pass the turbine exhaust gas through the turbine exhaust gas discharge structure 102. For example, the turbine exhaust gas discharge structure 102 is connected to the turbine exhaust gas source by hard piped and may be or include pipes, ducts, or other structures.

[0021] The turbine exhaust gas passing through the turbine exhaust gas discharge structure 102 passes through the catalytic turbine exhaust gas treatment device 104. The catalytic turbine exhaust gas treatment device 104 is positioned at least partially within the turbine exhaust gas discharge structure 102 so that the turbine exhaust gas comes into contact with the catalytic turbine exhaust gas treatment device 104. The catalytic turbine exhaust gas treatment device 104 is configured to treat at least one component of the turbine exhaust gas through a catalytic reaction between the catalyst housed within the catalytic turbine exhaust gas treatment device 104 and at least one component of the turbine exhaust gas. For example, the catalytic turbine exhaust gas treatment device 104 may contain any suitable activator for reacting with carbon monoxide to form carbon dioxide. For example, carbon monoxide may be treated with platinum, rhodium, palladium, a common oxidizer, or any other suitable catalyst.

[0022] System 100 may further include a second catalytic turbine exhaust gas treatment device 106 located within the turbine exhaust gas discharge structure 102 and downstream of the first catalytic turbine exhaust gas treatment device 104. The second catalytic turbine exhaust gas treatment device 106 is configured to treat at least one component of the turbine exhaust gas through a catalytic reaction between a catalyst housed within the second catalytic turbine exhaust gas treatment device 106 and at least one component of the turbine exhaust gas. For example, the second catalytic turbine exhaust gas treatment device 106 includes any suitable activator for reacting with nitrogen oxides to form one or more of water, diatomic nitrogen, or other compounds. The activator may be anhydrous ammonia, an aqueous solution of ammonia, or a similar reactant, or may include the same.

[0023] In some embodiments, the first catalytic turbine exhaust gas treatment system 104 is configured to treat both carbon monoxide and nitrogen oxides in the turbine exhaust gas. The first catalytic turbine exhaust gas treatment system 104 can treat both carbon monoxide and nitrogen oxides using multiple catalysts or a single catalyst. For example, in the case of a single catalyst, the first catalytic turbine exhaust gas treatment system 104 may include iron and cobalt impregnated on activated semi-coke. The catalyst is supplied with carbon monoxide (e.g., carbon monoxide from the turbine exhaust gas) and absorbs or otherwise removes nitrogen oxides from the turbine exhaust gas. To treat both carbon monoxide and nitrogen oxides, other single catalysts such as a barium-accelerated copper chromate catalyst or any other suitable catalyst may also be used.

[0024] To reduce the temperature of the turbine exhaust gas to a range suitable for treatment by the catalytic turbine exhaust gas treatment device 104, the system includes a first heat exchanger 108. The first heat exchanger 108 is located at least partially within the turbine exhaust gas discharge structure 102 and is positioned upstream of the catalytic turbine exhaust gas treatment device 104. The first heat exchanger 108 is configured to remove heat from the turbine exhaust gas passing through the turbine exhaust gas discharge structure 102 by transferring heat through the first heat exchanger 108 to a working fluid (e.g., carbon dioxide) within the first heat exchanger 108. The working fluid passes through a cooling loop, providing continuous (e.g., on demand) cooling to the turbine exhaust gas during operation of the turbine exhaust gas treatment system 100. It should be understood that the turbine exhaust gas may also be cooled for purposes other than improving turbine exhaust gas treatment (e.g., reduction of carbon monoxide and / or nitrogen oxides). For example, the turbine exhaust gas may be cooled to be maintained within a specific temperature range, independently of the temperature range for turbine exhaust gas treatment. This allows turbine exhaust gas to be processed into other products or used for other purposes.

[0025] The cooled working fluid passes through the first heat exchanger 108 and exits from the first heat exchanger 108 with additional heat. The working fluid exiting the first heat exchanger enters a second heat exchanger 110 located downstream of the first heat exchanger 108. The second heat exchanger 110 is configured to remove the heat acquired in the first heat exchanger 108 from the working fluid. The second heat exchanger 110 may also be a condenser that facilitates the phase change of the gaseous or partially gaseous working fluid discharged from the first heat exchanger 108 to at least partially liquid discharged from the second heat exchanger 110. This facilitates the pumping of the working fluid. Alternatively, the second heat exchanger 110 simply removes heat from the working fluid.

[0026] In some embodiments, the second heat exchanger 110 is an air-cooled heat exchanger, and in other embodiments, the second heat exchanger 110 is a water-cooled heat exchanger. The second heat exchanger 110 includes a fan that passes air over the second heat exchanger 110. The second heat exchanger 110 transfers heat to the atmosphere. In some embodiments, the second heat exchanger 110 is a cooling tower or an evaporative cooler, or may include both.

[0027] The working fluid (e.g., carbon dioxide) that has left the second heat exchanger 110 is received by a pump 112 located downstream of the second heat exchanger 110. The pump 112 is configured to be adapted to drive the working fluid by the cooling loop. The pump 112 may be driven by an electric motor, such as a variable frequency drive motor. The pump 112 is configured to be adapted to pump supercritical carbon dioxide (or any other applicable fluid). In other embodiments (described later in this specification with reference to other drawings), the working fluid may undergo a phase change within the cooling loop, and the pump 112 is configured to be adapted to pump a mixed-phase working fluid. The pump 112 may compress the working fluid or simply pump the working fluid.

[0028] Pump 112 delivers the carbon dioxide working fluid flowing through the cooling loop to the expansion nozzle 114. The expansion nozzle 114 is located downstream of pump 112 and upstream of the first heat exchanger 108. The expansion nozzle 114 is configured to expand the supercritical carbon dioxide working fluid before it enters the first heat exchanger 108, thereby lowering the working fluid temperature. The expansion nozzle 114 can be configured to adapt to change at least some of the phases of the working fluid. Alternatively, the expansion nozzle 114 expands the working fluid without a phase change. The use of the expansion nozzle 114 (compared to a system without the expansion nozzle 114) lowers the working fluid temperature, thus reducing the amount of working fluid required to achieve the target gas temperature at the inlet of the catalytic exhaust gas treatment device 104. The reduced temperature allows for the use of even less working fluid.

[0029] System 100 includes a bypass loop, which includes a bypass nozzle 116. The bypass loop (including the bypass nozzle 116) is configured to be adjustable and optionally allow the working fluid to bypass the expansion nozzle 114. The expansion nozzle 114 can be bypassed using the bypass 116 if sufficient cooling is provided by the second heat exchanger 110 removing heat from the working fluid. For example, the ambient temperature may be low enough that the second heat exchanger 110 can provide sufficient cooling to the turbine exhaust gas. By bypassing the expansion nozzle 114, system 100 can avoid or reduce the pressure loss associated with the use of the expansion nozzle 114. By bypassing the expansion nozzle 114 and avoiding the aforementioned pressure loss, efficiency is improved because the energy required to pump with a pressure-held working fluid is reduced.

[0030] In embodiments including a bypass nozzle 116, the bypass is configured to bypass the expansion nozzle 114 so that the working fluid is instead expanded by the bypass expansion nozzle 116. The bypass nozzle 116 is configured to expand the working fluid to a smaller extent than the expansion nozzle 114. Alternatively, the bypass nozzle 116 may expand the working fluid to a larger extent than the expansion nozzle 114 so that the expansion nozzle 114 is bypassed if additional cooling is required to maintain the exhaust gas temperature within a range suitable for handling, as described herein. In other embodiments, the bypass nozzle 116 can be designed to minimize or reduce the expansion of the fluid passing through the bypass. The bypass valve and expansion nozzle may be functionally a throttle valve or a fixed device and can be operated manually or automatically.

[0031] System 100 further includes a mass inventory management system 118. The mass inventory management system 118 is configured to be adapted to manage the amount of working fluid in a cooling loop including a first heat exchanger 108. The mass inventory management system 118 is configured to be adapted to controllably receive working fluid from downstream of the first heat exchanger 108 in order to manage the amount of working fluid in the cooling loop. The mass inventory management system 100 is also configured to be adapted to add or remove working fluid from the cooling loop.

[0032] The mass inventory management system 118 controls the removal of working fluid from downstream of the first heat exchanger 108 at the takeoff point 120 (e.g., using a controllable valve). The working fluid removed from the cooling loop at the takeoff point 120 passes through a valve toward the pump 122. The pump 122 delivers the working fluid from the takeoff point 120 to the mass inventory management system 118. The working fluid pumped by the pump 122 passes through additional valves on its way to the mass inventory management system 118.

[0033] In the enlarged schematic diagram of the inventory management system shown in Figure 1, the working fluid is received into the first tank 124 of the mass inventory management system 118. The first tank 124 can function as a storage and / or temporary storage tank for the working fluid. The first tank is discharged by the mass inventory pump 126. The working fluid leaving the first tank 124 passes through a check valve located between the first tank 124 and the mass inventory pump 126. The mass inventory pump 126 can be controlled to supply the working fluid to the second tank 128 of the mass inventory management system 118. The second tank 128 can function as a storage tank for the working fluid. The working fluid driven by the pump 126 passes through the check valve and / or additional valves on its way to the second tank 128.

[0034] A controllable valve 130 (which may be, for example, an open / close discrete valve with a generally fixed flow limit, or an active flow control valve with flow control characteristics that allow for a variable flow rate) is located downstream of the second tank 128 to control the addition of working fluid to the cooling loop. The controllable valve 130 is positioned to discharge working fluid from the mass inventory management system 118 into the cooling loop downstream of the second heat exchanger 110 and upstream of the pump 112. The mass inventory management system 118 is also configured to controllably receive working fluid from the cooling loop at a second take-off point 132 located downstream of the pump 112 and upstream of the expansion nozzle 114.

[0035] Next, referring to Figure 1, System 100 includes various sensors used to control the pumping of working fluid to the first heat exchanger 108, pump 112, mass inventory management system 118, etc. In Figure 1, the sensor indicated by the abbreviation "PT" includes a pressure transducer configured to measure the pressure of the working fluid at the relevant point in System 100. The sensor indicated by the abbreviation "TE" includes a temperature element (e.g., thermocouple, thermistor, or similar) configured to measure the temperature of the working fluid or the turbine exhaust gas in System 100. The sensor indicated by the abbreviation "FT" includes a flow transmitter / flow meter (e.g., an anemometer, magnetic flow meter, turbine flow meter, rotometer, spring piston flow meter, etc.). System 100 may also employ additional and / or different types of process measurements to control and / or provide process conditions for data acquisition and system optimization.

[0036] The system 100 is controlled in operation using such sensors and controllable devices (e.g., valves). The system 100 is controlled primarily based on the temperature of the turbine exhaust gas entering the catalytic turbine exhaust gas treatment device 104, which is located within the high-temperature turbine exhaust gas stream and the turbine exhaust gas discharge structure 102. Alternatively, the system may also be controlled based on the temperature of the turbine exhaust gas entering the second catalytic turbine exhaust gas treatment device 106. A setpoint temperature relative to the high-temperature turbine exhaust gas temperature at the catalyst surface (e.g., the inlet of the first catalytic turbine exhaust gas treatment device and / or the second catalytic turbine exhaust gas treatment device) is used to modulate a variable-frequency drive motor that drives the pump 112. This controls the flow rate of the working fluid in the cooling loop, increasing the flow rate when the turbine exhaust gas temperature at the catalyst surface is higher than the setpoint. In an alternative embodiment, the pump 112 is not driven by a variable-frequency drive motor; instead, a flow control valve is located downstream of the pump 112. Such a flow control valve is used to control the flow rate of the working fluid through the cooling loop, and consequently control the temperature of the turbine exhaust gas.

[0037] In some embodiments, the system 100 is controlled by setting the flow rate of the working fluid passing through the bypass valve 116 by controlling the turbine exhaust gas temperature at the surface of the catalytic turbine exhaust gas treatment device 104. When the pump flow rate reaches a predetermined level, the flow rate is modulated through the bypass valve 116, allowing the turbine exhaust gas temperature at the surface of the catalytic turbine exhaust gas treatment device 104 to be controlled.

[0038] In embodiments of system 100 that include a heat exchanger using fans (e.g., a second heat exchanger 110), ON / OFF sequence control of the fans within the heat exchanger may be used to optimize or reduce power consumption and / or for additional temperature control of the working fluid. For example, on days with low ambient temperatures, the fans can be stopped if the working fluid temperature is low enough to achieve the desired turbine exhaust gas temperature at the catalyst surface. Furthermore, in some embodiments, one or more heat exchangers can be bypassed in whole or in part, and the corresponding fans can be switched to low-speed operation. By optionally bypassing one or more ambient air heat exchangers, additional temperature control of the working fluid can be achieved before it enters the heat exchanger 108 located in the high-temperature turbine exhaust gas stream. Bypassing one or more ambient air heat exchangers also reduces power consumption by the pump 112 because it reduces the low total pressure loss for closed working fluid loop flow.

[0039] In applications using CO2 (e.g., system 100 shown in Figure 1), the mass inventory management system 118 can be operated to maintain the CO2 working fluid in a supercritical state (T>32°C, 77 bar) or a liquid state throughout the entire working loop. However, it should also be understood that the use of the expansion valve / nozzle 114 may also allow a two-phase fluid containing steam to be introduced into the first heat exchanger 108 (e.g., a heat transfer coil in a high-temperature gas stream). In the case of the CO2 working fluid, to ensure that the fluid state at the inlet of the pump 112 is either supercritical (high-temperature environmental conditions, typically T>28°C) or liquid phase (low-temperature environmental conditions, typically T<28°C), the mass inventory management system 118 is controlled based on the temperature at the inlet of the pump 112 and is controlled to manage the pressure at this location by adding or removing mass from the closed cooling loop system.

[0040] Referring to Figures 2 to 8, different embodiments of the system 100 are illustrated and will be described later. Components shown in the same way as those shown in Figure 1 are identical or substantially similar unless otherwise described below. For example, in Figure 2, the first heat exchanger 208 is identical to the first heat exchanger 108 described with reference to Figure 1.

[0041] Referring specifically to Figure 2, a turbine exhaust gas treatment system 200 is shown, which is a variation of the turbine exhaust gas treatment system 100 shown in Figure 1. Instead of using carbon dioxide as the working fluid (as in system 100, for example), system 200 uses thermal oil as the working fluid. System 200 does not include expansion nozzles or bypass nozzles. The thermal oil working fluid does not expand before entering the first heat exchanger 208. System 200 also differs from system 100 in that the second heat exchanger 210 can be optionally bypassed through the control of system 200.

[0042] The systems 200 also differ from each other in that the mass inventory management system 218 includes only a single tank 224. Tank 224 is monitored by a level transmitter (LT), and the amount of hot oil in the cooling loop is controlled to control the entire system 200 as described with reference to Figure 1.

[0043] Referring to Figure 3, a turbine exhaust gas treatment system 300 is shown, which is a variation of the turbine exhaust gas treatment systems 100 and 200 shown in Figures 1 and 2. The turbine exhaust gas treatment system 300 differs from the turbine exhaust gas treatment system 200 shown in Figure 2 in that it uses water as the working fluid. The turbine exhaust gas treatment system 300 also differs in that it does not include a bypass for the second heat exchanger 310.

[0044] Referring to Figure 4, a turbine exhaust gas treatment system 400 is shown, which is a variation of the turbine exhaust gas treatment system 100 shown in Figure 1. The turbine exhaust gas treatment system 400 uses carbon dioxide as the working fluid. The turbine exhaust gas treatment system 400 differs from the turbine exhaust gas treatment system 100 in that it includes a third heat exchanger 434 and additional sensors associated with the third heat exchanger 434 (e.g., a temperature sensor located downstream of the third heat exchanger 434 and upstream of the expansion nozzle 414).

[0045] The third heat exchanger 434 is located downstream of the pump 412 and is configured to remove heat from the working fluid. The third heat exchanger 434 is either air-cooled or water-cooled. The third heat exchanger 434 includes a fan that passes ambient air over or through the third heat exchanger 434, thereby transferring heat from the working fluid to the ambient air. As described in relation to Figure 1, the fan can be controlled to minimize power consumption while maintaining the turbine exhaust gas temperature within a range suitable for processing by a catalytic-based turbine exhaust gas treatment system (e.g., one or more SCR systems). For example, the fan can be controlled based on the temperature of the working fluid upstream of the third heat exchanger 434, the temperature of the working fluid downstream of the third heat exchanger 434, and / or the temperature of the turbine exhaust gas before it enters the first catalytic exhaust gas treatment system and / or the second catalytic exhaust gas treatment system.

[0046] The system 400 also includes a manually operated or actuated bypass valve 436, which is configured to be controllable or selectively allow the working fluid to bypass the third heat exchanger 434. The bypass 436 is controlled based on one or more inputs described immediately prior to the control of the fan of the third heat exchanger 434 and / or other elements described in the prior embodiments. The third heat exchanger 434 may be bypassed or partially bypassed to improve the efficiency of the system 434 by reducing the power consumption of the associated fan and / or reducing the total pressure loss in the cooling loop. The third heat exchanger 434 is bypassed only if an appropriate turbine exhaust gas temperature can be maintained without using the third heat exchanger 434.

[0047] Referring to Figure 5, a turbine exhaust gas treatment system 500 is illustrated, which is a modified version of the turbine exhaust gas treatment system 200 shown in Figure 2. This includes a third heat exchanger 534 and a bypass 536 of the type described in relation to Figure 4. The turbine exhaust gas treatment system 500 differs from system 200 in that it includes a third heat exchanger 534. The turbine exhaust gas treatment system 500 differs from system 400 primarily in that its working fluid is hot oil. System 500 has the advantages of systems 200 and 400 (like system 400), but uses hot oil instead of carbon dioxide.

[0048] Referring to Figure 6, a turbine exhaust gas treatment system 600 is shown, which is a modified version of the turbine exhaust gas treatment system 300 shown in Figure 3, and which includes a third heat exchanger 634 and a bypass 636 of the type described in relation to Figure 4. The turbine exhaust gas treatment system 600 differs from system 300 in that it includes a third heat exchanger 634. The turbine exhaust gas treatment system 600 differs from system 400 mainly in that the working fluid is water. System 600 has the advantages of systems 300 and 400 (like system 400), but uses water instead of carbon dioxide.

[0049] Referring to Figure 7, a turbine exhaust gas treatment system 700 is shown, which is a modified version of the turbine exhaust gas treatment system 100 shown in Figure 1. The turbine exhaust gas treatment system 700 differs from system 100 primarily in that it includes a fourth heat exchanger 738. The fourth heat exchanger 738 is at least partially located within the turbine exhaust gas discharge section 702, downstream of the catalytic exhaust gas treatment device 704. The fourth heat exchanger 738 is also located upstream of the second catalytic turbine exhaust gas treatment device 706. The fourth heat exchanger 738 is configured to remove heat from the turbine exhaust gas passing through the turbine exhaust gas discharge structure 102 and transfer heat to the working fluid (e.g., carbon dioxide) passing through the fourth heat exchanger 738. The fourth heat exchanger is located downstream of the pump 712 and upstream of the second heat exchanger 710 within the cooling loop. The fourth heat exchanger 738 is also located downstream of the expansion nozzle 714.

[0050] The first heat exchanger 708 and the fourth heat exchanger 738 are arranged in a parallel loop so that the working fluid is branched, with separate portions of the working fluid passing through the first heat exchanger 708 and the fourth heat exchanger 738, respectively. After leaving the first heat exchanger 708 and the fourth heat exchanger 738, the separate portions of the working fluid are merged to form a single flow. The combined output is received by the second heat exchanger 710. The fourth heat exchanger 738 is preferentially supplied to maintain the turbine exhaust gas temperature range within the operating parameters of the second catalytic exhaust gas treatment device 706 and can be configured to take off from the working fluid before it reaches the first heat exchanger 708. In other words, the flow of the working fluid is branched upstream of the first heat exchanger 708 and the fourth heat exchanger 738 so that a portion of the working fluid is supplied to the first heat exchanger 708 and the separated portion is supplied to the fourth heat exchanger 738. This configuration (for example, in a parallel configuration rather than a series configuration where a single stream of working fluid is heated sequentially) supplies separate streams of cooled working fluid to each of the two heat exchangers. The length and configuration of the branch piping are adapted and configured to preferentially supply the fourth heat exchanger 738. Alternatively, the heat exchangers (i.e., 708 and 738) may be in a series configuration where the flow of the same coolant (e.g., CO2) passes through each heat exchanger, and the direction of the fluid flow may be parallel to or counter-flowing to the high-temperature turbine exhaust gas stream. In other words, it is possible to preferentially supply to either of the two heat exchangers, to supply in series to the heat exchangers, or to supply in parallel to the heat exchangers.

[0051] Advantageously, the use of two heat exchangers to independently cool the turbine exhaust gas before different catalytic treatment devices allows for independent control of the turbine exhaust gas temperature before each independent treatment device. This makes it possible to maintain the turbine exhaust gas temperature within a first range for treatment by the first catalytic treatment device 704 (e.g., carbon monoxide treatment). The turbine exhaust gas temperature is then independently maintained within a lower second temperature range for treatment by the second catalytic treatment device 706 (e.g., SCR for nitrogen oxide treatment).

[0052] The fourth heat exchanger 738 and the first heat exchanger 708 can be controlled independently based on the working fluid temperature monitored at the outlets of both the first heat exchanger 708 and the fourth heat exchanger 738. The flow of working fluid to the first heat exchanger 708 and the fourth heat exchanger 738 can be controlled through a temperature control valve (e.g., control valve 740) located in piping converted into a controlled coil. Two temperature control valves (one for each heat exchanger) or a single control valve 740 may be used to control the flow rate of working fluid to the fourth heat exchanger 738, with the remainder of the working fluid being supplied to the first heat exchanger 708 located downstream of the fourth heat exchanger 738.

[0053] The system 700 includes a mass inventory management system 718 configured to controllly receive the working fluid downstream of the fourth heat exchanger 738 at the extraction point 742 (for example, using a controllable valve). Otherwise, the mass inventory system 718 operates as described above.

[0054] Referring to Figure 8, a turbine exhaust gas treatment system 800 is shown, which is a variation of the turbine exhaust gas treatment system 700 shown in Figure 7. The turbine exhaust gas treatment system 800 differs from system 700 mainly in that it further includes a third heat exchanger 834 and a bypass 836 of the type illustrated and described in relation to Figure 4. This system 800 combines the advantages of the fourth heat exchanger 838 and the third heat exchanger 834 described above.

[0055] In general, the use of the fourth heat exchanger is illustrated only in Figures 7 and 8, but it should be understood that the fourth heat exchanger may also be used in any system described herein.

[0056] Referring to Figures 9A to 9C, multiple independent cooling loops can cool the turbine exhaust gas within the turbine exhaust gas discharge structure 902. Each independent cooling loop 950, 950', 950” (shown as a dotted line) cools the turbine exhaust gas using an independent heat exchanger within the turbine exhaust gas discharge structure 902. Independent cooling loop 950 cools the turbine exhaust gas by supplying cooled working fluid to the first heat exchanger 908, receiving heated working fluid from the first heat exchanger 908, and cooling the heated working fluid before supplying it to the first heat exchanger 908. Independent cooling loop 950 uses solid piping to provide fluid communication and control of the working fluid between the other components of the cooling loop 950. The independent cooling loop 950' further includes conduits, valves, or similar components. The independent cooling loop 950' cools the turbine exhaust gas discharge structure 902. The independent cooling loop 950' cools the turbine exhaust gas by supplying cooled working fluid to the fourth heat exchanger 938, receiving heated working fluid from the fourth heat exchanger 938, and cooling the heated working fluid before supplying it to the fourth heat exchanger 938. The independent cooling loop 950' further includes piping, conduits, valves, etc., shown by solid lines, to provide fluid communication and control of the working fluid between the other components of the cooling loop 950'.

[0057] Each independent cooling loop 950 includes at least a second heat exchanger 910 and a pump 912. Similarly, each independent cooling loop 950' includes at least a second heat exchanger 910' and a pump 912'. Each independent cooling loop 950, 950' similarly includes heat exchangers (first heat exchanger 908 and fourth heat exchanger 938) located within the turbine exhaust gas discharge structure 902. Each independent cooling loop 950, 950' may include other equipment of the type described in relation to any embodiment disclosed herein. For example, each independent cooling loop 950, 950' may include expansion nozzles 914, 914', bypass nozzles 916, 916', mass inventory systems 918, 918', pumps 922, 922' for extracting and supplying the mass inventory systems, etc. Each independent cooling loop 950, 950' may also include a third heat exchanger of the type described in relation to Figures 4-6 and 8. The mass inventory systems 918, 918' may be of the type described in relation to the different embodiments disclosed herein.

[0058] It should also be understood that the system 900, including the independent cooling loops 950, 950', can use any working fluid described herein (e.g., carbon dioxide, water, thermal fluid / oil, etc.). Since the independent cooling loops 950, 950' are independent structures, each having its own independent mass inventory system 918, 918', the independent cooling loops 950, 950' can use different working fluids. For example, the independent cooling loop 950 may use water as its working fluid, and the independent cooling loop 950' may use carbon dioxide as its working fluid. Any combination of working fluids can be used.

[0059] Referring to Figure 9B, system 900 includes independent cooling loops 950, 950' but has a shared mass inventory system 918. This embodiment is substantially similar to that described with respect to Figure 9A, but differs substantially in that the independent cooling loops 950, 950' share a single mass inventory system 918 and the independent cooling loops share a working fluid. The mass inventory system 918 is any configuration described herein in relation to other embodiments and drawings, and appropriate modifications can be made to double the inputs and outputs to accommodate the two separate cooling loops 950, 950'. The mass inventory system 918 is adapted and configured to transmit the working fluid between the separate cooling loops 950, 950'.

[0060] Referring to Figure 9C, the type of system 900 described herein includes any number of catalytic turbine exhaust gas treatment devices and any number of separate cooling loops 950, 950', 950''. For example, and as shown in Figure 9C, the system 900 includes three catalytic turbine exhaust gas treatment devices. A first heat exchanger 908 is configured to work in conjunction with a separate cooling loop 950 to cool turbine exhaust gas within a turbine exhaust gas discharge structure upstream of the first catalytic turbine exhaust gas treatment device 904. A fourth heat exchanger 938 works in conjunction with a separate cooling loop 950' to cool turbine exhaust gas upstream of the second catalytic turbine exhaust gas treatment device 906. A sixth heat exchanger 952 works in conjunction with a separate cooling loop 950'' to cool turbine exhaust gas upstream of the third catalytic turbine exhaust gas treatment device 954. In this embodiment, each isolated cooling loop 950, 950', 950'' includes a separate mass inventory system, and each loop can use a different working fluid. It should be understood that three or more isolated cooling loops can be used with the type of single mass inventory system described in relation to Figure 9B. It should also be understood that three or more catalytic turbine exhaust gas treatment systems can be used in a system with a single cooling loop having parallel branches supplying each isolated heat exchanger (for example, as shown in at least Figure 7).

[0061] Referring to Figures 1 to 9C, the system described herein includes several heat exchangers as generally described. It should be understood that the heat exchangers described herein may be any suitable configuration. For example, any or all of the heat exchangers may be a parallel-flow heat exchanger, a cross-flow heat exchanger, a counter-flow heat exchanger, or any other suitable heat exchanger.

[0062] It should be understood that the systems described herein include multiple catalytic turbine exhaust gas treatment systems. However, in alternative embodiments, one or more catalytic turbine exhaust gas treatment systems may be replaced with different turbine exhaust gas treatment systems, but are not limited to non-catalytic treatment systems. The non-catalytic treatment system may include a membrane, a urea injection system, or other system configured to remove one or more compounds from the turbine exhaust gas. For example, the membrane may be a synthetic membrane made of a polymer, cellulose acetate, or ceramic material. Any suitable material may be used for the membrane, and the membrane may be configured to remove carbon monoxide, nitrogen oxides, sulfur dioxide, hexane, carbon dioxide, butane, methane, benzene, or other compounds.

[0063] Next, referring to Figures 1 to 9C, the system described herein provides the advantages described herein for improving turbine exhaust gas treatment. The system provides increased control over the temperature of the turbine exhaust gas, ensuring that the turbine exhaust gas is treated. The system described herein also provides increased efficiency through control of various components of the cooling subsystem used for cooling the turbine exhaust gas treatment. Furthermore, the system described herein does not use or does not include a forced draft fan for mixing the turbine exhaust gas with air, using a working fluid cooling system and corresponding technology (e.g., refrigeration or other common cooling methods), and does not require the injection of water into the high-temperature turbine exhaust gas stream. This not only improves efficiency by eliminating the power consumption associated with forced draft fans, but also reduces the negative effects (e.g., corrosion) that may occur as a result of water injection. Similarly, the system described herein does not use or include an induced draft fan. Such a fan is unnecessary because the use of the cooling system described herein does not require additional upstream air to cool the turbine exhaust gas. The system described herein exhausts the treated turbine exhaust gas directly into the atmosphere.

[0064] Figure 10 shows a further embodiment of the turbine exhaust gas treatment system 1000 of the present disclosure. Similar to the embodiment in Figure 1, the system 1000 of Figure 10 includes an exhaust gas discharge structure 1002 in communication with a gas turbine operating on a simple cycle. The exhaust gas discharge structure 1002 is structured and constructed in a position adjacent to the gas turbine that injects exhaust gas G, and is therefore configured to receive exhaust gas G injected from a gas turbine operating on a simple cycle (i.e., there is no heat recovery steam generator (HRSG) operating with the gas turbine). The exhaust gas discharge structure 1002 receives the high-temperature exhaust gas G from the gas turbine and is configured to allow the exhaust gas to pass through the exhaust gas discharge structure 1002. The exhaust gas discharge structure 1002 shown in Figure 10, similar to the system described above, further comprises a catalytic converter or catalytic turbine exhaust gas treatment device, such as a selective catalytic reduction (SCR) device 1006, inside the exhaust gas discharge structure 1002.

[0065] Similar to the embodiment in Figure 1, the exhaust gas G passing through the exhaust gas discharge structure 1002 in Figure 10 passes through the SCR 1006. The SCR 1006 receives the exhaust gas and is configured to process at least one component of the turbine exhaust gas G through a catalytic reaction between the catalyst housed in the SCR 1006 and at least one component of the turbine exhaust gas G. To reduce the temperature of the turbine exhaust gas G to a range suitable for processing by the SCR 1006, the system 1000 in Figure 10 further includes a heat transfer coil of a first heat exchanger 1008, which is at least partially located within the exhaust gas discharge structure 1002 and upstream of the SCR 1006. In a manner similar to the embodiment in Figure 1, the first heat exchanger 1008 receives the flow of exhaust gas passing through the exhaust gas discharge structure 1002 and is configured to remove heat from the flow of exhaust gas G passing through the exhaust gas discharge structure 1002 and cool it by transferring heat through the heat transfer coil of the first heat exchanger 1008 to the working fluid in the heat transfer coil. The working fluid may be carbon dioxide, water, hot oil, or any other fluid used in the heat exchanger. The first heat exchanger 1008 is part of the cooling loop, and the working fluid passes through the cooling loop during the operation of the system 1000 to continuously cool the exhaust gas G. As in the embodiments described above, the exhaust gas may be cooled for purposes other than improving the exhaust gas treatment by SCR 1006. For example, the exhaust gas may be cooled to maintain it within a predetermined temperature range, independently of the treatment temperature range by SCR 1006.

[0066] The working fluid passes through the first heat exchanger 1008 and is heated by the turbine exhaust gas G passing through the first heat exchanger. The heated working fluid leaves the first heat exchanger 1008 with additional heat and is led through the first conduit 1010 or other fluid transfer device. The first conduit 1010 extends from the first heat exchanger 1008 to one or more heat exchangers of the district heating (DH) system 1012. The district heating system 1012 includes a distribution network that connects the flow of working fluid in a cooling loop to the heat exchangers of the district heating system and connects the flow of working fluid from the heat exchangers of the district heating system to the cooling loop. The district heating system 1012 is located outside the exhaust gas discharge structure 1002.

[0067] The district heating system 1012, or heat network or teleheating system, is configured to distribute the heat generated at the centralized location of the gas turbine through a distribution network (e.g., a network of insulated piping). The distribution network is configured to communicate the generated heat to heat users (e.g., residential and / or commercial users) and to meet their heating requirements. The working fluid leaving the first heat exchanger 1008 enters the heat exchanger of the district heating system 1012 located downstream of the first heat exchanger 1008. The district heating system 1012 is configured to remove the heat acquired in the first heat exchanger 1008 from the working fluid.

[0068] The working fluid is cooled by the district heating system 1012 and led to the pump 1016 via a second conduit 1014. The pump 1016 is located downstream from the district heating system 1012 and is configured to receive the cooled working fluid from the second conduit 1014 and drive the working fluid through a cooling loop. The pump 1016 may be driven by an electric motor or a different type of drive mechanism.

[0069] Pump 1016 drives the working fluid through a third conduit 1018 of the cooling loop. The third conduit 1018 extends from pump 1016 to the heat transfer coil of the second heat exchanger 1020 and is configured to guide the working fluid from pump 1016 to the heat transfer coil of the second heat exchanger 1020. The second heat exchanger 1020 is located in the gas turbine exhaust gas flow path that passes through SCR 1006 and is discharged. The working fluid passing through the second heat exchanger 1020 acquires heat again from the gas turbine exhaust gas flow discharged from SCR 1006 and cools the flow. The second heat exchanger 1020 is configured to further cool the gas turbine exhaust gas passing through the second heat exchanger 1020 that is discharged from SCR 1006 before the exhaust gas enters components further downstream of the exhaust gas discharge structure 1002. For example, a component further downstream of the exhaust gas discharge structure 1002 may be an additional second catalytic converter, such as a second SCR 1022.

[0070] The fourth conduit 1024 extends from the second heat exchanger 1020 to the first heat exchanger 1008 and is configured to guide the working fluid from the second heat exchanger 1020 to the first heat exchanger 1008. The second heat exchanger 1020 is located downstream of the pump 1016 and upstream of the first heat exchanger 1008, and after recovering some of the final heat from the turbine exhaust gas discharged from the SCR 1006, it returns the working fluid to the first heat exchanger 1008 through the cooling loop.

[0071] As shown in Figure 10, the first heat exchanger 1008, the catalytic converter or SCR 1006, and the second heat exchanger 1020 are located within the exhaust gas discharge structure 1002. The exhaust gas discharge structure 1002 is configured to guide the exhaust gas received from a gas turbine operating in a simple cycle through the first heat exchanger 1008, the catalytic converter or SCR 1006, and the second heat exchanger 1020 in that order. The district heating system 1012 is located outside the exhaust gas discharge structure 1002 and is separate from the structure. The pump 1016 is located in the cooling loop but is located outside the exhaust gas discharge structure 1002, although the pump may be located inside the structure.

[0072] Figure 11 shows a further embodiment of the system 1100 for treating turbine exhaust gases according to the present disclosure. The embodiment in Figure 11 is substantially identical to the embodiment in Figure 10 described above. Among the components of system 1100 in Figure 11, those components that are the same as those in system 1000 in Figure 10 are denoted by the same reference numerals used in Figure 10. Similar to system 1000 in Figure 10, system 1100 in Figure 11 also includes an exhaust gas discharge structure 1002 that receives exhaust gas G discharged from a gas turbine and is configured to guide the exhaust gas through the exhaust gas discharge structure 1002. Similar to the systems described above, the exhaust gas discharge structure 1002 in Figure 11 also includes a catalytic converter or catalytic turbine exhaust gas treatment device, such as a selective catalytic reduction (SCR) device 1006, inside the exhaust gas discharge structure 1002. The SCR 1006 functions as described above.

[0073] Similar to system 1000 in Figure 10, system 1100 in Figure 11 also includes heat transfer coils for a first heat exchanger 1008 located at least partially within the exhaust gas discharge structure 1002 upstream of the SCR 1006. The first heat exchanger 1008 functions as described above.

[0074] Similar to system 1000 in Figure 10, in system 1100 in Figure 11, the first heat exchanger 1008 is part of the cooling loop. The working fluid passing through the first heat exchanger 1008 is heated in the first heat exchanger 1008 and then guided through the first conduit 1010 extending from the first heat exchanger 1008. However, instead of extending to the district heating system 1012 as shown in system 1000 in Figure 10, the first conduit 1010 in system 1100 shown in Figure 11 extends from the first heat exchanger 1008 to the heat exchanger coil of the primary heat exchanger 1102. The heat acquired by the working fluid in the first heat exchanger 1008 is transferred to the heat exchanger coil of the primary heat exchanger 1102. The primary heat exchanger 1102 is part of the district heating loop, which includes the district heating system 1104. The primary heat exchanger transfers heat to the district heating loop, as described below.

[0075] As the primary heat exchanger 1102 transfers heat to the district heating loop, the cooled working fluid is guided to the pump 1016 through the second conduit 1014. The pump 1016 receives the cooled working fluid from the primary heat exchanger 1102 and drives the working fluid through the third conduit 1018 of the cooling loop.

[0076] The third conduit 1018 extends from the pump 1016 to the heat transfer coil of the second heat exchanger 1020. As previously described, the second heat exchanger 1020 is positioned in the flow path of the gas turbine exhaust gas that is discharged through the SCR 1006. The working fluid passing through the second heat exchanger 1020 again acquires heat from the flow of gas turbine exhaust gas discharged from the SCR 1006, and cools that flow. The exhaust gas then passes through components further downstream of the exhaust gas discharge structure 1002, for example, the second SCR 1022.

[0077] In the same manner as described above, the fourth conduit 1024 extends from the second heat exchanger 1020 to the first heat exchanger 1008, and guides the working fluid from the second heat exchanger 1020 back to the first heat exchanger 1008.

[0078] System 1100 in Figure 11 differs from system 1000 in Figure 10 in that it includes a fifth conduit 1106 extending from the primary heat exchanger 1102 to the district heating system 1104. The fifth conduit 1106 guides the working fluid, which has acquired heat from the heat transfer coil of the primary heat exchanger 1102, to the district heating system 1104. The district heating system 1104 in Figure 11 is substantially the same type of district heating system as the district heating system 1012 in Figure 10 described above. The working fluid leaving the primary heat exchanger 1102 enters the heat exchanger of the district heating system 1104, which is located downstream of the primary heat exchanger 1102. The district heating system 1104 is configured to remove the heat acquired in the primary heat exchanger 1102 from the working fluid and distribute the heat through the distribution network in the same manner as described above.

[0079] In Figure 11, the working fluid is cooled by the district heating system 1104 and led to the pump 1110 via the sixth conduit 1108. The pump 1110 is located downstream of the district heating system 1104 and is configured to receive the cooled working fluid from the sixth conduit 1108 and to drive the working fluid through the district heating loop. The pump 1110 then drives the working fluid again through the seventh conduit 1112 of the district heating loop to the primary heat exchanger 1102, completing the district heating loop.

[0080] The additional advantages of the system described herein are as follows: The system described herein can eliminate or reduce the complexity of flow regulators, which are often required in turbine exhaust streams to ensure good flow distribution of high-temperature turbine exhaust gas in terms of catalytic systems. Such flow regulators have the problem of being expensive to supply / install due to their operating requirements, as they are under the influence of high turbine exhaust gas temperatures and highly turbulent turbine exhaust gas flow. The system described herein can eliminate or reduce such flow regulators as a result of the turbine exhaust gas being controlledly cooled and / or the use of dilution air being eliminated. That is, since the system described herein does not use dilution air, a flow regulator for adequately mixing dilution air with the turbine exhaust gas is unnecessary. Additionally or alternatively, heat exchangers placed within the turbine exhaust gas discharge structure can adequately disperse the flow of the turbine exhaust gas.

[0081] Furthermore, it should be understood that the systems described herein transfer heat from turbine exhaust gases for use in heating applications, while the energy can also be used for power generation. The heated working fluid can heat other process fluids through a heat exchanger. The heated working fluid can drive mechanical devices (e.g., pumps). In addition, it is possible to expand the heated working fluid to drive a turbine, which in turn drives an electric generator.

[0082] Furthermore, while the present invention is not limited to the use of CO2, the use of CO2 in particular further reduces the required pump power compared to other gases / steams and provides an inert fluid, so the system does not need to consider the potential hazardous operation required when using other fluids. The use of CO2 also eliminates the need for the equipment to remove fluid from the system during downtime when freezing conditions are present, and eliminates the need to provide expensive heat trace equipment (in terms of capital and operation) to prevent freezing (e.g., systems using water as the medium) or sludge formation (oil systems). Stack dampers, which are normally required to reduce airflow through gas pathways in freezing conditions, are also not used in the systems described herein.

[0083] Since various modifications can be made to the above structure and method without departing from the broad scope of this disclosure, all matters included in the above description or shown in the accompanying drawings should be interpreted as illustrative rather than restrictive.

Claims

1. A system for treating gas turbine exhaust gas, wherein the system is The first heat exchanger is configured to receive exhaust gas and to cool the exhaust gas as it passes through the first heat exchanger, As a catalytic converter, the catalytic converter is configured to receive exhaust gas from the first heat exchanger, and the catalytic converter is configured to reduce specific gaseous emissions from the exhaust gas received from the first heat exchanger as the exhaust gas from the first heat exchanger passes through the catalytic converter, As a second heat exchanger, the second heat exchanger is configured to receive exhaust gas from the catalytic converter with specific emissions reduced, and the second heat exchanger is configured to cool the exhaust gas received from the catalytic converter as the exhaust gas passes through the second heat exchanger, As a cooling loop, the cooling loop is configured to receive the flow of working fluid from the first heat exchanger and to guide the flow of working fluid from the first heat exchanger to the second heat exchanger, and the cooling loop is configured to receive the flow of working fluid from the second heat exchanger and to guide the flow of working fluid from the second heat exchanger to the first heat exchanger, As a district heating system, the district heating system is connected to the cooling loop and is in fluid communication with the flow of the working fluid guided by the cooling loop, Exhaust gas discharge structure, Includes, At least partially, the first heat exchanger is located within the exhaust gas discharge structure, and the catalytic converter and the second heat exchanger are located inside the exhaust gas discharge structure. The district heating system is a system located outside the exhaust gas discharge structure.

2. The district heating system includes a distribution network, the distribution network being configured to connect the flow of a working fluid in the cooling loop to the heat exchanger of the district heating system, and the flow of a working fluid from the heat exchanger of the district heating system to the cooling loop, according to claim 1.

3. The catalytic converter is a first catalytic converter, and further, The system according to claim 1, further comprising a second catalytic converter, the second catalytic converter configured to receive cooled exhaust gas from the second heat exchanger, and the second catalytic converter configured to reduce specific gaseous emissions from the exhaust gas received from the second heat exchanger as the exhaust gas receives from the second heat exchanger passes through the second catalytic converter.

4. The system according to claim 1, further comprising a pump, the pump connected to the cooling loop and in fluid communication with the flow of the working fluid guided by the cooling loop.

5. The system according to claim 3, further comprising the second catalytic converter being located inside the exhaust gas discharge structure.

6. The system according to claim 3, wherein the exhaust gas discharge structure is configured to communicate with a gas turbine and to receive exhaust gas from the gas turbine, and the exhaust gas discharge structure is further configured to guide the exhaust gas received from the gas turbine in the order of the first heat exchanger, the catalytic converter, the second heat exchanger, and the second catalytic converter.

7. The system according to claim 6, further comprising the exhaust gas discharge structure being configured to communicate with the gas turbine when the gas turbine is operating in a simple cycle.

8. The system according to claim 3, further comprising: the exhaust gas discharge structure communicating with a gas turbine operating in a simple cycle and configured to receive exhaust gas from the gas turbine operating in a simple cycle, the exhaust gas discharge structure being configured to guide the exhaust gas received from the gas turbine operating in a simple cycle to the first heat exchanger, the catalytic converter, the second heat exchanger, and the second catalytic converter in that order.

9. As a first conduit, the first conduit is configured to connect the working fluid from the first heat exchanger to the district heating system, As a second conduit, the second conduit is configured to connect the working fluid from the district heating system to the pump, As a third conduit, the third conduit is configured to connect the working fluid from the pump to the second heat exchanger, As a fourth conduit, the fourth conduit is configured to connect the working fluid from the second heat exchanger to the first heat exchanger, The system according to claim 1, further comprising:

10. A system for treating exhaust gas from a gas turbine, wherein the system is The first heat exchanger is configured to receive the flow of exhaust gas from a gas turbine and to cool the flow of exhaust gas as it passes through the first heat exchanger, As a catalytic converter, the catalytic converter receives the flow of exhaust gas from the gas turbine from the first heat exchanger and is configured to reduce specific gas emissions from the flow of exhaust gas as it passes through the catalytic converter, As a second heat exchanger, the second heat exchanger is configured to receive the flow of exhaust gas from the gas turbine, from which specific emissions have been reduced from the catalytic converter, and to cool the flow of exhaust gas as it passes through the second heat exchanger. As a district heating system, the district heating system is located outside the flow of exhaust gas from the gas turbine, As a cooling loop, the cooling loop is configured to receive the flow of working fluid from the first heat exchanger and to guide the flow of working fluid from the first heat exchanger to the district heating system, the cooling loop is configured to receive the flow of working fluid from the district heating system and to guide the flow of working fluid from the district heating system to the second heat exchanger, and the cooling loop is configured to receive the flow of working fluid from the second heat exchanger and to guide the flow of working fluid from the second heat exchanger to the first heat exchanger, The exhaust discharge structure is configured to receive the flow of exhaust gas from the gas turbine, guide the flow of exhaust gas to the first heat exchanger, then guide the flow of exhaust gas from the first heat exchanger to the catalytic converter, and then guide the flow of exhaust gas from the catalytic converter to the second heat exchanger. Includes, The district heating system is a system located outside the exhaust gas discharge structure.

11. The district heating system according to claim 10, wherein the district heating system includes a distribution network, the distribution network is configured to guide the flow of the working fluid in the cooling loop to the heat exchanger of the district heating system, and the flow of the working fluid from the heat exchanger of the district heating system to the cooling loop.

12. The catalytic converter is a first catalytic converter, As a second catalytic converter, the second catalytic converter is configured to receive cooled exhaust gas from the second heat exchanger, and the second catalytic converter is configured to reduce specific gaseous emissions from the exhaust gas received from the second heat exchanger as the exhaust gas passes through the second catalytic converter, The system according to claim 10, further comprising:

13. The system according to claim 10, further comprising the pump, wherein the pump is configured to receive the flow of the working fluid from the cooling loop and to guide the flow of the working fluid through the cooling loop.

14. The system according to claim 10, further comprising: the cooling loop including a pump, the pump being configured to receive the flow of working fluid from the district heating system and to guide the flow of working fluid through the cooling loop to the second heat exchanger.

15. The exhaust discharge structure is configured to receive the flow of exhaust gas from a gas turbine, guide the flow of exhaust gas to the first heat exchanger, then guide the flow of exhaust gas from the first heat exchanger to the catalytic converter, and then guide the flow of exhaust gas from the catalytic converter to the second heat exchanger. The system according to claim 10, further comprising the district heating system being located outside the exhaust gas discharge structure.

16. Further including an exhaust gas emission structure, The first heat exchanger, the catalytic converter, and the second heat exchanger are located inside the exhaust gas discharge structure. The district heating system is located outside the exhaust gas discharge structure. The system according to claim 10, wherein the exhaust gas discharge structure communicates with a gas turbine and is configured to receive exhaust gas from the gas turbine, and the exhaust gas discharge structure is configured to guide the exhaust gas from the gas turbine in the order of the first heat exchanger, the catalytic converter, and the second heat exchanger.

17. The system according to claim 16, further comprising the exhaust gas discharge structure being configured to communicate with the gas turbine when the gas turbine is operating in a simple cycle.

18. The system according to claim 16, further comprising: the exhaust gas discharge structure communicating with a gas turbine operating in a simple cycle and configured to receive exhaust gas from the gas turbine operating in a simple cycle, and the exhaust gas discharge structure being configured to guide the exhaust gas received from the gas turbine operating in a simple cycle to the first heat exchanger, the catalytic converter, and the second heat exchanger in that order.

19. The cooling loop includes a first conduit, which is configured to connect the working fluid from the first heat exchanger to the district heating system. The cooling loop includes a second conduit, which is configured to connect the working fluid from the district heating system to the pump. The cooling loop includes a third conduit, which is configured to connect the working fluid from the pump to the second heat exchanger. The system according to claim 10, further comprising: the cooling loop including a fourth conduit, the fourth conduit being configured to connect the working fluid from the second heat exchanger to the first heat exchanger.

20. A system for treating exhaust gas, wherein the system is As an exhaust gas discharge structure, the exhaust gas discharge structure is configured to receive the flow of exhaust gas from a gas turbine and to guide the flow of exhaust gas through the exhaust gas discharge structure, The first heat exchanger in the exhaust gas discharge structure is configured to receive the flow of exhaust gas introduced through the exhaust gas discharge structure and to cool the flow of exhaust gas as it passes through the first heat exchanger, As a first catalytic converter in the exhaust gas discharge structure, the first catalytic converter receives the flow of exhaust gas introduced through the exhaust gas discharge structure from the first heat exchanger, and is configured to reduce specific emissions from the flow of exhaust gas received from the first heat exchanger as the flow of exhaust gas passes through the first catalytic converter, The second heat exchanger in the exhaust gas discharge structure is configured to receive the flow of exhaust gas introduced through the exhaust gas discharge structure from the catalytic converter and to cool the flow of exhaust gas as it passes through the second heat exchanger, As a second catalytic converter in the exhaust gas discharge structure, the second catalytic converter is configured to be adapted to receive the flow of exhaust gas that is guided through the exhaust gas discharge structure and cooled by the second heat exchanger, and the second catalytic converter is configured to be adapted to reduce specific gas emissions from the flow of exhaust gas received from the second heat exchanger as the flow of exhaust gas passes through the second catalytic converter, A district heating system located outside the exhaust gas discharge structure and outside the flow of exhaust gas introduced through the exhaust gas discharge structure, As a cooling loop, the cooling loop is configured to receive the flow of working fluid from the first heat exchanger and to guide the flow of working fluid from the first heat exchanger to the district heating system, the cooling loop is configured to receive the flow of working fluid from the district heating system and to guide the flow of working fluid from the district heating system to the second heat exchanger, and the cooling loop is configured to receive the flow of working fluid from the second heat exchanger and to guide the flow of working fluid from the second heat exchanger to the first heat exchanger, A system that includes this.

21. The cooling loop includes a first conduit, which is configured to connect the working fluid from the first heat exchanger to the district heating system. The cooling loop includes a second conduit, which is configured to connect the working fluid from the district heating system to the pump. The cooling loop includes a third conduit, which is configured to connect the working fluid from the pump to the second heat exchanger. The system according to claim 20, further comprising: the cooling loop including a fourth conduit, the fourth conduit being configured to connect the working fluid from the second heat exchanger to the first heat exchanger.

22. The system according to claim 21, further comprising a pump, the pump connected to the cooling loop and in fluid communication with the flow of the working fluid guided by the cooling loop.

23. A method for treating gas turbine exhaust gas flowing through an exhaust gas discharge structure, wherein the method is The steps include: directing exhaust gas from a gas turbine to a flow through a first heat exchanger located at least partially within the exhaust gas discharge structure, and transferring heat from the flow of exhaust gas directed through the first heat exchanger to a working fluid passing through the first heat exchanger; The steps include: guiding the exhaust gas from the first heat exchanger through a catalytic converter located within the exhaust gas discharge structure to the flow of exhaust gas, and reducing specific gas emissions from the flow of exhaust gas guided through the catalytic converter; The steps include: directing specific gas emissions from the catalytic converter through a second heat exchanger located within the exhaust gas discharge structure to the flow of exhaust gas with reduced emissions, and transferring heat from the flow of exhaust gas directed through the second heat exchanger to the working fluid passing through the second heat exchanger; In a cooling loop with a district heating system, the steps include connecting the first heat exchanger and the second heat exchanger (the district heating system is located outside the exhaust gas discharge structure), The steps include circulating the working fluid in the cooling loop in the order of the first heat exchanger, the district heating system, the second heat exchanger, and the first heat exchanger, Methods that include...

24. The catalytic converter is a first catalytic converter, The method according to claim 23, further comprising the steps of guiding the flow of exhaust gas from the second heat exchanger to a second catalytic converter located within the exhaust gas discharge structure, and reducing specific gas emissions from the flow of exhaust gas received from the second heat exchanger and guided through the second catalytic converter.

25. A step of heating the working fluid with heat transferred from the first heat exchanger to the working fluid, The steps include circulating the working fluid from the first heat exchanger to the district heating system in the cooling loop, thereby transferring heat from the working fluid to the district heating system, The method according to claim 23, further comprising:

26. A pump placed in the aforementioned cooling loop, The method according to claim 23, further comprising the step of operating the pump to circulate the working fluid in the cooling loop.

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