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WO2010036849A2 - Système de combustion oxy-gaz comprenant une section convective et une section rayonnante combinées - Google Patents

Système de combustion oxy-gaz comprenant une section convective et une section rayonnante combinées Download PDF

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Publication number
WO2010036849A2
WO2010036849A2 PCT/US2009/058296 US2009058296W WO2010036849A2 WO 2010036849 A2 WO2010036849 A2 WO 2010036849A2 US 2009058296 W US2009058296 W US 2009058296W WO 2010036849 A2 WO2010036849 A2 WO 2010036849A2
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
thermal shield
tubes
fluid
flame
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2009/058296
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English (en)
Other versions
WO2010036849A3 (fr
Inventor
Reed Jacob Hendershot
Xiaoyi He
Jeffrey William Kloosterman
Michael Joseph Hibay
Aleksander Georgi Slavejkov
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Air Products and Chemicals Inc
Original Assignee
Air Products and Chemicals Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Air Products and Chemicals Inc filed Critical Air Products and Chemicals Inc
Priority to CN2009801377799A priority Critical patent/CN102834668A/zh
Priority to CA2733106A priority patent/CA2733106A1/fr
Priority to EP09792981A priority patent/EP2329194A2/fr
Publication of WO2010036849A2 publication Critical patent/WO2010036849A2/fr
Anticipated expiration legal-status Critical
Publication of WO2010036849A3 publication Critical patent/WO2010036849A3/fr
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L7/00—Supplying non-combustible liquids or gases, other than air, to the fire, e.g. oxygen, steam
    • F23L7/007—Supplying oxygen or oxygen-enriched air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M5/00—Casings; Linings; Walls
    • F23M5/08—Cooling thereof; Tube walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • the present disclosure is directed to a combustion system.
  • the present disclosure is directed to a combustion system combining the convective section and the radiant section.
  • FGR flue gas recycle
  • oxy/coal combustion coal combustion in oxygen
  • air/coal combustion air/coal combustion
  • Desirable furnace exit gas temperatures are in the range of 1200-1400 0 C (about 2200-2550 0 F), primarily based on convective pass tube fouling considerations. Therefore it is necessary to remove sufficient heat in the furnace section so that the furnace exit gas temperature is reduced to acceptable limits.
  • This disclosure provides a boiler design that does not require flue gas recycle to achieve the correct heat distribution to superheat and reheat steam, achieves lower overall cost, permits superheating of at least a portion of the steam in the radiant section of an oxy/solid fuel boiler, and/or adequately protects the superheat tubes from the high heat fluxes prevailing in the radiant section.
  • An embodiment of the disclosure includes a heat transfer system having a radiant source, a first heat exchanger configured to permit a first fluid to flow therethrough, and a thermal shield configured to provide controlled radiative heat from the radiant source to the first exchanger.
  • the radiant source is a flame and the thermal shield is a second heat exchanger configured to permit a second fluid to flow therethrough.
  • Another embodiment of the disclosure includes an oxy/fuel combustion system.
  • the system includes a furnace arranged and disposed to provide a flame radiant source.
  • a first exchanger is disposed in the furnace and is arranged and disposed to exchange radiant heat from the radiant source and steam for use in a steam turbine.
  • the system further includes a thermal shield configured to provide controlled radiative heat exposure from the radiant source to the first exchanger.
  • the thermal shield is a second heat exchanger configured to permit a second fluid to flow therethrough.
  • Another embodiment of the disclosure includes an oxy/fuel combustion system.
  • the system includes a furnace arranged and disposed to provide a flame radiant source a furnace having a chamber arranged and disposed to provide a flame radiant source and to circulate combustion fluid.
  • a first heat exchanger configured to permit a first fluid to flow therethrough.
  • the system further includes a non-contact thermal shield fabricated from a material arranged to provide controlled radiative heat exposure from the radiant source to the first exchanger.
  • the radiant source is a flame and the first heat exchanger and the thermal shield are disposed within the chamber and in contact with the combustion fluid.
  • An advantage of the present disclosure is not requiring flue gas recycle to achieve the correct heat distribution to superheat and reheat steam.
  • the reduction or elimination of recycle permits reduction in the size or elimination of the convection section and boiler and therefore decreases the overall capital and operating cost of the system.
  • Another advantage of the present disclosure is lower overall cost.
  • Another advantage of the present disclosure is the ability to superheat at least a portion of the steam in the radiant section of an oxy/solid fuel boiler.
  • Yet another advantage of the present disclosure is providing increased protection of the superheat tubes from the high heat fluxes prevailing in the radiant section.
  • Yet another advantage of the present disclosure is reduced flue gas recycle without increasing temperature at which gases exit the radiant section thereby reducing the propensity for convective pass fouling as well as maintaining the heat and mass balance for a given turbine cycle.
  • FIG. 1 illustrates a perspective view of an exemplary embodiment of a combustion system.
  • FIG. 2 illustrates a sectioned view of an exemplary embodiment of a heat transfer system.
  • FIG. 5 illustrates the effect of changing tube row spacing (DY).
  • FIG. 6 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 7 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 8 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 9 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 10 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 11 illustrates a sectioned view of a heat exchanger system according to an embodiment.
  • FIG. 12 illustrates a sectioned view of a heat exchanger system according to another embodiment.
  • FIG. 13 illustrates a sectioned view of a heat exchanger system according to another embodiment.
  • FIG. 14 illustrates a sectioned view of a heat exchanger system according to another embodiment.
  • FIG. 15 illustrates a temperature plot for an exemplary heat exchanger system arrangement according to an embodiment.
  • solid fuel and grammatical variations thereof refers to any solid fuel suitable for combustion purposes.
  • the disclosure may be used with many types of carbon-containing solid fuels, including but not limited to: anthracite, bituminous, sub-bituminous, and lignite coals; tar; bitumen; petroleum coke; paper mill sludge solids and sewage sludge solids; wood; peat; grass; and combinations and mixtures of all of those fuels.
  • oxygen and grammatical variations thereof refers to an oxidizer having an O 2 concentration greater than that of atmospheric or ambient conditions.
  • combustion fluid and grammatical variations thereof refers to a fluid formed from and/or mixed with the products of combustion, which may be utilized for convective heat transfer. The term is not limited to the products of combustion and may include fluids mixed with or otherwise traveling through at least a portion of combustion system.
  • flue gas Although not so limited, one such example is flue gas.
  • cycled flue gas and grammatical variations thereof refers to combustion fluid exiting the system that is recirculated to any portion of the system.
  • flue gas recycle and grammatical variations thereof refers to a configuration permitting the combustion fluid to be recirculated.
  • an embodiment of the present disclosure includes a combustion system 102 with a furnace 104, a convective pass 106, a radiant source 108, a thermal shield 110, and a first heat exchanger 112.
  • the furnace 104 is depicted as a large enclosed space configured for fuel combustion and cooling of flue gas before the flue gas enters the convective pass 106.
  • the convective pass 106 generally includes one or more of a superheater, a reheater, and an economizer.
  • the superheater, the reheater, and the economizer surfaces are generally located in the path of the flue gas horizontal and vertical downflow sections of the boiler enclosure.
  • the radiant source 108 includes a solid fuel flame. In one embodiment the radiant source 108 is oxy/coal flame.
  • the first heat exchanger 1 12 is configured to permit a first fluid 114 to flow through it.
  • the term fluid includes, but is not limited to, movable solids, molten solids, gases, liquids, insoluble process components, colloids, and combinations thereof.
  • a thermal shield 1 10 is arranged and disposed to partially insulate the first heat exchanger 112 from the radiant source 108.
  • the thermal shield 110 and the first heat exchanger 112 are substantially within the furnace 104 of the combustion system 102.
  • First heat exchanger 112 may, for example, include heat exchanger tubes or other structures integrated into the walls of the furnace 104 or otherwise disposed to receive radiant heat generated within the furnace 104.
  • the thermal shield 1 10 is a heat exchanger.
  • the position of the thermal shield 1 10 is such that the first heat exchanger 112 is controllably shielded from radiative heat exposure from the radiant source 108.
  • "Radiative heat exposure" includes a susceptibility or ability of a component to exchange heat from a radiation heat source.
  • a plurality of thermal shields 110 and/or a plurality of thermally shielded heat exchangers may be included.
  • the thermal shield 110 may be a structure other than a heat exchanger.
  • the thermally shielded heat exchanger comprises a plurality of steam tubes.
  • the thermally shielded heat exchanger i.e. first heat exchanger 1 12
  • the thermal shield 110 is a mesh structure.
  • the thermal shield 1 10 may be configured to permit a second fluid 116 to flow through it.
  • the first fluid 114 differs from the second fluid 116 in at least one physical property.
  • the physical property that differs may include one or more properties selected from the group of properties consisting of heat capacity, density, viscosity, thermal conductivity, pressure, phase, phase fraction, velocity, mass, mass-flow, and combinations thereof.
  • the first fluid 1 14 is steam and the second fluid 1 16 is water.
  • the reduced internal heat transfer coefficient for steam tubes i.e. first heat exchanger 112 as compared to water tubes (i.e., thermal shield 110) leads to higher tube temperatures for steam tubes for a given heat flux.
  • high temperature piping is designed for operational limits of about 1242 0 F (672 0 C). Therefore placing steam tubes within a high heat flux location, such as an unprotected portion of the furnace 104, can lead to excessive metal temperatures and subsequent failure.
  • the thermal shield 110 is a plurality of tubes specifically configured to transport water.
  • the first heat exchanger 1 12 is a plurality of tubes specifically configured to transport steam.
  • the water-cooled tubes may reduce the heat flux to the steam tubes thereby reducing the metal temperature of the first heat exchanger 112 to a desired temperature.
  • the thermal shield 110 controllably reduces the radiative heat exposure of the first heat exchanger.
  • any remaining superheat duty that is required may be obtained in the convective pass 106 as is known with air/coal combustion boilers.
  • including the water tubes (i.e. the thermal shield 110) and the superheat tubes (i.e. first heat exchanger 1 12) in the furnace 104 decreases the desire for including flue gas recycle.
  • including the thermal shield 110 and the first heat exchanger 1 12 in the furnace 104 permits the furnace 104 to serve the role of the convective pass 106 in known air/coal combustion boilers in addition to the role of the furnace 104 in known air/coal combustion boilers.
  • FIG. 2 illustrates an embodiment of a heat transfer system 204.
  • the thermal shield 110 includes a plurality of transport structures 202.
  • the transport structures 202 are depicted as tubes filled with fluid, such as water or steam.
  • the transport structures 202 may be steel tubes.
  • the transport structures 202 may be comprised of any material capable of withstanding the temperatures in the furnace 104 of the combustion system 102.
  • other embodiments may include transport structures 202 with alternate geometries, such as, but not limited to, oval, square, triangular, or rectangular cross-sectional geometries.
  • the first heat exchanger 112 additionally includes a plurality of transport structures 202.
  • the transport structures 202 of the thermal shield 110 and the transport structures 202 of the first heat exchanger 112 are substantially the same. In other embodiments, the transport structures 202 of the thermal shield 110 and the first heat exchanger 112 differ in geometry, structure, orientation, or any other physical properties. In yet other embodiments, the transport structures 202 within the thermal shield 110 may differ from each other. Likewise, the transport structures 202 in the first heat exchanger 1 12 may differ from each other.
  • the arrangement of the thermal shield 110 and the first heat exchanger 1 12 is specifically configured to permit the thermal shield 1 10 to insulate, or protect from radiation heat exposure, the first heat exchanger 112.
  • the plurality of the transport structures 202 in the first heat exchanger 112 are equally separated by a distance D x i.
  • D ⁇ i is a distance corresponding to a distance between the centerpoints of transport structures 202 of the first heat exchanger 1 12.
  • the transport structures 202 have a diameter d Tube i
  • the transport structures 202 of the thermal shield 110 are separated by a distance D X2 .
  • D x2 is a distance corresponding to a distance between the centerpoints of transport structures 202 of the thermal shield 110.
  • the transport structures 202 of the thermal shield 110 are arranged parallel to the transport structures 202 of the first heat exchanger 112. In other embodiments, other arrangements may be included. In the embodiment illustrated in Figure 2, the transport structures 202 of the thermal shield 110 are positioned intermediate between the radiant source 108 and the transport structures 202 of the first heat exchanger 112. D y represents a distance between the thermal shield 110 and the first heat exchanger 1 12. More specifically, the distance D y is the distance between a plane 208 passing through the center points of the transport structures 202 of the thermal shield and a plane 210 passing through the center points of the transports structures 202 of the first heat exchanger.
  • D x i, D x2 , dj U bei > d ⁇ U be2, and D y may be modified. As illustrated in Figures 3-5, modifying D x i, D x2 , and D y may provide reduced exposure of radiant heat to the first heat exchanger and reducing or eliminating damage or failure of the transport structures 202 due to overheating and/or exceeding maximum temperatures. Further, the overall heat exchange profile for the system including, in certain embodiments, the heating of water and superheating of steam in the furnace 104, provides improved heat transfer efficiency and increased component life within the furnace 104. In the embodiments represented by Figure 3, D x i and D X2 are depicted as being equal. In other embodiments, D x i and D X2 are not equal.
  • first heat exchanger 112 and subsequent hotter surroundings provide additional heat flux to the side of the water tubes (i.e., thermal shield 110) away from the radiation source 108. With increased spacing, the heat flux to the steam tubes increases due to a decrease in the shielding from the water tubes. [0045] As indicated in the embodiments represented by Figure 5, modifying D y results in a less pronounced effect over the range studied except for when D x1 and D x2 , with D x i and D x2 being equal, are greater than three times djubei and djube2. with djubei and d ⁇ U be2 being equal.
  • Figures 6 through 10 illustrate other embodiments including various configurations modifying D y .
  • the embodiment illustrated by Figure 6 includes the plurality of the transport structures 202 of the thermal shield 1 10 arranged with the plurality of the transport structures 202 of the first heat exchanger 112 attached by means of a plurality of webbed connections 602.
  • the webbed connections 602 provide additional surface area and connectivity between transports structures 202.
  • D y is approximately three times d ⁇ ubei and d ⁇ U be2, with d ⁇ U bei and d ⁇ U be2 being equal.
  • the embodiment illustrated by Figure 7 includes the plurality of the transport structures 202 of the thermal shield 1 10 arranged with the plurality of the transport structures 202 of the first heat exchanger 1 12 such that each of the transport structures 202 of the first heat exchanger 1 12 abuts a portion of one or more of the transport structures 202 of the thermal shield 110.
  • D y is approximately equal to % D x i or % D x2 , (i.e., % D x ) with D x i and D X2 being equal.
  • a small gap may exist between some of the transport structures 202 of the thermal shield 1 10 and the transport structures 202 of the first heat exchanger 112.
  • the embodiment illustrated by Figure 8 includes the plurality of the transport structures 202 of the thermal shield 110 arranged with the plurality of the transport structures 202 of the first heat exchanger 1 12 parallel to the transport structures 202 of the thermal shield 110.
  • D y is approximately 3 to 4 times d ⁇ ubei and d Tu be2, with d Tu bei and d Tu be2 being equal.
  • FIG. 9 includes the plurality of the transport structures 202 of the thermal shield 110 arranged with the plurality of the transport structures 202 of the first heat exchanger 112 parallel to the transport structures 202 of the thermal shield 1 10 and at an equal distance from the radiant source 108 and attached by a plurality of the webbed connections 602.
  • the webbed connections 602 provide additional surface area and connectivity between transports structures 202 to increase heat transfer.
  • D y is approximately zero.
  • the embodiment illustrated by Figure 10 includes the plurality of the transport structures 202 of the thermal shield 1 10 arranged with the plurality of the transport structures 202 of the first heat exchanger 112 parallel to the transport structures 202 of the thermal shield 110.
  • the configuration of Figure 10 includes webbed connection 602 between transport structures 202 of the first heat exchanger 112.
  • the webbed connections 602 provide additional surface area and connectivity between transports structures 202 to increase heat transfer.
  • D y is approximately 3 to 4 times each of dj U bei and d ⁇ U be2. with d Tu bei and d ⁇ ub ⁇ 2 being equal.
  • refractory 1101 may be included as the thermal shield 110 between the transport structures 202 of the first heat exchanger 112 and the radiant source 108.
  • the thermal shield is a non-contact thermal shield 1 10 fabricated from a material arranged to provide controlled radiative heat exposure from the radiant source 108 to the first exchanger.
  • the refractory 1 101 may be comprised of materials such as, for example, alumina, silica, magnesia, and/or lime.
  • the refractory 1101 is shown in addition to the transport structures 202 as the thermal shield 110. Refractory 1 101 provides additional reduction in heat flux to the transport structures of the first heat exchanger 1 12.
  • the refractory 1101 may be integrated into the thermal shield 110.
  • the first heat exchanger 1 12 is configured to transport a near saturation wet fluid or low quality steam (i.e. a water-steam mixture), as opposed to pure steam.
  • a near saturation wet fluid or low quality steam i.e. a water-steam mixture
  • a water-steam mixture may be obtained by using a near saturation wet fluid (water/steam) mixture obtained from the bottom of the steam drum (or similar area with like conditions) rather than utilizing a saturated steam stream from the steam portion of a drum for a sub-critical plant.
  • the energy transferred into the first heat exchanger 112 boils the slightly sub-cooled fluid into a higher enthalpy wet steam which may be directed into the upper low pressure region of the steam drum.
  • the wet steam containing greater enthalpy than the surrounding drum environment may exit the tube bundle in a slightly superheated state due to the lower pressure. This direct mixing serves to potentially deliver a marginally higher quality steam from the drum into the super heater.
  • the low quality steam in first heat exchanger 112 has a much higher heat transfer capacity than pure steam and will serve to protect tubes 202 in 1 12 during both steady state and transient conditions.
  • the steam exiting 112 With increased steam demand from the steam drum during escalation, the steam exiting 112 will be at a slightly more superheated condition relative to the bulk conditions within the steam drum.
  • the increased steam demand from the steam drum, thereby causing a decrease in steam drum pressure will result in increased flow through transport structures 202 in first heat exchanger 112, thereby rapidly increasing the heat removal from transport structures 202 in first heat exchanger 112 in anticipation of an automatic response of the furnace burners to increase firing rate.
  • first heat exchanger 112 If additional sub-cooling for the heat transfer fluid in first heat exchanger 112 is desired, provisions can be made for utilizing a small sub- cooled stream of feed water as an eductive fluid supplying a jet pump to draw water from the steam drum resulting in continuous or additional flow into transport structures 202 of first heat exchanger 1 12. This may be accomplished during all modes of operation utilizing several methods.
  • the disclosure allows for reduced flue gas recycle rates while maintaining heat transfer to the steam/heat transfer fluid system by extracting additional heat in the furnace.
  • the disclosure focuses on a power boiler using water as the heat transfer fluid, other embodiments may be applied to other process heaters where two dissimilar fluids (with regards to heat transfer properties) are heated.
  • additional heat duty in the furnace being taken from the superheat duty
  • economizer duty may also be taken from the furnace in place of the superheat duty.
  • a third row (or more) of tubes may be added in the furnace.
  • the simulation region consists of a 2D rectangular area.
  • One wall boundary was assumed to be at 3140 0 F (2000 K) to mimic hot furnace gases. This boundary temperature was chosen to ensure that the maximum heat flux to the water tube was less than the critical heat flux for water.
  • a mixed boundary condition (convection plus radiation) was applied at the opposite boundary which was assumed to be made of a 1 ft thick refractory brick.
  • a periodic boundary condition was applied at the adjacent sides of the simulation area (see e.g., Figure 15).
  • the water tubes i.e.
  • the thermal shield 110 and steam tubes i.e., the first heat exchanger 112 were 2 inches in outer diameter with a wall thickness of 0.375 inches (0.95 cm).
  • the conductivity of the metal tubes varied with temperature and was assumed to be the same as stainless steel. Both the water and steam tube walls were assumed to have an emissivity of 0.7.
  • the convection boundary condition was applied at the inner walls of the water and steam tubes.
  • the water and steam temperatures were kept constant at approximately 620 0 F and 800 0 F (327 0 C and 427 0 C), respectively.
  • the internal heat transfer coefficients for the water and steam tubes were 50,000 W/m 2 -K and 5,000 W/m 2 -K, respectively.
  • Table 1 details the analysis of a high volatile bituminous coal.
  • Table 2 shows the absorbed heat duty for the furnace (104) and the convection pass (106).
  • Table 1 details the analysis of a high volatile bituminous coal.
  • Table 2 shows the absorbed heat duty for the furnace (104) and the convection pass (106).
  • Table 2 shows the absorbed heat duty for two main boiler zones for a nominal 600 MW supercritical typical pulverized coal boiler. By shifting some of the duty from the connective pass to the furnace according to the present disclosure, the heat and material balance may be estimated for a power boiler.
  • Table 3 shows the firing duty and relative heat duty for the furnace and convection pass for different flue gas recycle (FGR) amounts based on the oxygen concentration in the oxidant for the process configurations and coal combustion defined in Tables 1 and 2.
  • FGR flue gas recycle
  • example 1 is an air-fired combustion boiler for power generation using 650 0 F (343 0 C) preheated air.
  • Example 2 is an FGR simulation using pure oxygen premixed with recycled particulate-free flue gas preheated to about 650 0 F (343 0 C) to closely approximate air combustion heat distribution.
  • Examples 3 through 6 refer to configurations that decrease the amount of flue gas recycled while maintaining the oxidant preheat temperature at about 650 0 F (343 °C).
  • the total duty transferred to the steam system at the turbine conditions defined in example 1 was kept constant. The configuration and the duty of the furnace and convection pass were kept constant for examples 1 and 2 as documented in Table 2.
  • a portion of the duty required for producing steam was shifted from the convection pass to the furnace.
  • the duty absorbed in the furnace beyond 2150 MMBtu/h was used to provide heat to the steam that was previously transferred in the convection pass.
  • the amount of heat duty transferred from the convection pass to the radiant section was adjusted such that the furnace exit gas temperature was consistent with example 1.
  • the remaining duty required for superheating the steam was transferred in the convection pass.
  • the temperatures in the convection pass were checked to ensure that the temperatures in the exchangers did not cross.
  • the overall firing duty was allowed to vary to close the energy balance.
  • the total required firing duty was slightly lower than in example 1 because the duty required for preheating incoming coal and oxidant was only about 84% of that required for example 1.
  • the lower duty for the FGR was due to the lower oxidant mass flow required for preheating in example 2.
  • the radiant duty increased and the total firing duty decreased.
  • the radiant duty had increased about 57% above the air firing case. This result is consistent with the CFD studies that showed that about 60 to 70% of the duty transferred to the high density water heat transfer tubes could be transferred to the lower density steam heat transfer tubes in the furnace.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Supply (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L’invention concerne un système de transfert de chaleur comprenant une source rayonnante, un premier échangeur de chaleur conçu pour permettre l’écoulement d’un premier fluide, et un bouclier thermique conçu pour fournir une chaleur radiative contrôlée depuis la source rayonnante vers le premier échangeur. La source rayonnante est une flamme. Le bouclier thermique est un second échangeur de chaleur conçu pour permettre l’écoulement d’un second fluide ou un bouclier thermique sans contact fabriqué à partir d'un matériau conçu pour fournir une exposition à la chaleur radiative contrôlée depuis la source rayonnante vers le premier échangeur. L’invention concerne également des systèmes de combustion oxy-gaz.
PCT/US2009/058296 2008-09-26 2009-09-25 Système de combustion oxy-gaz comprenant une section convective et une section rayonnante combinées Ceased WO2010036849A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN2009801377799A CN102834668A (zh) 2008-09-26 2009-09-25 具有合并的对流段和辐射段的氧-燃料燃烧系统
CA2733106A CA2733106A1 (fr) 2008-09-26 2009-09-25 Systeme de combustion oxy-gaz comprenant une section convective et une section rayonnante combinees
EP09792981A EP2329194A2 (fr) 2008-09-26 2009-09-25 Système de combustion oxy-gaz comprenant une section convective et une section rayonnante combinées

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12/238,695 US20100077968A1 (en) 2008-09-26 2008-09-26 Oxy/fuel combustion system having combined convective section and radiant section
US12/238,695 2008-09-26

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WO2010036849A2 true WO2010036849A2 (fr) 2010-04-01
WO2010036849A3 WO2010036849A3 (fr) 2012-06-21

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CN (1) CN102834668A (fr)
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WO (1) WO2010036849A2 (fr)

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US8478446B2 (en) * 2008-06-13 2013-07-02 Air Products And Chemicals, Inc. Oxygen control system for oxygen enhanced combustion
US9863013B2 (en) * 2011-02-22 2018-01-09 Linde Aktiengesellschaft Apparatus and method for heating a blast furnace stove
CN103453547A (zh) * 2013-09-05 2013-12-18 哈尔滨锅炉厂有限责任公司 异墙水冷壁结构及介质循环方法

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CN102834668A (zh) 2012-12-19
US20100077968A1 (en) 2010-04-01
CA2733106A1 (fr) 2010-04-01
EP2329194A2 (fr) 2011-06-08
WO2010036849A3 (fr) 2012-06-21

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