Patent Grant
10968781
The subject matter disclosed herein relates to probes, and more specifically, to control of discharge flows from probes coupled to gas turbine engines.
A gas turbine engine combusts a mixture of fuel and oxidant to generate hot exhaust gases, which in turn drive one or more turbine stages. Probes, such as temperature probes, pressure probes, and lambda probes, may be coupled to various components of the gas turbine engine that may operate in a high temperature environment. Unfortunately, the probes may be subjected to high temperatures. Therefore, a need exists for cooling of the probes with minimal impact to the surrounding environment.
Certain embodiments commensurate in scope with the present disclosure are summarized below. These embodiments are not intended to limit the scope of the claims, but rather these embodiments are intended only to provide a brief summary of possible forms of the present disclosure. Indeed, embodiments of the present disclosure may encompass a variety of forms that may be similar to or different from the embodiments set forth below.
In a first embodiment, a system includes a probe. The probe includes a sensing component configured to sense a parameter of a turbomachine. The probe also includes an inlet configured to receive a cooling inflow. The probe also includes a cooling passage configured to receive the cooling inflow from the inlet. The cooling passage is disposed along at least a portion of the probe, and the cooling inflow absorbs heat from the probe. The probe also includes an outlet coupled to the cooling passage and configured to receive an outflow from the cooling passage. The outflow includes at least a portion of the cooling inflow. The system also includes an ejector coupled to the outlet. The ejector includes an interior. The ejector also includes an opening fluidly coupled to the interior. The opening is configured to receive a coolant. The ejector also includes a nozzle coupled to the outlet. The nozzle is configured to constrict the outflow from the outlet and to deliver the outflow to the interior. The ejector also includes a mixing portion configured to mix the outflow and the coolant to provide a discharge flow.
In a second embodiment, a system includes a probe. The probe includes a sensing component configured to sense a parameter of a gas turbine engine. The probe also includes an inlet configured to receive a cooling inflow. The probe also includes a cooling passage configured to receive the cooling inflow from the inlet. The cooling passage is disposed along at least a portion of the probe, and the cooling inflow absorbs heat from the probe to form a heated outflow. The probe also includes an outlet coupled to the cooling passage and configured to receive the heated outflow from the cooling passage. A temperature of the heated outflow at the outlet is greater than 80° C. The system also includes an ejector coupled to the outlet. The ejector includes an interior. The ejector also includes an opening fluidly coupled to the interior. The opening is configured to receive a coolant. The ejector also includes a nozzle coupled to the outlet. The nozzle is configured to constrict the heated outflow from the outlet and to deliver the heated outflow to the interior. The ejector also includes a mixing portion configured to mix the heated outflow and the coolant to provide a discharge flow. A temperature of the discharge flow is less than 80° C.
In a third embodiment, a method includes supplying a cooling inflow to a probe configured to sense a parameter of a gas turbine engine. The cooling inflow is configured to absorb heat from the probe to form a heated outflow. The method also includes directing the heated outflow from the probe to an ejector. The ejector includes a nozzle coupled to an outlet of the probe. The method also includes constricting the heated outflow through the nozzle into an interior of the ejector to draw a coolant into the interior of the ejector via an opening. The method also includes mixing the heated outflow and the coolant to form a discharge flow in a mixing portion of the ejector. The method also includes directing the discharge flow to an ejector outlet of the ejector. A temperature of the discharge flow is less than 80° C.
These and other features, aspects, and advantages of the present disclosure will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
One or more specific embodiments of the present disclosure will be described below. In an effort to provide a concise description of these embodiments, all features of an actual implementation may not be described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers' specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.
Accordingly, while example embodiments are capable of various modifications and alternative forms, embodiments thereof are illustrated by way of example in the figures and will herein be described in detail. It should be understood, however, that there is no intent to limit example embodiments to the particular forms disclosed, but to the contrary, example embodiments are to cover all modifications, equivalents, and alternatives falling within the scope of the present invention.
The terminology used herein is for describing particular embodiments only and is not intended to be limiting of example embodiments. As used herein, the singular forms “a”, “an” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms “comprises”, “comprising”, “includes” and/or “including”, when used herein, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof.
Although the terms first, second, primary, secondary, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another. For example, but not limiting to, a first element could be termed a second element, and, similarly, a second element could be termed a first element, without departing from the scope of example embodiments. As used herein, the term “and/or” includes any, and all, combinations of one or more of the associated listed items.
Certain terminology may be used herein for the convenience of the reader only and is not to be taken as a limitation on the scope of the invention. For example, words such as “upper”, “lower”, “left”, “right”, “front”, “rear”, “top”, “bottom”, “horizontal”, “vertical”, “upstream”, “downstream”, “fore”, “aft”, and the like; merely describe the configuration shown in the figures. Indeed, the element or elements of an embodiment of the present invention may be oriented in any direction and the terminology, therefore, should be understood as encompassing such variations unless specified otherwise.
As discussed in detail below, the disclosed embodiments relate generally to gas turbine systems with exhaust gas recirculation (EGR), and particularly stoichiometric operation of the gas turbine systems using EGR. For example, the gas turbine systems may be configured to recirculate the exhaust gas along an exhaust recirculation path, stoichiometrically combust fuel and oxidant along with at least some of the recirculated exhaust gas, and capture the exhaust gas for use in various target systems. The recirculation of the exhaust gas along with stoichiometric combustion may help to increase the concentration level of carbon dioxide (CO2) in the exhaust gas, which can then be post treated to separate and purify the CO2 and nitrogen (N2) for use in various target systems. The gas turbine systems also may employ various exhaust gas processing (e.g., heat recovery, catalyst reactions, etc.) along the exhaust recirculation path, thereby increasing the concentration level of CO2, reducing concentration levels of other emissions (e.g., carbon monoxide, nitrogen oxides, and unburnt hydrocarbons), and increasing energy recovery (e.g., with heat recovery units). Furthermore, the gas turbine engines may be configured to combust the fuel and oxidant with one or more diffusion flames (e.g., using diffusion fuel nozzles), premix flames (e.g., using premix fuel nozzles), or any combination thereof. In certain embodiments, the diffusion flames may help to maintain stability and operation within certain limits for stoichiometric combustion, which in turn helps to increase production of CO2. For example, a gas turbine system operating with diffusion flames may enable a greater quantity of EGR, as compared to a gas turbine system operating with premix flames. In turn, the increased quantity of EGR helps to increase CO2 production. Possible target systems include pipelines, storage tanks, carbon sequestration systems, and hydrocarbon production systems, such as enhanced oil recovery (EOR) systems.
In certain embodiments, cooling flows may be used to cool probes (e.g., sensors) that are coupled to various components of a gas turbine engine, such as a compressor, a compressor discharge casing, a combustor, and a turbine. In operating conditions, the various components of the gas turbine engine may be in a high temperature environment. For example, the compressor outlet may have a temperature of about 250° C. to 350° C., and the turbine outlet may have a temperature of about 500° C. to 600° C. When the probes are coupled to the components that operate in the high temperature environment, cooling flows (e.g., streams of compressed air, carbon dioxide, and nitrogen) may be routed to directly or indirectly contact the probes to facilitate cooling of the probes. For example, the probes may include one or more cooling passages surrounding at least a part of the probes, and the cooling flows may be directed to flow through the one or more cooling passages to absorb heat from the probe (e.g., via convection). After absorbing heat from the probe, the cooling flows exiting the one or more cooling passages may have high temperatures (e.g., above 80° C.) and high velocities (e.g., above 60 m/s). The exit temperatures and/or the exit velocities of the cooling flows may be subject to various regulatory requirements or other requirements. For example, regulations may require that the exit temperature of a cooling flow that is released into the atmosphere is no greater than a threshold level, such as 80° C. Accordingly, without the disclosed embodiments, separate piping (or conduits, or flow lines) may be coupled to the exit of the cooling passage to direct the high temperature and high velocity exit cooling flows to a remote location to process and/or release to the atmosphere.
The present disclosure provides an ejector that may be coupled to an exit of a cooling passage of a probe coupled to various components of a gas turbine engine operating in high temperature environment. The ejector may be coupled to the exit of the cooling passage to receive the exit cooling flow. The exit cooling flow may then flow into an interior of the ejector via a nozzle, which is configured to constrict the exit cooling flow. The ejector also includes an opening fluidly coupled to the interior and configured to receive a coolant (e.g., ambient air). As the exit cooling flow passes and is constricted by the nozzle, the exit cooling flow may draw the coolant from the ambient environment (e.g., outside of the ejector) into the interior of the ejector. The coolant and the constricted exit cooling flow may mix in a mixing portion of the interior of the ejector. The mixture may then be discharged into the atmosphere as a discharge flow. Because the exit cooling flow mixes with the coolant within the ejector, the discharge flow may have a lower temperature than the cooling flow exiting the cooling passage of the probe. For example, the discharge flow may have a temperature lower than the regulatory threshold, such that the discharge flow may be released directly from the ejector into the atmosphere without separate piping and/or heat exchangers. In addition, the ejector may include design features, for example, the discharge outlet of the ejector may have a diameter that is greater than a diameter of the exit of the cooling passage, such that the discharge flow has a lower velocity than the cooling flow exiting the cooling passage of the probe. As such, by incorporating the ejector to the exit of the cooling flowing passage, in accordance with the present disclosure, separate piping that directs the exit outflow to a remote location may be eliminated, and the exit cooling flow may be directly released to the atmosphere (e.g., via the ejector in close proximity of the probe).
Accordingly, the EOR system 18 may include a fluid injection system 34, which has one or more tubulars 36 extending through a bore 38 in the earth 32 to the subterranean reservoir 20. For example, the EOR system 18 may route one or more fluids 40, such as gas, steam, water, chemicals, or any combination thereof, into the fluid injection system 34. For example, as discussed in further detail below, the EOR system 18 may be coupled to the turbine-based service system 14, such that the system 14 routes an exhaust gas 42 (e.g., substantially or entirely free of oxygen) to the EOR system 18 for use as the injection fluid 40. The fluid injection system 34 routes the fluid 40 (e.g., the exhaust gas 42) through the one or more tubulars 36 into the subterranean reservoir 20, as indicated by arrows 44. The injection fluid 40 enters the subterranean reservoir 20 through the tubular 36 at an offset distance 46 away from the tubular 28 of the oil/gas well 26. Accordingly, the injection fluid 40 displaces the oil/gas 48 disposed in the subterranean reservoir 20, and drives the oil/gas 48 up through the one or more tubulars 28 of the hydrocarbon production system 12, as indicated by arrows 50. As discussed in further detail below, the injection fluid 40 may include the exhaust gas 42 originating from the turbine-based service system 14, which is able to generate the exhaust gas 42 on-site as needed by the hydrocarbon production system 12. In other words, the turbine-based system 14 may simultaneously generate one or more services (e.g., electrical power, mechanical power, steam, water (e.g., desalinated water), and exhaust gas (e.g., substantially free of oxygen)) for use by the hydrocarbon production system 12, thereby reducing or eliminating the reliance on external sources of such services.
In the illustrated embodiment, the turbine-based service system 14 includes a stoichiometric exhaust gas recirculation (SEGR) gas turbine system 52 and an exhaust gas (EG) processing system 54. The gas turbine system 52 may be configured to operate in a stoichiometric combustion mode of operation (e.g., a stoichiometric control mode) and a non-stoichiometric combustion mode of operation (e.g., a non-stoichiometric control mode), such as a fuel-lean control mode or a fuel-rich control mode. In the stoichiometric control mode, the combustion generally occurs in a substantially stoichiometric ratio of a fuel and oxidant, thereby resulting in substantially stoichiometric combustion. In particular, stoichiometric combustion generally involves consuming substantially all of the fuel and oxidant in the combustion reaction, such that the products of combustion are substantially or entirely free of unburnt fuel and oxidant. One measure of stoichiometric combustion is the equivalence ratio, or phi (Φ), which is the ratio of the actual fuel/oxidant ratio relative to the stoichiometric fuel/oxidant ratio. An equivalence ratio of greater than 1.0 results in a fuel-rich combustion of the fuel and oxidant, whereas an equivalence ratio of less than 1.0 results in a fuel-lean combustion of the fuel and oxidant. In contrast, an equivalence ratio of 1.0 results in combustion that is neither fuel-rich nor fuel-lean, thereby substantially consuming all of the fuel and oxidant in the combustion reaction. In context of the disclosed embodiments, the term stoichiometric or substantially stoichiometric may refer to an equivalence ratio of approximately 0.95 to approximately 1.05. However, the disclosed embodiments may also include an equivalence ratio of 1.0 plus or minus 0.01, 0.02, 0.03, 0.04, 0.05, or more. Again, the stoichiometric combustion of fuel and oxidant in the turbine-based service system 14 may result in products of combustion or exhaust gas (e.g., 42) with substantially no unburnt fuel or oxidant remaining. For example, the exhaust gas 42 may have less than 1, 2, 3, 4, or 5 percent by volume of oxidant (e.g., oxygen), unburnt fuel or hydrocarbons (e.g., HCs), nitrogen oxides (e.g., NOX), carbon monoxide (CO), sulfur oxides (e.g., SOX), hydrogen, and other products of incomplete combustion. By further example, the exhaust gas 42 may have less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 200, 300, 400, 500, 1000, 2000, 3000, 4000, or 5000 parts per million by volume (ppmv) of oxidant (e.g., oxygen), unburnt fuel or hydrocarbons (e.g., HCs), nitrogen oxides (e.g., NOX), carbon monoxide (CO), sulfur oxides (e.g., SOX), hydrogen, and other products of incomplete combustion. However, the disclosed embodiments also may produce other ranges of residual fuel, oxidant, and other emissions levels in the exhaust gas 42. As used herein, the terms emissions, emissions levels, and emissions targets may refer to concentration levels of certain products of combustion (e.g., NOX, CO, SOX, O2, N2, H2, HCs, etc.), which may be present in recirculated gas streams, vented gas streams (e.g., exhausted into the atmosphere), and gas streams used in various target systems (e.g., the hydrocarbon production system 12).
Although the SEGR gas turbine system 52 and the EG processing system 54 may include a variety of components in different embodiments, the illustrated EG processing system 54 includes a heat recovery steam generator (HRSG) 56 and an exhaust gas recirculation (EGR) system 58, which receive and process an exhaust gas 60 originating from the SEGR gas turbine system 52. The HRSG 56 may include one or more heat exchangers, condensers, and various heat recovery equipment, which collectively function to transfer heat from the exhaust gas 60 to a stream of water, thereby generating steam 62. The steam 62 may be used in one or more steam turbines, the EOR system 18, or any other portion of the hydrocarbon production system 12. For example, the HRSG 56 may generate low pressure, medium pressure, and/or high pressure steam 62, which may be selectively applied to low, medium, and high pressure steam turbine stages, or different applications of the EOR system 18. In addition to the steam 62, a treated water 64, such as a desalinated water, may be generated by the HRSG 56, the EGR system 58, and/or another portion of the EG processing system 54 or the SEGR gas turbine system 52. The treated water 64 (e.g., desalinated water) may be particularly useful in areas with water shortages, such as inland or desert regions. The treated water 64 may be generated, at least in part, due to the large volume of air driving combustion of fuel within the SEGR gas turbine system 52. While the on-site generation of steam 62 and water 64 may be beneficial in many applications (including the hydrocarbon production system 12), the on-site generation of exhaust gas 42, 60 may be particularly beneficial for the EOR system 18, due to its low oxygen content, high pressure, and heat derived from the SEGR gas turbine system 52. Accordingly, the HRSG 56, the EGR system 58, and/or another portion of the EG processing system 54 may output or recirculate an exhaust gas 66 into the SEGR gas turbine system 52, while also routing the exhaust gas 42 to the EOR system 18 for use with the hydrocarbon production system 12. Likewise, the exhaust gas 42 may be extracted directly from the SEGR gas turbine system 52 (i.e., without passing through the EG processing system 54) for use in the EOR system 18 of the hydrocarbon production system 12.
The exhaust gas recirculation is handled by the EGR system 58 of the EG processing system 54. For example, the EGR system 58 includes one or more conduits, valves, blowers, exhaust gas treatment systems (e.g., filters, particulate removal units, gas separation units, gas purification units, heat exchangers, heat recovery units, moisture removal units, catalyst units, chemical injection units, or any combination thereof), and controls to recirculate the exhaust gas along an exhaust gas circulation path from an output (e.g., discharged exhaust gas 60) to an input (e.g., intake exhaust gas 66) of the SEGR gas turbine system 52. In the illustrated embodiment, the SEGR gas turbine system 52 intakes the exhaust gas 66 into a compressor section having one or more compressors, thereby compressing the exhaust gas 66 for use in a combustor section along with an intake of an oxidant 68 and one or more fuels 70. The oxidant 68 may include ambient air, pure oxygen, oxygen-enriched air, oxygen-reduced air, oxygen-nitrogen mixtures, or any suitable oxidant that facilitates combustion of the fuel 70. The fuel 70 may include one or more gas fuels, liquid fuels, or any combination thereof. For example, the fuel 70 may include natural gas, liquefied natural gas (LNG), syngas, methane, ethane, propane, butane, naphtha, kerosene, diesel fuel, ethanol, methanol, biofuel, or any combination thereof.
The SEGR gas turbine system 52 mixes and combusts the exhaust gas 66, the oxidant 68, and the fuel 70 in the combustor section, thereby generating hot combustion gases or exhaust gas 60 to drive one or more turbine stages in a turbine section. In certain embodiments, each combustor in the combustor section includes one or more premix fuel nozzles, one or more diffusion fuel nozzles, or any combination thereof. For example, each premix fuel nozzle may be configured to mix the oxidant 68 and the fuel 70 internally within the fuel nozzle and/or partially upstream of the fuel nozzle, thereby injecting an oxidant-fuel mixture from the fuel nozzle into the combustion zone for a premixed combustion (e.g., a premixed flame). By further example, each diffusion fuel nozzle may be configured to isolate the flows of oxidant 68 and fuel 70 within the fuel nozzle, thereby separately injecting the oxidant 68 and the fuel 70 from the fuel nozzle into the combustion zone for diffusion combustion (e.g., a diffusion flame). In particular, the diffusion combustion provided by the diffusion fuel nozzles delays mixing of the oxidant 68 and the fuel 70 until the point of initial combustion, i.e., the flame region. In embodiments employing the diffusion fuel nozzles, the diffusion flame may provide increased flame stability, because the diffusion flame generally forms at the point of stoichiometry between the separate streams of oxidant 68 and fuel 70 (i.e., as the oxidant 68 and fuel 70 are mixing). In certain embodiments, one or more diluents (e.g., the exhaust gas 60, steam, nitrogen, or another inert gas) may be pre-mixed with the oxidant 68, the fuel 70, or both, in either the diffusion fuel nozzle or the premix fuel nozzle. In addition, one or more diluents (e.g., the exhaust gas 60, steam, nitrogen, or another inert gas) may be injected into the combustor at or downstream from the point of combustion within each combustor. The use of these diluents may help temper the flame (e.g., premix flame or diffusion flame), thereby helping to reduce NOX emissions, such as nitrogen monoxide (NO) and nitrogen dioxide (NO2). Regardless of the type of flame, the combustion produces hot combustion gases or exhaust gas 60 to drive one or more turbine stages. As each turbine stage is driven by the exhaust gas 60, the SEGR gas turbine system 52 generates a mechanical power 72 and/or an electrical power 74 (e.g., via an electrical generator). The system 52 also outputs the exhaust gas 60, and may further output water 64. Again, the water 64 may be a treated water, such as a desalinated water, which may be useful in a variety of applications on-site or off-site.
Exhaust extraction is also provided by the SEGR gas turbine system 52 using one or more extraction points 76. For example, the illustrated embodiment includes an exhaust gas (EG) supply system 78 having an exhaust gas (EG) extraction system 80 and an exhaust gas (EG) treatment system 82, which receive exhaust gas 42 from the extraction points 76, treat the exhaust gas 42, and then supply or distribute the exhaust gas 42 to various target systems. The target systems may include the EOR system 18 and/or other systems, such as a pipeline 86, a storage tank 88, or a carbon sequestration system 90. The EG extraction system 80 may include one or more conduits, valves, controls, and flow separations, which facilitate isolation of the exhaust gas 42 from the oxidant 68, the fuel 70, and other contaminants, while also controlling the temperature, pressure, and flow rate of the extracted exhaust gas 42. The EG treatment system 82 may include one or more heat exchangers (e.g., heat recovery units such as heat recovery steam generators, condensers, coolers, or heaters), catalyst systems (e.g., oxidation catalyst systems), particulate and/or water removal systems (e.g., gas dehydration units, inertial separators, coalescing filters, water impermeable filters, and other filters), chemical injection systems, solvent based treatment systems (e.g., absorbers, flash tanks, etc.), carbon capture systems, gas separation systems, gas purification systems, and/or a solvent based treatment system, exhaust gas compressors, any combination thereof. These subsystems of the EG treatment system 82 enable control of the temperature, pressure, flow rate, moisture content (e.g., amount of water removal), particulate content (e.g., amount of particulate removal), and gas composition (e.g., percentage of CO2, N2, etc.).
The extracted exhaust gas 42 is treated by one or more subsystems of the EG treatment system 82, depending on the target system. For example, the EG treatment system 82 may direct all or part of the exhaust gas 42 through a carbon capture system, a gas separation system, a gas purification system, and/or a solvent based treatment system, which is controlled to separate and purify a carbonaceous gas (e.g., carbon dioxide) 92 and/or nitrogen (N2) 94 for use in the various target systems. For example, embodiments of the EG treatment system 82 may perform gas separation and purification to produce a plurality of different streams 95 of exhaust gas 42, such as a first stream 96, a second stream 97, and a third stream 98. The first stream 96 may have a first composition that is rich in carbon dioxide and/or lean in nitrogen (e.g., a CO2 rich, N2 lean stream). The second stream 97 may have a second composition that has intermediate concentration levels of carbon dioxide and/or nitrogen (e.g., intermediate concentration CO2, N2 stream). The third stream 98 may have a third composition that is lean in carbon dioxide and/or rich in nitrogen (e.g., a CO2 lean, N2 rich stream). Each stream 95 (e.g., 96, 97, and 98) may include a gas dehydration unit, a filter, a gas compressor, or any combination thereof, to facilitate delivery of the stream 95 to a target system. In certain embodiments, the CO2 rich, N2 lean stream 96 may have a CO2 purity or concentration level of greater than approximately 70, 75, 80, 85, 90, 95, 96, 97, 98, or 99 percent by volume, and a N2 purity or concentration level of less than approximately 1, 2, 3, 4, 5, 10, 15, 20, 25, or 30 percent by volume. In contrast, the CO2 lean, N2 rich stream 98 may have a CO2 purity or concentration level of less than approximately 1, 2, 3, 4, 5, 10, 15, 20, 25, or 30 percent by volume, and a N2 purity or concentration level of greater than approximately 70, 75, 80, 85, 90, 95, 96, 97, 98, or 99 percent by volume. The intermediate concentration CO2, N2 stream 97 may have a CO2 purity or concentration level and/or a N2 purity or concentration level of between approximately 30 to 70, 35 to 65, 40 to 60, or 45 to 55 percent by volume. Although the foregoing ranges are merely non-limiting examples, the CO2 rich, N2 lean stream 96 and the CO2 lean, N2 rich stream 98 may be particularly well suited for use with the EOR system 18 and the other systems 84. However, any of these rich, lean, or intermediate concentration CO2 streams 95 may be used, alone or in various combinations, with the EOR system 18 and the other systems 84. For example, the EOR system 18 and the other systems 84 (e.g., the pipeline 86, storage tank 88, and the carbon sequestration system 90) each may receive one or more CO2 rich, N2 lean streams 96, one or more CO2 lean, N2 rich streams 98, one or more intermediate concentration CO2, N2 streams 97, and one or more untreated exhaust gas 42 streams (i.e., bypassing the EG treatment system 82).
The EG extraction system 80 extracts the exhaust gas 42 at one or more extraction points 76 along the compressor section, the combustor section, and/or the turbine section, such that the exhaust gas 42 may be used in the EOR system 18 and other systems 84 at suitable temperatures and pressures. The EG extraction system 80 and/or the EG treatment system 82 also may circulate fluid flows (e.g., exhaust gas 42) to and from the EG processing system 54. For example, a portion of the exhaust gas 42 passing through the EG processing system 54 may be extracted by the EG extraction system 80 for use in the EOR system 18 and the other systems 84. In certain embodiments, the EG supply system 78 and the EG processing system 54 may be independent or integral with one another, and thus may use independent or common subsystems. For example, the EG treatment system 82 may be used by both the EG supply system 78 and the EG processing system 54. Exhaust gas 42 extracted from the EG processing system 54 may undergo multiple stages of gas treatment, such as one or more stages of gas treatment in the EG processing system 54 followed by one or more additional stages of gas treatment in the EG treatment system 82.
At each extraction point 76, the extracted exhaust gas 42 may be substantially free of oxidant 68 and fuel 70 (e.g., unburnt fuel or hydrocarbons) due to substantially stoichiometric combustion and/or gas treatment in the EG processing system 54. Furthermore, depending on the target system, the extracted exhaust gas 42 may undergo further treatment in the EG treatment system 82 of the EG supply system 78, thereby further reducing any residual oxidant 68, fuel 70, or other undesirable products of combustion. For example, either before or after treatment in the EG treatment system 82, the extracted exhaust gas 42 may have less than 1, 2, 3, 4, or 5 percent by volume of oxidant (e.g., oxygen), unburnt fuel or hydrocarbons (e.g., HCs), nitrogen oxides (e.g., NOX), carbon monoxide (CO), sulfur oxides (e.g., SOX), hydrogen, and other products of incomplete combustion. By further example, either before or after treatment in the EG treatment system 82, the extracted exhaust gas 42 may have less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 200, 300, 400, 500, 1000, 2000, 3000, 4000, or 5000 parts per million by volume (ppmv) of oxidant (e.g., oxygen), unburnt fuel or hydrocarbons (e.g., HCs), nitrogen oxides (e.g., NOX), carbon monoxide (CO), sulfur oxides (e.g., SOX), hydrogen, and other products of incomplete combustion. Thus, the exhaust gas 42 is particularly well suited for use with the EOR system 18.
The EGR operation of the turbine system 52 specifically enables the exhaust extraction at a multitude of locations 76. For example, the compressor section of the system 52 may be used to compress the exhaust gas 66 without any oxidant 68 (i.e., only compression of the exhaust gas 66), such that a substantially oxygen-free exhaust gas 42 may be extracted from the compressor section and/or the combustor section prior to entry of the oxidant 68 and the fuel 70. The extraction points 76 may be located at interstage ports between adjacent compressor stages, at ports along the compressor discharge casing, at ports along each combustor in the combustor section, or any combination thereof. In certain embodiments, the exhaust gas 66 may not mix with the oxidant 68 and fuel 70 until it reaches the head end portion and/or fuel nozzles of each combustor in the combustor section. Furthermore, one or more flow separators (e.g., walls, dividers, baffles, or the like) may be used to isolate the oxidant 68 and the fuel 70 from the extraction points 76. With these flow separators, the extraction points 76 may be disposed directly along a wall of each combustor in the combustor section.
Once the exhaust gas 66, oxidant 68, and fuel 70 flow through the head end portion (e.g., through fuel nozzles) into the combustion portion (e.g., combustion chamber) of each combustor, the SEGR gas turbine system 52 is controlled to provide a substantially stoichiometric combustion of the exhaust gas 66, oxidant 68, and fuel 70. For example, the system 52 may maintain an equivalence ratio of approximately 0.95 to approximately 1.05. As a result, the products of combustion of the mixture of exhaust gas 66, oxidant 68, and fuel 70 in each combustor is substantially free of oxygen and unburnt fuel. Thus, the products of combustion (or exhaust gas) may be extracted from the turbine section of the SEGR gas turbine system 52 for use as the exhaust gas 42 routed to the EOR system 18. Along the turbine section, the extraction points 76 may be located at any turbine stage, such as interstage ports between adjacent turbine stages. Thus, using any of the foregoing extraction points 76, the turbine-based service system 14 may generate, extract, and deliver the exhaust gas 42 to the hydrocarbon production system 12 (e.g., the EOR system 18) for use in the production of oil/gas 48 from the subterranean reservoir 20.
The SEGR gas turbine system 52 produces the exhaust gas 42, 60, which may be substantially free of oxygen, and routes this exhaust gas 42, 60 to the EG processing system 54 and/or the EG supply system 78. The EG supply system 78 may treat and delivery the exhaust gas 42 (e.g., streams 95) to the hydrocarbon production system 12 and/or the other systems 84. As discussed above, the EG processing system 54 may include the HRSG 56 and the EGR system 58. The HRSG 56 may include one or more heat exchangers, condensers, and various heat recovery equipment, which may be used to recover or transfer heat from the exhaust gas 60 to water 108 to generate the steam 62 for driving the steam turbine 104. Similar to the SEGR gas turbine system 52, the steam turbine 104 may drive one or more loads or machinery 106, thereby generating the mechanical power 72 and the electrical power 74. In the illustrated embodiment, the SEGR gas turbine system 52 and the steam turbine 104 are arranged in tandem to drive the same machinery 106. However, in other embodiments, the SEGR gas turbine system 52 and the steam turbine 104 may separately drive different machinery 106 to independently generate mechanical power 72 and/or electrical power 74. As the steam turbine 104 is driven by the steam 62 from the HRSG 56, the steam 62 gradually decreases in temperature and pressure. Accordingly, the steam turbine 104 recirculates the used steam 62 and/or water 108 back into the HRSG 56 for additional steam generation via heat recovery from the exhaust gas 60. In addition to steam generation, the HRSG 56, the EGR system 58, and/or another portion of the EG processing system 54 may produce the water 64, the exhaust gas 42 for use with the hydrocarbon production system 12, and the exhaust gas 66 for use as an input into the SEGR gas turbine system 52. For example, the water 64 may be a treated water 64, such as a desalinated water for use in other applications. The desalinated water may be particularly useful in regions of low water availability. Regarding the exhaust gas 60, embodiments of the EG processing system 54 may be configured to recirculate the exhaust gas 60 through the EGR system 58 with or without passing the exhaust gas 60 through the HRSG 56.
In the illustrated embodiment, the SEGR gas turbine system 52 has an exhaust recirculation path 110, which extends from an exhaust outlet to an exhaust inlet of the system 52. Along the path 110, the exhaust gas 60 passes through the EG processing system 54, which includes the HRSG 56 and the EGR system 58 in the illustrated embodiment. The EGR system 58 may include one or more conduits, valves, blowers, gas treatment systems (e.g., filters, particulate removal units, gas separation units, gas purification units, heat exchangers, heat recovery units such as heat recovery steam generators, moisture removal units, catalyst units, chemical injection units, or any combination thereof) in series and/or parallel arrangements along the path 110. In other words, the EGR system 58 may include any flow control components, pressure control components, temperature control components, moisture control components, and gas composition control components along the exhaust recirculation path 110 between the exhaust outlet and the exhaust inlet of the system 52. Accordingly, in embodiments with the HRSG 56 along the path 110, the HRSG 56 may be considered a component of the EGR system 58. However, in certain embodiments, the HRSG 56 may be disposed along an exhaust path independent from the exhaust recirculation path 110. Regardless of whether the HRSG 56 is along a separate path or a common path with the EGR system 58, the HRSG 56 and the EGR system 58 intake the exhaust gas 60 and output either the recirculated exhaust gas 66, the exhaust gas 42 for use with the EG supply system 78 (e.g., for the hydrocarbon production system 12 and/or other systems 84), or another output of exhaust gas. Again, the SEGR gas turbine system 52 intakes, mixes, and stoichiometrically combusts the exhaust gas 66, the oxidant 68, and the fuel 70 (e.g., premixed and/or diffusion flames) to produce a substantially oxygen-free and fuel-free exhaust gas 60 for distribution to the EG processing system 54, the hydrocarbon production system 12, or other systems 84.
As noted above with reference to
The quantity, quality, and flow of the exhaust gas 42 and/or the steam 62 may be controlled by the control system 100. The control system 100 may be dedicated entirely to the turbine-based service system 14, or the control system 100 may optionally also provide control (or at least some data to facilitate control) for the hydrocarbon production system 12 and/or other systems 84. In the illustrated embodiment, the control system 100 includes a controller 118 having a processor 120, a memory 122, a steam turbine control 124, a SEGR gas turbine system control 126, and a machinery control 128. The processor 120 may include a single processor or two or more redundant processors, such as triple redundant processors for control of the turbine-based service system 14. The memory 122 may include volatile and/or non-volatile memory. For example, the memory 122 may include one or more hard drives, flash memory, read-only memory, random access memory, or any combination thereof. The controls 124, 126, and 128 may include software and/or hardware controls. For example, the controls 124, 126, and 128 may include various instructions or code stored on the memory 122 and executable by the processor 120. The control 124 is configured to control operation of the steam turbine 104, the SEGR gas turbine system control 126 is configured to control the system 52, and the machinery control 128 is configured to control the machinery 106. Thus, the controller 118 (e.g., controls 124, 126, and 128) may be configured to coordinate various sub-systems of the turbine-based service system 14 to provide a suitable stream of the exhaust gas 42 to the hydrocarbon production system 12.
In certain embodiments of the control system 100, each element (e.g., system, subsystem, and component) illustrated in the drawings or described herein includes (e.g., directly within, upstream, or downstream of such element) one or more industrial control features, such as sensors and control devices, which are communicatively coupled with one another over an industrial control network along with the controller 118. For example, the control devices associated with each element may include a dedicated device controller (e.g., including a processor, memory, and control instructions), one or more actuators, valves, switches, and industrial control equipment, which enable control based on sensor feedback 130, control signals from the controller 118, control signals from a user, or any combination thereof. Thus, any of the control functionality described herein may be implemented with control instructions stored and/or executable by the controller 118, dedicated device controllers associated with each element, or a combination thereof.
In order to facilitate such control functionality, the control system 100 includes one or more sensors distributed throughout the system 10 to obtain the sensor feedback 130 for use in execution of the various controls, e.g., the controls 124, 126, and 128. For example, the sensor feedback 130 may be obtained from sensors distributed throughout the SEGR gas turbine system 52, the machinery 106, the EG processing system 54, the steam turbine 104, the hydrocarbon production system 12, or any other components throughout the turbine-based service system 14 or the hydrocarbon production system 12. For example, the sensor feedback 130 may include temperature feedback, pressure feedback, flow rate feedback, flame temperature feedback, combustion dynamics feedback, intake oxidant composition feedback, intake fuel composition feedback, exhaust composition feedback, the output level of mechanical power 72, the output level of electrical power 74, the output quantity of the exhaust gas 42, 60, the output quantity or quality of the water 64, or any combination thereof. For example, the sensor feedback 130 may include a composition of the exhaust gas 42, 60 to facilitate stoichiometric combustion in the SEGR gas turbine system 52. For example, the sensor feedback 130 may include feedback from one or more intake oxidant sensors along an oxidant supply path of the oxidant 68, one or more intake fuel sensors along a fuel supply path of the fuel 70, and one or more exhaust emissions sensors disposed along the exhaust recirculation path 110 and/or within the SEGR gas turbine system 52. The intake oxidant sensors, intake fuel sensors, and exhaust emissions sensors may include temperature sensors, pressure sensors, flow rate sensors, and composition sensors. The emissions sensors may includes sensors for nitrogen oxides (e.g., NOX sensors), carbon oxides (e.g., CO sensors and CO2 sensors), sulfur oxides (e.g., SOX sensors), hydrogen (e.g., H2 sensors), oxygen (e.g., O2 sensors), unburnt hydrocarbons (e.g., HC sensors), or other products of incomplete combustion, or any combination thereof.
Using this feedback 130, the control system 100 may adjust (e.g., increase, decrease, or maintain) the intake flow of exhaust gas 66, oxidant 68, and/or fuel 70 into the SEGR gas turbine system 52 (among other operational parameters) to maintain the equivalence ratio within a suitable range, e.g., between approximately 0.95 to approximately 1.05, between approximately 0.95 to approximately 1.0, between approximately 1.0 to approximately 1.05, or substantially at 1.0. For example, the control system 100 may analyze the feedback 130 to monitor the exhaust emissions (e.g., concentration levels of nitrogen oxides, carbon oxides such as CO and CO2, sulfur oxides, hydrogen, oxygen, unburnt hydrocarbons, and other products of incomplete combustion) and/or determine the equivalence ratio, and then control one or more components to adjust the exhaust emissions (e.g., concentration levels in the exhaust gas 42) and/or the equivalence ratio. The controlled components may include any of the components illustrated and described with reference to the drawings, including but not limited to, valves along the supply paths for the oxidant 68, the fuel 70, and the exhaust gas 66; an oxidant compressor, a fuel pump, or any components in the EG processing system 54; any components of the SEGR gas turbine system 52, or any combination thereof. The controlled components may adjust (e.g., increase, decrease, or maintain) the flow rates, temperatures, pressures, or percentages (e.g., equivalence ratio) of the oxidant 68, the fuel 70, and the exhaust gas 66 that combust within the SEGR gas turbine system 52. The controlled components also may include one or more gas treatment systems, such as catalyst units (e.g., oxidation catalyst units), supplies for the catalyst units (e.g., oxidation fuel, heat, electricity, etc.), gas purification and/or separation units (e.g., solvent based separators, absorbers, flash tanks, etc.), and filtration units. The gas treatment systems may help reduce various exhaust emissions along the exhaust recirculation path 110, a vent path (e.g., exhausted into the atmosphere), or an extraction path to the EG supply system 78.
In certain embodiments, the control system 100 may analyze the feedback 130 and control one or more components to maintain or reduce emissions levels (e.g., concentration levels in the exhaust gas 42, 60, 95) to a target range, such as less than approximately 10, 20, 30, 40, 50, 100, 200, 300, 400, 500, 1000, 2000, 3000, 4000, 5000, or 10000 parts per million by volume (ppmv). These target ranges may be the same or different for each of the exhaust emissions, e.g., concentration levels of nitrogen oxides, carbon monoxide, sulfur oxides, hydrogen, oxygen, unburnt hydrocarbons, and other products of incomplete combustion. For example, depending on the equivalence ratio, the control system 100 may selectively control exhaust emissions (e.g., concentration levels) of oxidant (e.g., oxygen) within a target range of less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 250, 500, 750, or 1000 ppmv; carbon monoxide (CO) within a target range of less than approximately 20, 50, 100, 200, 500, 1000, 2500, or 5000 ppmv; and nitrogen oxides (NOX) within a target range of less than approximately 50, 100, 200, 300, 400, or 500 ppmv. In certain embodiments operating with a substantially stoichiometric equivalence ratio, the control system 100 may selectively control exhaust emissions (e.g., concentration levels) of oxidant (e.g., oxygen) within a target range of less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, or 100 ppmv; and carbon monoxide (CO) within a target range of less than approximately 500, 1000, 2000, 3000, 4000, or 5000 ppmv. In certain embodiments operating with a fuel-lean equivalence ratio (e.g., between approximately 0.95 to 1.0), the control system 100 may selectively control exhaust emissions (e.g., concentration levels) of oxidant (e.g., oxygen) within a target range of less than approximately 500, 600, 700, 800, 900, 1000, 1100, 1200, 1300, 1400, or 1500 ppmv; carbon monoxide (CO) within a target range of less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 150, or 200 ppmv; and nitrogen oxides (e.g., NOX) within a target range of less than approximately 50, 100, 150, 200, 250, 300, 350, or 400 ppmv. The foregoing target ranges are merely examples, and are not intended to limit the scope of the disclosed embodiments.
The control system 100 also may be coupled to a local interface 132 and a remote interface 134. For example, the local interface 132 may include a computer workstation disposed on-site at the turbine-based service system 14 and/or the hydrocarbon production system 12. In contrast, the remote interface 134 may include a computer workstation disposed off-site from the turbine-based service system 14 and the hydrocarbon production system 12, such as through an internet connection. These interfaces 132 and 134 facilitate monitoring and control of the turbine-based service system 14, such as through one or more graphical displays of sensor feedback 130, operational parameters, and so forth.
Again, as noted above, the controller 118 includes a variety of controls 124, 126, and 128 to facilitate control of the turbine-based service system 14. The steam turbine control 124 may receive the sensor feedback 130 and output control commands to facilitate operation of the steam turbine 104. For example, the steam turbine control 124 may receive the sensor feedback 130 from the HRSG 56, the machinery 106, temperature and pressure sensors along a path of the steam 62, temperature and pressure sensors along a path of the water 108, and various sensors indicative of the mechanical power 72 and the electrical power 74. Likewise, the SEGR gas turbine system control 126 may receive sensor feedback 130 from one or more sensors disposed along the SEGR gas turbine system 52, the machinery 106, the EG processing system 54, or any combination thereof. For example, the sensor feedback 130 may be obtained from temperature sensors, pressure sensors, clearance sensors, vibration sensors, flame sensors, fuel composition sensors, exhaust gas composition sensors, or any combination thereof, disposed within or external to the SEGR gas turbine system 52. Finally, the machinery control 128 may receive sensor feedback 130 from various sensors associated with the mechanical power 72 and the electrical power 74, as well as sensors disposed within the machinery 106. Each of these controls 124, 126, and 128 uses the sensor feedback 130 to improve operation of the turbine-based service system 14.
In the illustrated embodiment, the SEGR gas turbine system control 126 may execute instructions to control the quantity and quality of the exhaust gas 42, 60, 95 in the EG processing system 54, the EG supply system 78, the hydrocarbon production system 12, and/or the other systems 84. For example, the SEGR gas turbine system control 126 may maintain a level of oxidant (e.g., oxygen) and/or unburnt fuel in the exhaust gas 60 below a threshold suitable for use with the exhaust gas injection EOR system 112. In certain embodiments, the threshold levels may be less than 1, 2, 3, 4, or 5 percent of oxidant (e.g., oxygen) and/or unburnt fuel by volume of the exhaust gas 42, 60; or the threshold levels of oxidant (e.g., oxygen) and/or unburnt fuel (and other exhaust emissions) may be less than approximately 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 200, 300, 400, 500, 1000, 2000, 3000, 4000, or 5000 parts per million by volume (ppmv) in the exhaust gas 42, 60. By further example, in order to achieve these low levels of oxidant (e.g., oxygen) and/or unburnt fuel, the SEGR gas turbine system control 126 may maintain an equivalence ratio for combustion in the SEGR gas turbine system 52 between approximately 0.95 and approximately 1.05. The SEGR gas turbine system control 126 also may control the EG extraction system 80 and the EG treatment system 82 to maintain the temperature, pressure, flow rate, and gas composition of the exhaust gas 42, 60, 95 within suitable ranges for the exhaust gas injection EOR system 112, the pipeline 86, the storage tank 88, and the carbon sequestration system 90. As discussed above, the EG treatment system 82 may be controlled to purify and/or separate the exhaust gas 42 into one or more gas streams 95, such as the CO2 rich, N2 lean stream 96, the intermediate concentration CO2, N2 stream 97, and the CO2 lean, N2 rich stream 98. In addition to controls for the exhaust gas 42, 60, and 95, the controls 124, 126, and 128 may execute one or more instructions to maintain the mechanical power 72 within a suitable power range, or maintain the electrical power 74 within a suitable frequency and power range.
The fuel nozzles 164 may include any combination of premix fuel nozzles 164 (e.g., configured to premix the oxidant 68 and fuel 70 for generation of an oxidant/fuel premix flame) and/or diffusion fuel nozzles 164 (e.g., configured to inject separate flows of the oxidant 68 and fuel 70 for generation of an oxidant/fuel diffusion flame). Embodiments of the premix fuel nozzles 164 may include swirl vanes, mixing chambers, or other features to internally mix the oxidant 68 and fuel 70 within the nozzles 164, prior to injection and combustion in the combustion chamber 168. The premix fuel nozzles 164 also may receive at least some partially mixed oxidant 68 and fuel 70. In certain embodiments, each diffusion fuel nozzle 164 may isolate flows of the oxidant 68 and the fuel 70 until the point of injection, while also isolating flows of one or more diluents (e.g., the exhaust gas 66, steam, nitrogen, or another inert gas) until the point of injection. In other embodiments, each diffusion fuel nozzle 164 may isolate flows of the oxidant 68 and the fuel 70 until the point of injection, while partially mixing one or more diluents (e.g., the exhaust gas 66, steam, nitrogen, or another inert gas) with the oxidant 68 and/or the fuel 70 prior to the point of injection. In addition, one or more diluents (e.g., the exhaust gas 66, steam, nitrogen, or another inert gas) may be injected into the combustor (e.g., into the hot products of combustion) either at or downstream from the combustion zone, thereby helping to reduce the temperature of the hot products of combustion and reduce emissions of NOX (e.g., NO and NO2). Regardless of the type of fuel nozzle 164, the SEGR gas turbine system 52 may be controlled to provide substantially stoichiometric combustion of the oxidant 68 and fuel 70.
In diffusion combustion embodiments using the diffusion fuel nozzles 164, the fuel 70 and oxidant 68 generally do not mix upstream from the diffusion flame, but rather the fuel 70 and oxidant 68 mix and react directly at the flame surface and/or the flame surface exists at the location of mixing between the fuel 70 and oxidant 68. In particular, the fuel 70 and oxidant 68 separately approach the flame surface (or diffusion boundary/interface), and then diffuse (e.g., via molecular and viscous diffusion) along the flame surface (or diffusion boundary/interface) to generate the diffusion flame. It is noteworthy that the fuel 70 and oxidant 68 may be at a substantially stoichiometric ratio along this flame surface (or diffusion boundary/interface), which may result in a greater flame temperature (e.g., a peak flame temperature) along this flame surface. The stoichiometric fuel/oxidant ratio generally results in a greater flame temperature (e.g., a peak flame temperature), as compared with a fuel-lean or fuel-rich fuel/oxidant ratio. As a result, the diffusion flame may be substantially more stable than a premix flame, because the diffusion of fuel 70 and oxidant 68 helps to maintain a stoichiometric ratio (and greater temperature) along the flame surface. Although greater flame temperatures can also lead to greater exhaust emissions, such as NOX emissions, the disclosed embodiments use one or more diluents to help control the temperature and emissions while still avoiding any premixing of the fuel 70 and oxidant 68. For example, the disclosed embodiments may introduce one or more diluents separate from the fuel 70 and oxidant 68 (e.g., after the point of combustion and/or downstream from the diffusion flame), thereby helping to reduce the temperature and reduce the emissions (e.g., NOX emissions) produced by the diffusion flame.
In operation, as illustrated, the compressor section 152 receives and compresses the exhaust gas 66 from the EG processing system 54, and outputs a compressed exhaust gas 170 to each of the combustors 160 in the combustor section 154. Upon combustion of the fuel 60, oxidant 68, and exhaust gas 170 within each combustor 160, additional exhaust gas or products of combustion 172 (i.e., combustion gas) is routed into the turbine section 156. Similar to the compressor section 152, the turbine section 156 includes one or more turbines or turbine stages 174, which may include a series of rotary turbine blades. These turbine blades are then driven by the products of combustion 172 generated in the combustor section 154, thereby driving rotation of a shaft 176 coupled to the machinery 106. Again, the machinery 106 may include a variety of equipment coupled to either end of the SEGR gas turbine system 52, such as machinery 106, 178 coupled to the turbine section 156 and/or machinery 106, 180 coupled to the compressor section 152. In certain embodiments, the machinery 106, 178, 180 may include one or more electrical generators, oxidant compressors for the oxidant 68, fuel pumps for the fuel 70, gear boxes, or additional drives (e.g. steam turbine 104, electrical motor, etc.) coupled to the SEGR gas turbine system 52. Non-limiting examples are discussed in further detail below with reference to TABLE 1. As illustrated, the turbine section 156 outputs the exhaust gas 60 to recirculate along the exhaust recirculation path 110 from an exhaust outlet 182 of the turbine section 156 to an exhaust inlet 184 into the compressor section 152. Along the exhaust recirculation path 110, the exhaust gas 60 passes through the EG processing system 54 (e.g., the HRSG 56 and/or the EGR system 58) as discussed in detail above.
Again, each combustor 160 in the combustor section 154 receives, mixes, and stoichiometrically combusts the compressed exhaust gas 170, the oxidant 68, and the fuel 70 to produce the additional exhaust gas or products of combustion 172 to drive the turbine section 156. In certain embodiments, the oxidant 68 is compressed by an oxidant compression system 186, such as a main oxidant compression (MOC) system (e.g., a main air compression (MAC) system) having one or more oxidant compressors (MOCs). The oxidant compression system 186 includes an oxidant compressor 188 coupled to a drive 190. For example, the drive 190 may include an electric motor, a combustion engine, or any combination thereof. In certain embodiments, the drive 190 may be a turbine engine, such as the gas turbine engine 150. Accordingly, the oxidant compression system 186 may be an integral part of the machinery 106. In other words, the compressor 188 may be directly or indirectly driven by the mechanical power 72 supplied by the shaft 176 of the gas turbine engine 150. In such an embodiment, the drive 190 may be excluded, because the compressor 188 relies on the power output from the turbine engine 150. However, in certain embodiments employing more than one oxidant compressor is employed, a first oxidant compressor (e.g., a low pressure (LP) oxidant compressor) may be driven by the drive 190 while the shaft 176 drives a second oxidant compressor (e.g., a high pressure (HP) oxidant compressor), or vice versa. For example, in another embodiment, the HP MOC is driven by the drive 190 and the LP oxidant compressor is driven by the shaft 176. In the illustrated embodiment, the oxidant compression system 186 is separate from the machinery 106. In each of these embodiments, the compression system 186 compresses and supplies the oxidant 68 to the fuel nozzles 164 and the combustors 160. Accordingly, some or all of the machinery 106, 178, 180 may be configured to increase the operational efficiency of the compression system 186 (e.g., the compressor 188 and/or additional compressors).
The variety of components of the machinery 106, indicated by element numbers 106A, 106B, 106C, 106D, 106E, and 106F, may be disposed along the line of the shaft 176 and/or parallel to the line of the shaft 176 in one or more series arrangements, parallel arrangements, or any combination of series and parallel arrangements. For example, the machinery 106, 178, 180 (e.g., 106A through 106F) may include any series and/or parallel arrangement, in any order, of: one or more gearboxes (e.g., parallel shaft, epicyclic gearboxes), one or more compressors (e.g., oxidant compressors, booster compressors such as EG booster compressors), one or more power generation units (e.g., electrical generators), one or more drives (e.g., steam turbine engines, electrical motors), heat exchange units (e.g., direct or indirect heat exchangers), clutches, or any combination thereof. The compressors may include axial compressors, radial or centrifugal compressors, or any combination thereof, each having one or more compression stages. Regarding the heat exchangers, direct heat exchangers may include spray coolers (e.g., spray intercoolers), which inject a liquid spray into a gas flow (e.g., oxidant flow) for direct cooling of the gas flow. Indirect heat exchangers may include at least one wall (e.g., a shell and tube heat exchanger) separating first and second flows, such as a fluid flow (e.g., oxidant flow) separated from a coolant flow (e.g., water, air, refrigerant, or any other liquid or gas coolant), wherein the coolant flow transfers heat from the fluid flow without any direct contact. Examples of indirect heat exchangers include intercooler heat exchangers and heat recovery units, such as heat recovery steam generators. The heat exchangers also may include heaters. As discussed in further detail below, each of these machinery components may be used in various combinations as indicated by the non-limiting examples set forth in TABLE 1.
Generally, the machinery 106, 178, 180 may be configured to increase the efficiency of the compression system 186 by, for example, adjusting operational speeds of one or more oxidant compressors in the system 186, facilitating compression of the oxidant 68 through cooling, and/or extraction of surplus power. The disclosed embodiments are intended to include any and all permutations of the foregoing components in the machinery 106, 178, 180 in series and parallel arrangements, wherein one, more than one, all, or none of the components derive power from the shaft 176. As illustrated below, TABLE 1 depicts some non-limiting examples of arrangements of the machinery 106, 178, 180 disposed proximate and/or coupled to the compressor and turbine sections 152, 156.
As illustrated above in TABLE 1, a cooling unit is represented as CLR, a clutch is represented as CLU, a drive is represented by DRV, a gearbox is represented as GBX, a generator is represented by GEN, a heating unit is represented by HTR, a main oxidant compressor unit is represented by MOC, with low pressure and high pressure variants being represented as LP MOC and HP MOC, respectively, and a steam generator unit is represented as STGN. Although TABLE 1 illustrates the machinery 106, 178, 180 in sequence toward the compressor section 152 or the turbine section 156, TABLE 1 is also intended to cover the reverse sequence of the machinery 106, 178, 180. In TABLE 1, any cell including two or more components is intended to cover a parallel arrangement of the components. TABLE 1 is not intended to exclude any non-illustrated permutations of the machinery 106, 178, 180. These components of the machinery 106, 178, 180 may enable feedback control of temperature, pressure, and flow rate of the oxidant 68 sent to the gas turbine engine 150. As discussed in further detail below, the oxidant 68 and the fuel 70 may be supplied to the gas turbine engine 150 at locations specifically selected to facilitate isolation and extraction of the compressed exhaust gas 170 without any oxidant 68 or fuel 70 degrading the quality of the exhaust gas 170.
The EG supply system 78, as illustrated in
The extracted exhaust gas 42, which is distributed by the EG supply system 78, has a controlled composition suitable for the target systems (e.g., the hydrocarbon production system 12 and the other systems 84). For example, at each of these extraction points 76, the exhaust gas 170 may be substantially isolated from injection points (or flows) of the oxidant 68 and the fuel 70. In other words, the EG supply system 78 may be specifically designed to extract the exhaust gas 170 from the gas turbine engine 150 without any added oxidant 68 or fuel 70. Furthermore, in view of the stoichiometric combustion in each of the combustors 160, the extracted exhaust gas 42 may be substantially free of oxygen and fuel. The EG supply system 78 may route the extracted exhaust gas 42 directly or indirectly to the hydrocarbon production system 12 and/or other systems 84 for use in various processes, such as enhanced oil recovery, carbon sequestration, storage, or transport to an offsite location. However, in certain embodiments, the EG supply system 78 includes the EG treatment system (EGTS) 82 for further treatment of the exhaust gas 42, prior to use with the target systems. For example, the EG treatment system 82 may purify and/or separate the exhaust gas 42 into one or more streams 95, such as the CO2 rich, N2 lean stream 96, the intermediate concentration CO2, N2 stream 97, and the CO2 lean, N2 rich stream 98. These treated exhaust gas streams 95 may be used individually, or in any combination, with the hydrocarbon production system 12 and the other systems 84 (e.g., the pipeline 86, the storage tank 88, and the carbon sequestration system 90).
Similar to the exhaust gas treatments performed in the EG supply system 78, the EG processing system 54 may include a plurality of exhaust gas (EG) treatment components 192, such as indicated by element numbers 194, 196, 198, 200, 202, 204, 206, 208, and 210. These EG treatment components 192 (e.g., 194 through 210) may be disposed along the exhaust recirculation path 110 in one or more series arrangements, parallel arrangements, or any combination of series and parallel arrangements. For example, the EG treatment components 192 (e.g., 194 through 210) may include any series and/or parallel arrangement, in any order, of: one or more heat exchangers (e.g., heat recovery units such as heat recovery steam generators, condensers, coolers, or heaters), catalyst systems (e.g., oxidation catalyst systems), particulate and/or water removal systems (e.g., inertial separators, coalescing filters, water impermeable filters, and other filters), chemical injection systems, solvent based treatment systems (e.g., absorbers, flash tanks, etc.), carbon capture systems, gas separation systems, gas purification systems, and/or a solvent based treatment system, or any combination thereof. In certain embodiments, the catalyst systems may include an oxidation catalyst, a carbon monoxide reduction catalyst, a nitrogen oxides reduction catalyst, an aluminum oxide, a zirconium oxide, a silicone oxide, a titanium oxide, a platinum oxide, a palladium oxide, a cobalt oxide, or a mixed metal oxide, or a combination thereof. The disclosed embodiments are intended to include any and all permutations of the foregoing components 192 in series and parallel arrangements. As illustrated below, TABLE 2 depicts some non-limiting examples of arrangements of the components 192 along the exhaust recirculation path 110.
As illustrated above in TABLE 2, a catalyst unit is represented by CU, an oxidation catalyst unit is represented by OCU, a booster blower is represented by BB, a heat exchanger is represented by HX, a heat recovery unit is represented by HRU, a heat recovery steam generator is represented by HRSG, a condenser is represented by COND, a steam turbine is represented by ST, a particulate removal unit is represented by PRU, a moisture removal unit is represented by MRU, a filter is represented by FIL, a coalescing filter is represented by CFIL, a water impermeable filter is represented by WFIL, an inertial separator is represented by INER, and a diluent supply system (e.g., steam, nitrogen, or other inert gas) is represented by DIL. Although TABLE 2 illustrates the components 192 in sequence from the exhaust outlet 182 of the turbine section 156 toward the exhaust inlet 184 of the compressor section 152, TABLE 2 is also intended to cover the reverse sequence of the illustrated components 192. In TABLE 2, any cell including two or more components is intended to cover an integrated unit with the components, a parallel arrangement of the components, or any combination thereof. Furthermore, in context of TABLE 2, the HRU, the HRSG, and the COND are examples of the HE; the HRSG is an example of the HRU; the COND, WFIL, and CFIL are examples of the WRU; the INER, FIL, WFIL, and CFIL are examples of the PRU; and the WFIL and CFIL are examples of the FIL. Again, TABLE 2 is not intended to exclude any non-illustrated permutations of the components 192. In certain embodiments, the illustrated components 192 (e.g., 194 through 210) may be partially or completed integrated within the HRSG 56, the EGR system 58, or any combination thereof. These EG treatment components 192 may enable feedback control of temperature, pressure, flow rate, and gas composition, while also removing moisture and particulates from the exhaust gas 60. Furthermore, the treated exhaust gas 60 may be extracted at one or more extraction points 76 for use in the EG supply system 78 and/or recirculated to the exhaust inlet 184 of the compressor section 152.
As the treated, recirculated exhaust gas 66 passes through the compressor section 152, the SEGR gas turbine system 52 may bleed off a portion of the compressed exhaust gas along one or more lines 212 (e.g., bleed conduits or bypass conduits). Each line 212 may route the exhaust gas into one or more heat exchangers 214 (e.g., cooling units), thereby cooling the exhaust gas for recirculation back into the SEGR gas turbine system 52. For example, after passing through the heat exchanger 214, a portion of the cooled exhaust gas may be routed to the turbine section 156 along line 212 for cooling and/or sealing of the turbine casing, turbine shrouds, bearings, and other components. In such an embodiment, the SEGR gas turbine system 52 does not route any oxidant 68 (or other potential contaminants) through the turbine section 156 for cooling and/or sealing purposes, and thus any leakage of the cooled exhaust gas will not contaminate the hot products of combustion (e.g., working exhaust gas) flowing through and driving the turbine stages of the turbine section 156. By further example, after passing through the heat exchanger 214, a portion of the cooled exhaust gas may be routed along line 216 (e.g., return conduit) to an upstream compressor stage of the compressor section 152, thereby improving the efficiency of compression by the compressor section 152. In such an embodiment, the heat exchanger 214 may be configured as an interstage cooling unit for the compressor section 152. In this manner, the cooled exhaust gas helps to increase the operational efficiency of the SEGR gas turbine system 52, while simultaneously helping to maintain the purity of the exhaust gas (e.g., substantially free of oxidant and fuel).
The process 220 may begin by initiating a startup mode of the SEGR gas turbine system 52 of
The process 220 may then combust a mixture of the compressed oxidant, fuel, and exhaust gas in the combustors 160 to produce hot combustion gas 172, as indicated by block 230 by the one or more diffusion flames, premix flames, or a combination of diffusion and premix flames. In particular, the process 220 may be controlled by the control system 100 of
The process 220 then drives the turbine section 156 with the hot combustion gas 172, as indicated by block 232. For example, the hot combustion gas 172 may drive one or more turbine stages 174 disposed within the turbine section 156. Downstream of the turbine section 156, the process 220 may treat the exhaust gas 60 from the final turbine stage 174, as indicated by block 234. For example, the exhaust gas treatment 234 may include filtration, catalytic reaction of any residual oxidant 68 and/or fuel 70, chemical treatment, heat recovery with the HRSG 56, and so forth. The process 220 may also recirculate at least some of the exhaust gas 60 back to the compressor section 152 of the SEGR gas turbine system 52, as indicated by block 236. For example, the exhaust gas recirculation 236 may involve passage through the exhaust recirculation path 110 having the EG processing system 54 as illustrated in
In turn, the recirculated exhaust gas 66 may be compressed in the compressor section 152, as indicated by block 238. For example, the SEGR gas turbine system 52 may sequentially compress the recirculated exhaust gas 66 in one or more compressor stages 158 of the compressor section 152. Subsequently, the compressed exhaust gas 170 may be supplied to the combustors 160 and fuel nozzles 164, as indicated by block 228. Steps 230, 232, 234, 236, and 238 may then repeat, until the process 220 eventually transitions to a steady state mode, as indicated by block 240. Upon the transition 240, the process 220 may continue to perform the steps 224 through 238, but may also begin to extract the exhaust gas 42 via the EG supply system 78, as indicated by block 242. For example, the exhaust gas 42 may be extracted from one or more extraction points 76 along the compressor section 152, the combustor section 154, and the turbine section 156 as indicated in
As noted above, the control system 100 may include one or more sensors or probes distributed throughout the system 10 to obtain the sensor feedback 130 for use in execution of the various controls, e.g., the controls 124, 126, and 128. For example, the sensor feedback 130 may be obtained from sensors or probes distributed throughout the SEGR gas turbine system 52. As the various components of the SEGR gas turbine system 52 may operate in high temperature conditions, the probes coupled to the various components of the SEGR gas turbine system 52 may also operate in high temperature environments. As such, cooling flows may be used to cool the probes to facilitate operations and increase lifetime of the probes. When the cooling flows exit the probes, the cooling flows may have high temperatures and high velocities. In accordance with the present disclosure, ejectors are coupled to the probes such that the cooling flows exiting the probes may flow through the ejectors to be cooled and decelerated for discharging into the atmosphere.
As illustrated, the compressor section 152 directs the compressed exhaust gas 170 from the compressor stages 158 into a compressor discharge casing 410. The compressor discharge casing 410 encloses at least part of the combustor 160 of the combustor section 154 (e.g., the combustion chamber 168), a combustor liner 414, and a flow sleeve 412. The flow sleeve 412 may direct the compressed exhaust gas 170 to the head end portion 166. In some embodiments, portions of the flow sleeve 412 also receive the oxidant 68. Gas (e.g., oxidant 68 and/or compressed exhaust gas 170) within the flow sleeve 412 may cool the combustor liner 414 that at least partially encloses the combustion chamber 168. The compressed exhaust gas 170 in the compressor discharge casing 410 may enter the flow sleeve 412 through passages 416. Some of the compressed exhaust gas 170, other diluent (e.g., steam, water), or oxidant 68 may enter the combustion chamber 168 through dilution holes 418 in the combustor liner 414. The dilution holes 418 may direct the compressed exhaust gas 170 and/or oxidant 68 into a dilution zone 420. As discussed above, some of the compressed exhaust gas 170 may be extracted through the extraction point 76 to the exhaust gas supply system 78 external to the compressor discharge casing 410. The exhaust gas supply system 78 may treat and supply the exhaust gas 42 to the hydrocarbon production system 12, such as for enhanced oil recovery. A cap 422 divides the combustor 160 into the head end portion 166 and the combustion chamber 168. The fuel nozzles 164 are positioned in the head end portion 166, and flames, if any, from combustion occur within the combustion chamber 168. The combustion gases 172 flow through the combustion chamber 168 primarily in a downstream direction 424 toward the turbine section 156. The compressed exhaust gas 170 and/or the oxidant 68 may flow through the flow sleeve 412 toward the head end portion 166 from the compressor section 152 in an upstream direction 426 relative to the combustion gases 172.
As illustrated in
As noted above, when in operation, various components of the compressor section 152 and combustor section 154 may be in high temperature conditions. For example, the outlet 504 of the compressor section 152 has a temperature of about 250° C. to 350° C., and the transition piece 432 of the combustor section 154 has a temperature of about 800° C. to 1350° C. A cooling flow is used to cool each of the probes in the probe-ejector assemblies 500 (e.g., the first, second, third, fourth, fifth, sixth probe-ejector assemblies 502, 506, 510, 512, 514, 516). The cooling flow becomes a heated outflow after cooling the probe, and the heated outflow is directed to the respective ejector in the probe-ejector assemblies 500. Each ejector in the probe-ejector assemblies 500, as discussed in greater detail below, cools the heated outflow (e.g., below a threshold or a range of temperature) and decelerates the outflow (e.g., below a threshold or a range of velocity), thereby releasing the cooled and decelerated outflow to the atmosphere. Also, as discussed in greater detail below, each ejector in the probe-ejector assemblies 500 may draw ambient air as a coolant into the respective ejector to mix with the heated outflow. As such, each of the probe-ejector assemblies 500, as illustrated in
The probe 602 includes a sensing component 612 configured to sense a parameter of the system 10. The probe 602 may be any type of probe, and the sensing component 612 may be configured to sense any suitable parameters of the system 10, including, but not limited to, temperature, pressure, flow rate, gas composition, gas concentration (e.g., O2 content, CO2 content, NOX content, SOX content), electrical current, electrical power, magnetic field, and volume. For example, the probe 602 may include a temperature probe (e.g., a thermocouple), a pressure probe, a lambda probe (e.g., a O2 sensor), a flow rate probe, a composition probe (e.g., a fuel sensor, a NOX sensor, a CO sensor, a CO2 sensor, a SOX sensor, a H2 sensor, or a HC sensor), a concentration probe, an electric probe (e.g., a current probe), an electromagnetic probe (e.g., an Eddy current probe), or any combination thereof. The probe 602 also includes a body 614 coupled to the sensing component 612. The body 614 may include any functional components (e.g., processor, memory, connecting circuitry, display, and/or user input) suitable for the operation of the probe 602.
When the system 10 operates in high temperature conditions, all or a portion of the probe 602, including the sensing component 612 and the body 614, may be at high temperatures. For example, the sensing component 612 may be on the warm side 608 of the side wall 606. As such, the probe 602 may be cooled for improved measurement accuracy and/or extended lifetime. The probe 602 includes a cooling passage 616 disposed along at least a portion of the probe 602. The cooling passage 616 may be a flow path, a conduit, an annulus, or a shell that is completely or partially enclosing the probe 602. The cooling passage 616 includes an inlet 618 and an outlet 620. The inlet 616 is configured to receive a cooling inflow 622. As the cooling inflow 622 flows through the cooling passage 616, the cooling inflow 622 absorbs heat from the probe 602, thereby cooling the probe 602. A cool probe 602 may facilitate the operation of and increase the lifetime of the probe 602. As the cooling inflow 622 absorbs the heat from the probe 602, the cooling inflow 622 becomes heated to form an outflow 624 exiting the outlet 620. The cooling inflow may be any suitable fluid, including air, carbon dioxide, nitrogen, argon, water, steam, exhaust gas (e.g., the compressed exhaust gas 170, or recirculated exhaust gas from various components of the system 10), or any combination thereof.
In some embodiments, the cooling passage 616 is closed with respect to the system 10. For example, the cooling inflow 622 only flows into the cooling passage 616 via the inlet 618 and exits out of the cooling passage 616 via the outlet 620 (as the outflow 624). In other embodiments, the cooling passage 616 is open to the system 10. For example, the cooling passage 616 may include one or more openings to the system 10 near the sensing component 612. As such, a portion of the cooling inflow 622 may flow out of the cooling passage 616, or a portion of fluid (e.g., oxidant, fuel, exhaust gas) present in the system 10 may flow into the cooling passage 616. Accordingly, outflow 624 may include not all, but a portion of, the cooling inflow 622.
As illustrated, the ejector 604 includes an ejector inlet 626. The ejector inlet 626 is fluidly coupled to the outlet 620 of the probe 602. The outflow 624 enters the ejector 604 via the ejector inlet 626 and flows through a nozzle 628 (e.g., a converging conduit such as a conical conduit) into an interior 630 of the ejector 604. As the outflow 624 flows through the nozzle 628, the velocity of the outflow 624 increases and a low pressure area 632 forms at or near an exit of the nozzle 628. The low pressure area 632 creates a suction force within a coolant passage 634 of the ejector 604. As shown, the coolant passage 634 is formed about the nozzle 628 and includes an opening 636 through which a coolant 638 may flow. The suction force within the coolant passage 634 created by the low pressure area 632 draws the coolant 638 into the coolant passage 634 through the opening 636. The coolant 638 flows into the coolant passage 634 and, subsequently, flows into a mixing portion 640 (e.g., downstream of the low pressure area 632) where the coolant 638 mixes with the outflow 624 to form a discharge flow 642. The mixing portion 640 is a converging conduit or section, such as a conical conduit. Thereafter, the discharge flow 642 continues through a throat portion 644 (e.g., a reduced width conduit or minimum diameter section, such as a venturi section) and a diffuser portion 646 (e.g., a diverging conduit or section) to exit the ejector 604 through an ejector outlet 648. It should be noted that the various sections (e.g., the nozzle 628, the coolant passage 634, the throat portion 644, and the diffuser portion 646) of the ejector 604 may have any suitable shape or configurations, such as circular, oval, square, rectangular, or the like, or any combination thereof.
As noted above, the cooling inflow 622 absorbs the heat from the probe 602 and becomes the heated outflow 624 exiting the outlet 620 of the cooling passage 616. The coolant 638 drawn into the ejector 604 has a lower temperature than the outflow 624 and, when mixing with the outflow 624 in the ejector 604, decreases the temperature of the outflow 624. Consequently, the discharge flow 642 exiting the ejector 604 may have a lower temperature than the outflow 624 that enters the ejector 604. For example, the outflow 624 has a temperature of greater than approximately 80° C., such as between approximately 80° C. and 1800° C., between approximately 90° C. and 1700° C., between approximately 100° C. and 1600° C., between approximately 120° C. and 1500° C., between approximately 140° C. and 1400° C., between approximately 160° C. and 1300° C., between approximately 180° C. and 1200° C., between approximately 200° C. and 1100° C., between approximately 250° C. and 1000° C., between approximately 300° C. and 900° C., between approximately 400° C. and 800° C., or between approximately 500° C. and 700° C. The coolant 638 has a temperature of less than approximately 40° C., such as between approximately 40° C. and 0° C., between approximately 35° C. and 0° C., between approximately 30° C. and 5° C., between approximately 25° C. and 10° C., or between approximately 20° C. and 15° C. The discharge flow 642 has a temperature of less than approximately 80° C., such as between approximately 80° C. and 0° C., between approximately 75° C. and 0° C., between approximately 70° C. and 5° C., between approximately 65° C. and 10° C., between approximately 60° C. and 15° C., between approximately 55° C. and 20° C., between approximately 50° C. and 25° C., between approximately 45° C. and 30° C., or between approximately 40° C. and 35° C. The coolant 638 may be any suitable fluid, including, but not limited to, air (e.g., ambient air, compressed air, or air stream from an air supply unit), water, any other liquid or gas coolant, or a combination thereof.
As noted above, the temperature of the discharge flow 642 depends at least on the temperature of the outflow 624 and the temperature of the coolant 638. In addition, the flow rate (or amount) of the outflow 624 exiting the nozzle 628 and the flow rate (or amount) of the coolant entering the ejector 604 through the opening 636 may affect the temperature of the discharge flow 642. For example, with the same amount of the outflow 624 exiting the nozzle 628, increasing the quantity of the coolant 638 that enters through the opening 636 to mix with the outflow 624 may result in a lower temperature of the discharge flow 642. The flow rate of the outflow 624 exiting the nozzle 628 may in turn depend at least on the configuration of the nozzle 628, such as a ratio of a size (e.g., a diameter 650) of a tip 652 of the nozzle 628 to a size (e.g., a diameter 654) of an inlet 656 of the nozzle 628. The flow rate of the coolant 638 entering through the opening 636 may in turn depend at least on the size (e.g., a diameter 658) of the opening 636. In some embodiments, the ejector 604 includes a door 660 coupled to the opening 636. The door 660 is controlled (e.g., via a controller) to change the size of the opening 636, thereby adjusting the flow rate and/or amount of the coolant 638 through the opening 636. For example, the door 660 may be a check valve (e.g., responsive to a certain setpoint pressure or flow rate), and the controller may adjust the setpoint to control opening and closing of the check valve to control the flow rate (or the quantity) of the coolant 638 drawn into the ejector 604. In certain embodiments, the door 660 may be a motorized valve, and the controller may control the motorized valve to open and close to any certain degree based on control signals (e.g., currents, voltages, pressures, temperatures, or the like). As noted above, by controlling the size of the opening 636, the temperature and/or flow rate of the discharge flow 642 exiting the ejector 604 may be adjusted. For example, by increasing the size of the opening 636, the temperature of the discharge flow 642 exiting the ejector 604 may decrease. By decreasing the size of the opening 636, the temperature of the discharge flow 642 exiting the ejector 604 may increase.
The ejector 604 is also formed in such a shape to increase the cross sectional area of the interior 630, thereby having an effect of reducing the velocity of the mixture of the outflow 624 and the coolant 638 as the mixture flowing through the throat portion 644 and the diffuser portion 646. In other words, the discharge flow 642 exiting the ejector 604 may have a lower velocity than the outflow 624 entering the ejector 604. For example, the diffuser portion 646 includes a diverging conduit with a size (e.g., a diameter 662) at the ejector outlet 648 greater than the size (e.g., the diameter 654) of the inlet 656 of the nozzle 628. As such, the diffuser portion 646 has an effect of converting at least a portion of the velocity energy of the mixture to the pressure energy thereof. In some embodiments, the velocity of the discharge flow 642 exiting the ejector 604 is less than 95%, such as 90%, 85%, 80%, 75%, 70%, 65%, 60%, 55%, 50%, 45%, 40%, 35%, 30%, 25%, 20%, 15%, 10%, or 5%, of the velocity of the outflow 624 exiting the probe 602. In certain embodiments, the velocity of the discharge flow 642 exiting the ejector 604 is less than 60 m/s, such as 55 m/s, 50 m/s, 45 m/s, 40 m/s, 35 m/s, 30 m/s, 25 m/s, 20 m/s, 15 m/s, 10 m/s, 5 m/s, 2 m/s, or 1 m/s.
As will be appreciated, the discharge flow 642 exiting the ejector 604 has a lower temperature and a lower velocity compared to the outflow 624 exiting the probe 602. The discharge flow 642 may be released directly to the atmosphere. Thus, separate piping (and/or heat exchangers) for directing the high temperature and high velocity cooling flows from the exit of the cooling passage to a remote location for releasing may be eliminated. Also, separate heat exchangers (e.g., disposed in the remote location) for cooling the high temperature cooling flows exiting the cooling passage may be eliminated. Moreover, as will be appreciated, the ejector 604 may operate without a motor, fan, or other powered mechanical device, which may help reduce the cost and/or complexity of the probe-ejector assembly 500.
The probe 684 includes a cooling passage 692. The probe 688 includes a cooling passage 694. A flow path 696 (e.g., a conduit, a passage, a line, or the like) couples the cooling passages 692 and 694 from an opening 698 on the cooling passage 692 to an inlet 700 of the cooling passage 694. As such, a cooling inflow 702 may flow through the cooling passage 692 (or a portion thereof) and the cooling passage 694 in series to exchange heat with both of the probes 684 and 688. While two of the probe-ejector assemblies 500 are illustrated in
The method 750 may start when the cooling inflow 622 is supplied (block 752) to cool the probe 602 coupled to a component of the system 10, including the hydrocarbon production system 12 and the turbine-based service system 14. The component of the system 10 and, consequently, the probe 602, may operate in high temperature conditions. As such, the cooling inflow 622 may be used to cool the probe 602. The probe 602 includes the cooling passage 616 disposed along at least a portion of the probe 602. The cooling inflow 622 flows through the cooling passage 616 to absorb heat from the probe 602, thereby forming the heated outflow 624.
The outlet 620 of the probe 602 is fluidly coupled to the ejector inlet 626. The outflow 624 is directed (block 754) to the ejector 604 from the outlet 620 of the probe 602 via the ejector inlet 626. The outflow 624 is constricted (block 756) by the nozzle 628 of the ejector inlet 626. Due to the constriction by the nozzle 628, the velocity of the outflow 624 increases and the low pressure area 632 forms at or near the exit of the nozzle 628. The low pressure area 632 creates a suction force, and the coolant 638 (e.g., ambient air) is drawn (block 758) into the interior 630 of the ejector 604. The coolant 638 is mixed (block 760) with the outflow 624 in the interior 630 to form the mixture (e.g., the discharge flow 642). Thereafter, the discharge flow 642 continues through the ejector 604 (e.g., the throat portion 644 and the diffuser portion 646) and is discharged (block 762) from the ejector 604 through the ejector outlet 648.
As discussed above, the coolant 638 has a lower temperature than the outflow 624 and, when mixing with the outflow 624 in the ejector 604, decreases the temperature of the outflow 624. In addition, the ejector 604 is also formed in such a shape to increase the sectional area of the interior 630, thereby having an effect of reducing the velocity of the mixture of the outflow 624 and the coolant 638 as the mixture flowing through the throat portion 644 and the diffuser portion 646. Accordingly, the discharge flow 642 exiting the ejector 604 may have a lower temperature and a lower velocity than the outflow 624 entering the ejector 604. Consequently, the discharge flow 642 may be released directly into the atmosphere without separate piping or heat exchangers to cool and reduce the velocity of the outflow 624.
This written description uses examples to disclose the embodiments, including the best mode, and also to enable any person skilled in the art to practice the present disclosure, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the present disclosure is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.
The present embodiments provide a system and method for cooling and decelerating discharge flows from probes coupled to a gas turbine system. It should be noted that any one or a combination of the features described above may be utilized in any suitable combination. Indeed, all permutations of such combinations are presently contemplated. By way of example, the following clauses are offered as further description of the present disclosure:
A system includes a probe. The probe includes a sensing component configured to sense a parameter of a turbomachine. The probe also includes an inlet configured to receive a cooling inflow. The probe also includes a cooling passage configured to receive the cooling inflow from the inlet, wherein the cooling passage is disposed along at least a portion of the probe, and the cooling inflow absorbs heat from the probe. The probe also includes an outlet coupled to the cooling passage and configured to receive an outflow from the cooling passage, wherein the outflow includes at least a portion of the cooling inflow. The system also includes an ejector coupled to the outlet. The ejector includes an interior. The ejector also includes an opening fluidly coupled to the interior, wherein the opening is configured to receive a coolant. The ejector also includes a nozzle coupled to the outlet, wherein the nozzle is configured to constrict the outflow from the outlet and to deliver the outflow to the interior. The ejector also includes a mixing portion configured to mix the outflow and the coolant to provide a discharge flow.
The system of embodiment 1, wherein the probe includes a lambda probe and the parameter includes an oxygen content of a working flow of the turbomachine, and the turbomachine includes a gas turbine engine.
The system of any preceding embodiment, wherein the probe includes a temperature probe and the parameter includes a temperature of a portion of the turbomachine.
The system of any preceding embodiment, wherein the probe includes a flow-sensing probe and the parameter includes a flow rate of a working flow of the turbomachine.
The system of any preceding embodiment, wherein the cooling inflow includes air, carbon dioxide, nitrogen, or any combination thereof.
The system of any preceding embodiment, wherein the turbomachine includes a gas turbine engine, and the cooling inflow includes a recirculated exhaust gas of the gas turbine engine.
The system of any preceding embodiment, wherein the coolant includes ambient air, wherein a temperature of the ambient air is less than approximately 40° C.
The system of any preceding embodiment, wherein the sensing component of the probe is disposed at an axial end of the probe, and cooling passage directs the cooling inflow along an axis of the probe towards the axial end.
The system of any preceding embodiment, wherein the system includes the gas turbine engine, wherein the gas turbine engine includes a turbine combustor, a turbine driven by combustion gases from the turbine combustor and that outputs an exhaust gas, and an exhaust gas compressor driven by the turbine, wherein the exhaust gas compressor is configured to compress and to route the exhaust gas to the turbine combustor.
The system of embodiment 9, wherein the gas turbine engine is a stoichiometric exhaust gas recirculation (SEGR) gas turbine engine.
The system of embodiment 10, wherein the system includes an exhaust gas extraction system coupled to the gas turbine engine, and a hydrocarbon production system coupled to the exhaust gas extraction system.
The system of any preceding embodiment, wherein the ejector includes a converging section, a throat disposed downstream of the converging section, and a diverging section disposed downstream of the throat, wherein the nozzle is disposed upstream of the converging section, and the mixing portion is disposed in the converging section.
A system includes a probe. The probe includes a sensing component configured to sense a parameter of a gas turbine engine. The probe also includes an inlet configured to receive a cooling inflow. The probe also includes a cooling passage configured to receive the cooling inflow from the inlet, wherein the cooling passage is disposed along at least a portion of the probe, and the cooling inflow absorbs heat from the probe to form a heated outflow. The probe also includes an outlet coupled to the cooling passage and configured to receive the heated outflow from the cooling passage, wherein a temperature of the heated outflow at the outlet is greater than 80° C. The system also includes an ejector coupled to the outlet. The ejector includes an interior. The ejector also includes an opening fluidly coupled to the interior, wherein the opening is configured to receive a coolant. The ejector also includes a nozzle coupled to the outlet, wherein the nozzle is configured to constrict the heated outflow from the outlet and to deliver the heated outflow to the interior. The ejector also includes a mixing portion configured to mix the heated outflow and the coolant to provide a discharge flow, wherein a temperature of the discharge flow is less than 80° C.
The system of embodiment 13, wherein the probe includes a lambda probe and the parameter includes an oxygen content of a working flow of the gas turbine engine.
The system of embodiments 13 or 14, wherein the probe includes a temperature probe and the parameter includes a temperature of a portion of the gas turbine engine.
The system of embodiments 13, 14, or 15, wherein the probe includes a flow-sensing probe and the parameter includes a flow rate of a working flow of the gas turbine engine.
The system of embodiments 13, 14, 15, or 16, wherein the cooling inflow includes air, carbon dioxide, nitrogen, or any combination thereof.
The system of embodiments 13, 14, 15, 16, or 17, wherein the coolant includes ambient air, and a temperature of the ambient air is less than approximately 40° C.
The system of embodiments 13, 14, 15, 16, 17, or 18, wherein the nozzle includes a nozzle outlet adjacent to the interior, the nozzle outlet includes a first diameter, the outlet of the probe includes a second diameter, and the first diameter is greater than the second diameter.
The system of embodiments 13, 14, 15, 16, 17, 18, or 19, wherein the ejector includes a door coupled to the opening, wherein the door is configured to control a flow rate of the coolant through the opening.
A method includes supplying a cooling inflow to a probe configured to sense a parameter of a gas turbine engine, wherein the cooling inflow is configured to absorb heat from the probe to form a heated outflow. The method also includes directing the heated outflow from the probe to an ejector, wherein the ejector includes a nozzle coupled to an outlet of the probe. The method also includes constricting the heated outflow through the nozzle into an interior of the ejector to draw a coolant into the interior of the ejector via an opening. The method also includes mixing the heated outflow and the coolant to form a discharge flow in a mixing portion of the ejector. The method also includes directing the discharge flow to an ejector outlet of the ejector, wherein a temperature of the discharge flow is less than 80° C.
The method of embodiment 21, wherein the probe includes a lambda probe and the parameter includes an oxygen content of a working flow of the gas turbine engine, the probe includes a temperature probe and the parameter includes a temperature of a portion of the gas turbine engine, the probe includes a flow-sensing probe and the parameter includes a flow rate of a working flow of the gas turbine engine, or any combination thereof.
The method of embodiments 21 or 22, wherein the cooling inflow includes air, carbon dioxide, nitrogen, or any combination thereof.
The method of embodiments 21, 22, or 23, wherein the coolant includes ambient air, wherein a temperature of the ambient air is less than approximately 40° C.
The method of embodiments 21, 22, 23, or 24, where the method includes controlling a size of the opening to adjust a flow rate of the coolant based at least in part on a temperature of the discharge flow.
This application is a continuation of U.S. patent application Ser. No. 15/060,089, entitled “SYSTEM AND METHOD FOR COOLING DISCHARGE FLOW,” filed Mar. 3, 2016, which claims priority to and benefit of U.S. Provisional Patent Application No. 62/128,337, entitled “SYSTEM AND METHOD FOR COOLING DISCHARGE FLOW,” filed on Mar. 4, 2015, which are incorporated by reference herein in their entirety for all purposes.
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