EP0698198B1 - Procede et appareil de chauffage de fluides au moyen d'un bruleur par impulsions - Google Patents

Procede et appareil de chauffage de fluides au moyen d'un bruleur par impulsions Download PDF

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Publication number
EP0698198B1
EP0698198B1 EP93915114A EP93915114A EP0698198B1 EP 0698198 B1 EP0698198 B1 EP 0698198B1 EP 93915114 A EP93915114 A EP 93915114A EP 93915114 A EP93915114 A EP 93915114A EP 0698198 B1 EP0698198 B1 EP 0698198B1
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Prior art keywords
fluid
combustion
vessel
pulse
tube
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German (de)
English (en)
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EP0698198A1 (fr
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Momtaz N. Mansour
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Manufacturing and Technology Conversion International Inc
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Manufacturing and Technology Conversion International Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C15/00—Apparatus in which combustion takes place in pulses influenced by acoustic resonance in a gas mass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B7/00—Steam boilers of furnace-tube type, i.e. the combustion of fuel being performed inside one or more furnace tubes built-in in the boiler body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J15/00—Arrangements of devices for treating smoke or fumes
    • F23J15/003—Arrangements of devices for treating smoke or fumes for supplying chemicals to fumes, e.g. using injection devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J15/00—Arrangements of devices for treating smoke or fumes
    • F23J15/02—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material
    • F23J15/022—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material for removing solid particulate material from the gasflow
    • F23J15/027—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material for removing solid particulate material from the gasflow using cyclone separators

Definitions

  • This invention relates to apparatus and processes for treating fluids such as gases, water and other liquids with heat using a pulse combustor.
  • Fluid heating systems known in the art include conventional combustion systems in communication with boiler assemblies. Oil or gas is primarily used in these conventional combustion systems to provide heat to water passing through boiler systems. The heated water or steam is then forwarded for its desired application, such as space heating, turbine operation, or otherwise.
  • a particulate-contaminant-laden gas stream operating such systems can adversely impact the atmosphere as such particulate is released thereto.
  • conventional devices such as cyclones may be used to remove larger particulate matter from combustion gas streams, these devices generally fail to remove smaller particulates such as fly ash from the streams. Similar problems also exist in other gas streams in which the suspended particulate matter originates from other than combustion.
  • Fuel-bound nitrogen also causes nitrogen oxide (NO x ) emissions to form in the gas stream.
  • NO x nitrogen oxide
  • Methods and processes to either reduce the production of nitrogen oxides or to destroy or remove such pollutants from the flue gas stream are necessary to meet the requirements of the Clean Air Act. Economically viable means for removing these pollutants from the exhaust stream before discharging such exhaust into the atmosphere have not heretofore been available.
  • Acoustic agglomeration is a process in which high intensity sound is used to agglomerate submicron- and micron-sized particles in aerosols.
  • This concept is a pretreatment process to increase the average size of entrained particulates to permit high collection/ removal efficiencies using cyclone or other conventional separators.
  • Sound waves cause relative motion between the solid particles, and hence, increase their collision frequency. Once the particles collide, they are likely to stick together.
  • the particle size distribution in the aerosol shifts significantly from small to larger sizes relatively quickly. Larger particles may be more effectively filtered from the carrying gas stream by conventional particulate removal devices such as cyclones.
  • the combination of an acoustic agglomeration chamber with one or more cyclones in series provides a promising high-efficiency system to clean particulate-laden gases such as hot flue gases from pressurized combustors.
  • sirens and air horns require auxiliary compressors to pressurize air.
  • Electromagnetic devices require special designs and precautions to provide the desired equipment reliability, availability and life.
  • powerful amplifiers are required to drive such speakers to deliver 160 decibels (dB) or more of sound pressure.
  • desired system performance goals include dual fuel capability (i.e., coal as primary fuel and a premium fuel as secondary fuel), combustion efficiency exceeding 99 percent, thermal efficiency greater than 80 percent, turndown of at least 3:1, dust-free and semi-automatic dry ash removal, fully automatic start-up with system purge and ignition verification, emissions performance exceeding new source performance standards and approaching those produced by fuel oil-fired commercial-scale units, and reliability, safety, operability, maintainability, and service life comparable to the oil-fired units currently employed for heating fluids.
  • the apparatus and process according to the present invention overcome most, if not all, of the above-noted problems of the prior art and generally possess the desired attributes set forth above by using a pulse combustor to produce a heat source for enhancing the generation of fluid heat, such as the creation of steam.
  • the present invention may be designed to operate in both a slagging and a non-slagging mode.
  • Another object of the present invention is to provide an improved combustor that operates on high sulfur fuel such as coals, while providing for enhanced heat source production and simultaneous, efficient clean-up of particulates produced by the burning of such fuels.
  • Still another object according to the present invention is to provide a high efficiency pulse combustor system to heat a fluid.
  • Another object of the present invention is to provide for contaminant capture and removal of particulate combustion products entrained within a gas stream.
  • Another object according to the present invention is to provide a pulse combustor for producing a heat source for enhanced steam generation.
  • a further object according to the present invention is to provide a slagging pulse combustion system for improved heating of fluids.
  • Yet another object of the present invention is to provide a non-slagging pulse combustion system for improved heating of fluids.
  • the invention provides apparatus for heating a fluid utilizing a fluid heating vessel, such as a fire tube boiler, wherein said vessel has means therein for containing a fluid to be heated and a fluid inlet and outlet means in communication therewith, the vessel having means therein including a fire tube for heat exchange between hot gases passing through the heat exchange means and the said fluid, there being outlet means from the heat exchange means; and the apparatus further having pulse combustion means, e.g.
  • the pulse combustion means being capable of combusting a fuel-air mixture to produce a pulsating flow of hot combustion products and an acoustic wave at a frequency in a range of from 20 to 1,500 Hz
  • the pulse combustion means also including valve means for receiving a fuel-air mixture on demand, a combustion chamber in communication with the valve means and at least one resonance tube in communication with the combustion chamber and the heat exchange means of the fluid heating vessel to supply hot gases to the heat exchange means
  • said apparatus further including means, such as a cyclone, for removal of particulate material from the gas, the pulse combustion means coacting with the heat exchange means so that the pulsating flow of hot combustion products and the acoustic wave supply heat and acoustic vibrations directly to the heat exchange means, a portion of the at least one resonance tube being located within the fire tube of the said vessel for heat transfer therefrom to fluid in that portion of the fluid heating vessel.
  • the invention also provides, from another aspect, a process for heating a fluid comprising the steps of
  • Figure 1 is a schematic of a pulse combusted boiler tube apparatus for heating fluids according to the present invention.
  • FIG 2 is a more detailed schematic view of the pulse combustor means of the apparatus shown in Figure 1.
  • FIG. 3 is a schematic illustration of a valve means for a pulse combustor for use in the present invention.
  • Figure 4 is a schematic illustration of a compact pulse combustor useable in apparatus according to the present invention.
  • Figure 5 is an illustration of a preferred pulse combustion chamber for use in apparatus according to the present invention.
  • Figures 6A and 6B are illustrations of the diodic effect for a diffuser-based aerodynamic valve means for a pulse combustor for use in apparatus according to the present invention.
  • Figures 7A and 7B are illustrations of a tandemly configured set of pulse combustors showing a fuel injection means for each pulse combustor.
  • Figure 8 shows a further embodiment of a pulse combusted fluid heating apparatus according to the present invention.
  • Figure 9 is a schematic illustration of a further preferred embodiment of a pulse combustor for use in apparatus according to the present invention.
  • the preferred apparatus for heating a fluid integrates a pulse combustor means with a fluid treating vessel having means for containing a fluid to be heated and allowing entrance and exit of the fluid therefrom.
  • the fluid treating vessel further has means to allow for the passage of hot gases therethrough that have been are produced by a pulse combustion means, with the gases being in a heat exchange relationship with the fluid to be heated.
  • the apparatus further includes a means for removing particulate entrained in the combustion products flow created by the pulse combustor and may additionally employ an advanced pulse combustion chamber design and valve means.
  • the pulse combustor system according to the present invention is especially useful for burning a solid fuel such as a low grade coal.
  • Advanced coal-fired combustors generally use coal prepared in one of the following forms: dry pulverized coal, dry ultrafine coal, coal-water mixture.
  • Dry pulverized coal is conventional ground coal that typically has a product fineness of 70% through a 74 ⁇ m (200-mesh) sieve and less than 3% surface moisture. This is the cheapest of the three forms.
  • Dry ultrafine coal is a product of an integrated process comprising grinding, drying and beneficiation. Ultrafine coal is thus a fine powder with low ash and sulfur content and is more expensive than dry pulverized coal.
  • Coal-water mixture refers to a mixture of pulverized coal and water with certain chemicals added to enhance stability and flow characteristics. A coal-water mixture fuel is cheaper and safer to transport and store than dry pulverized coal and dry ultrafine coal. The availability of coal-water mixture fuels is, however, rather limited.
  • Pulse combustors can burn all types of coal efficiently (greater than 99% carbon conversion) and without gas support. Dry pulverized coal, however, is more economical to burn and boasts a more mature technology and infrastructure as compared to dry ultrafine coal.
  • the high combustion intensity and the acoustic wave achieved in the pulse combustion permits the use of pulverized rather than ultrafine coal without any performance penalty.
  • sulfur and particulate are easily removable from the combustion product stream wherefore the cheaper, unbeneficiated coal may be advantageously employed.
  • sorbents for produced sulfur derivatives may be injected into the system for this purpose.
  • Exemplary sorbents for sulfur derivatives include limestone, lime, hydrated lime, and dolomite.
  • a particularly preferred sorbent for the present application is Gen-Star limestone with a calcium carbonate content of about 89% by weight.
  • the present invention is particularly useful for heating water to generate steam.
  • the ability of steam to give off heat, promote its own circulation, and permit ease of distribution and control in a heating system are equally advantageous.
  • a significant number of steam-heat installations already exist throughout the world representing a large retrofit market, though many of such systems are fired by petroleum-based fuels which are subject to significant price instability and availability as explained above. It should be appreciated, however, that other fluids such as gases and other liquids may be heated by the apparatus disclosed herein.
  • FIG. 1 One apparatus of the present invention having combustion, heat recovery, and emissions control systems is shown in Figure 1.
  • This embodiment integrates a pulse combustor with a heat recovery system through a main fire tube to a conventional Scotch boiler 20.
  • This particular embodiment is shown operating in a non-slagging mode.
  • a non-slagging mode is achieved by maintaining the temperature of the system below the point at which the particulate formed during combustion and the sorbents, if any, added to the combustion products stream begin to slag (become molten).
  • solid particles must be removed from the hot gas stream.
  • boiler 20 is in communication with a pulse combustion means generally 10.
  • Boiler 20 includes a main fire tube 40 (Morrison tube) and a number of boiler tube conduits 41 for circulation of the hot gases for heating. Although a four pass fire tube boiler is illustrated, a water tube boiler could also be used with obvious modification.
  • Fluid to be heated enters boiler 20 through a fluid inlet means 30, with steam exiting through fluid outlet means 35.
  • Fluid inlet and outlet means 30 and 35 may be any type of conventional couplings which allow fluids to enter or exit a pressurized container.
  • fluid inlet means 30 allows water to enter the fluid treating vessel and fluid outlet means 35 allows steam to exit. Additionally, as shown, water may exit vessel 20 feeding a water jacket 17 around a portion of pulse combustor means 10 through line 31, with steam exiting jacket 17 and being routed to boiler 20 via line 36.
  • Pulse combustor means 10 includes a valve means 12 which may be an aerodynamic valve (fluidic diode), a mechanical valve or the like, a combustion chamber 14 and one or more tailpipes or resonance tubes 16. Additionally, pulse combustor means 10 may include an air plenum 18 and a thrust augmenter (not shown).
  • a valve means 12 which may be an aerodynamic valve (fluidic diode), a mechanical valve or the like, a combustion chamber 14 and one or more tailpipes or resonance tubes 16. Additionally, pulse combustor means 10 may include an air plenum 18 and a thrust augmenter (not shown).
  • Pulse combustor means 10 of Figure 1 is more readily seen in Figure 2, wherein like numerals represent like members.
  • a plurality of resonance tubes 16 extend into main fire tube (or Morrison tube) 40. Water may be contained within the shell of main fire tube 40 in a conventional fashion.
  • the pulse combustor unit shown in Figure 2 additionally may employ flanges 62 and expansion joints 67 as necessary for connection to boiler 20.
  • Resonance tubes 16 may employ a number of different designs.
  • the tube may flare continuously outwardly (shown in the embodiment of Figure 8) allowing the entire resonance tube 16 to act as a diffuser. Such diffusion reduces gas exit velocity from combustion chamber 14 and provides for recirculation of combustion products and increased particulate residence time within pulse combustor means 10.
  • a compact pulse combustor design employing a spiral-shaped resonance tube 16 is shown in Figure 4.
  • resonance tube 16 is surrounded by a water jacket 90 so that steam created by the heat in resonance tube 16 may be removed from the system and directed to a boiler or other heated fluid device.
  • resonance tube 16 may be essentially straight as in Figure 1, but have at its outer end a diffuser section that consists of an outwardly flaring tailpipe section.
  • resonance tube 16 may integrate a diffuser section at the end nearest combustion chamber 14 with an essentially straight tube extending therefrom (shown in Figure 9).
  • pulse combustor means 10 When operated as described hereinbelow, pulse combustor means 10 produces a pulsating flow of hot combustion products with an acoustic wave having a frequency in a range of from about 20 to about 1500 Hz.
  • a pulsating flow of hot combustion products exits combustion chamber 14 and passes into resonance tubes 16 of pulse combustor means 10 and tubes 16 may or may not be water jacketed as the system dictates.
  • the end of Morrison tube 40 opposite pulse combustor means 10 acts as a decoupler section 50 where the hot combustion products stream exits resonance tubes 16 and begins passage through the arrangement of conduits 41 of boiler 20.
  • An ash drop-out chute 60 or other means may also be provided for removing a portion of the particulate within the gaseous combustion product stream.
  • Location of chute 60 in decoupler section 50 of Morrison tube 40 removes significant particulate from the gas stream prior to gas passage through the rest of boiler 20.
  • An impact or inertial solid separator is one of the alternative means that may be used to effect partial removal of particulate from the gas stream.
  • the hot combustion product stream exits resonance tube 16 at decoupler section 50 and then enters into conduit 41 to begin its passage through boiler 20. Prior to entering conduit 41, a portion of the larger particles entrained within the combustion product stream tend to separate from the gaseous stream.
  • These particulates may then be collected and removed through ash drop-out chute 60 as the gas stream makes its first turn within the hot gas passage means.
  • These larger particles include acoustically agglomerated dry ash and spent sorbent which may be entrained in the gaseous stream.
  • the residual particulate matter in the gaseous stream remains essentially entrained within the gaseous stream during its pass through boiler conduits 41.
  • pulse combustion means 10 may operate at a temperature below the slagging point of the particulates contained within the gas stream so that solids remain suspended.
  • pulse combustion means 10 When operated in a non-slagging dry ash rejection mode, the need for a refractory-lining for combustion chamber 14 and resonance tubes 16 is eliminated, but a multiple resonance tube arrangement employing four (4) or more tailpipes may become necessary.
  • a further benefit of operating in a non-slagging mode is the potential for reduced nitrogen oxide emissions and improved sulfur capture. Lower temperatures enhance the control of both of these contaminants. Additionally, multiple air staging may be employed for further controlling nitrogen oxide emissions. The incorporation of multiple air staging with near stoichiometric or substoichiometric combustion in combustion chamber 14 and tailpipe 16 by secondary air addition into decoupler section 50 also lowers nitrogen oxide emissions.
  • Boiler conduits 41 may be arranged within boiler 20 in a conventional serpentine-like pattern within the fluid to be heated. As the hot gas stream passes through boiler 20, heat is transferred to the fluid surrounding conduits 41. As previously mentioned, however, a water tube boiler may also be employed with fluid to be heated circulated through a conduit and with the hot gases surrounding same. The heated fluid may be supplied to other applications such as space heating.
  • FIG. 1 After exiting boiler 20, the hot gases are fed to a further means for removing a substantial portion of the remaining particulate material entrained therein.
  • Conventional particulate collection/removal means for this purpose are denoted in Figure 1 at 70.
  • Such conventional systems include one or more cyclones or other solids separators. From cyclone 70, the gas is allowed to escape to the atmosphere through a flue gas exhaust. Collected fly ash and other particulate matter, including sorbent that may have been injected into the system for sorption of contaminants, is removed through separator 70.
  • An induced draft fan 80 may be placed along the hot gas passage means and adjusted to preferably maintain zero gauge static pressure within decoupler section 50. Additionally, a forced draft fan 90 may be employed for supplying primary air to air plenum 18. Air plenum 18 operates as a capacitor and seeks to provide primary air to the pulse combustion means 10 at approximately constant static pressure. The pressure boost developed due to pulse combustion within the present apparatus also reduces the size, power requirements, and cost of forced draft fan 90 and induced draft fan 80.
  • a sorbent such as hydrated lime, lime, limestone, or dolomite may be injected into pulse combustor means 10, or anywhere along the hot gas passage means when operated in a non-slagging mode, to effect sorption of contaminants present in the hot gaseous stream.
  • the above-noted sorbents are useful in removing sulfur derivatives such as sulfur dioxide from the gas stream.
  • a means may be provided for injecting a particulate having a size different than the size of the particulate entrained within the combustion product stream.
  • Bimodal agglomeration occurs whereby particulates of differing sizes are agglomerated with acoustic enhancement being provided by pulse combustor means 10.
  • Pulse combustor means 10 produces an intense acoustic wave by combustion-induced pressure oscillations when fired with a fuel.
  • the acoustic field produced by combustion resonates through resonance tubes 16 acting directly on the gaseous stream carrying the particulates to effectuate acoustically-enhanced bimodal agglomeration of the particulates in the gaseous stream. Because the agglomerates are larger in size, enhanced removal of the agglomerated particulate is permitted either at the first turn of the hot gas passage means by ash drop-out chute 60 or at the downstream location of removal means 70.
  • the particulate used to enhance acoustic agglomeration and/or capture contaminants is preferably introduced into the system near the junction of pulse combustion chamber 14 and resonance tubes 16.
  • the interface between resonance tubes 16 and combustion chamber 14 is a region of high heat release and high heat transfer.
  • the high heat provides for a rapid rate of sorbent calcination, further providing for high porosity in the calcined sorbent which, in turn, generates high surface-to-mass ratio without the need for micronization of the sorbent. This, together with the effects of the oscillating flow field, enhances sorbent utilization at relatively low calcium-to-sulfur molar ratios on the order of about 2.5.
  • the design of the present apparatus may operate at low pressures [less than 2.1 bar (30 psig) and, preferably, about 1.0 bar (15 psig)], for saturated steam generation.
  • the boiler shell utilized in the present invention may be one designed initially for oil and gas fired systems.
  • the apparatus disclosed herein has space requirements similar to those for oil- and gas-fired boilers.
  • coal combustors operate at sufficiently high temperature by controlling the stoichiometry of the combustion air to near stoichiometric, in an adiabatic combustion chamber, so that ash becomes molten and is removed in the form of slag from the flue gas.
  • the high temperatures at which the slagging combustors must operate tend to increase the amount of nitrogen oxides produced in the combustion process. This, in turn, generally requires other means downstream from the coal combustor to reduce the concentration of nitrogen oxides in the effluent gas stream.
  • the high combustion temperatures in the slagging combustors are also inappropriate for sulfur sorbent introduction at pulse combustor 10, for when added, the sorbents also slag, thus destroying their capability to effect sorption of contaminants.
  • Pulse combustor means 10 may be designed for dual-fuel capacity.
  • the primary fuel may be coal and the secondary fuel natural gas.
  • the secondary fuel not only enables rapid start-up of the unit but also provides back-up in case of disruption in primary fuel supply.
  • a pulse combustor typically operates in the following manner. Fuel and air enter into combustion chamber 14 and an emission source detonates the explosive mixture during start-up. The sudden increase in volume, triggered by the rapid increase in temperature and evolution of combustion products, pressurizes chamber 14. As the hot gas expands, the valve means 12, preferably a fluidic diode, permits preferential flow in the direction of resonance tube 16. The gaseous combustion products stream exiting combustion chamber 14 and resonance tube 16 possesses significant momentum. A vacuum is created in combustion chamber 14 due to the inertia of the gases within resonance tube 16. The inertia of gases in resonance tube 16 permit only a small fraction of exhaust gases to return to combustion chamber 14, with the balance of the gas exiting through resonance tube 16. Because the chamber pressure is then below atmospheric pressure, air and fuel mixtures are drawn into chamber 14 where auto-ignition takes place. Again, valve means 12 constrains reverse flow, and the cycle begins anew. Once the first cycle is initiated, engine operation is thereafter self-sustained.
  • the valve means utilized in many pulse combustion systems is a mechanical "flapper valve".
  • the flapper valve is actually a check valve permitting flow from inlet to the combustion chamber, and constraining reverse flow by a mechanical seating arrangement.
  • a mechanical valve may be used in conjunction with the present system, an aerodynamic valve without moving parts is preferred.
  • an aerodynamic valve With an aerodynamic valve, during the exhaust stroke, a boundary layer builds in the valve and turbulent eddies choke off much of the reverse flow.
  • the exhaust gases are of a much higher temperature than the inlet gases. Accordingly, the viscosity of the gas is much higher and the reverse resistance of the inlet diameter, in turn, is much higher than that for forward flow through the same opening.
  • pulse combustion creates a self-aspirating engine, drawing its own air and fuel into combustion chamber 14 and auto-igniting combustion products.
  • the preferred pulse combustor used herein for coal-firing is based on a Helmholtz configuration with an aerodynamic valve.
  • the pressure fluctuations which are combustion-induced in the Helmholtz resonator-shaped combustor, coupled with the fluidic diodicity of the aerodynamic valve, causes a bias flow of air and combustion products from the combustor's inlet to the exit of resonance tube 16. This results in the combustion air being self-aspirated by the combustor and for an average pressure boost to develop in the combustion chamber to expel the products of combustion at a high average flow velocity (over 1,000 feet/second) through resonance tube 16.
  • the rapid pressure oscillation through combustion chamber 14 generates the intense oscillating flow field.
  • the fluctuating flow field causes the products of combustion to be swept away from the reacting solid coal thus providing access to oxygen with little or no diffusion limitation.
  • pulse combustors experience very high mass transfer and heat transfer rates within the combustion zone. While these combustors tend to have very high heat release rates, (typically ten times those of conventional burners), the vigorous mass transfer and high heat transfer within the combustion region result in a more uniform temperature. Thus, peak temperatures attained are much lower than in the case of conventional systems. This results in a significant reduction in nitrogen oxides (NO x ) formation as previously noted.
  • the high heat release rates also result in a smaller required combustor size for a given firing rate and a reduction in the required resonance time.
  • a pulse combustion chamber design of the type shown in Figure 5 is preferred.
  • This design employs quadratic form generators to define an axisymmetric geometry that would be alike to accommodate a number of design and chamber performance attributes.
  • Alphanumeric legends on the pulse combustor illustrated in Figure 5 correspond to following dimensions which relate to a slagging combustor design (as described hereinafter) having a heat output of 2200 kW (7.5 MMBtu/hr) and may be used for determining other pulse combustor designs.
  • Inlet port 100 has a diameter of 14.4 cm (5.69 inches) and exit port 101 has a diameter of 12.8 cm (5.06 inches).
  • L 1 is 41.1 cm (16.17 inches); L 2 is 10.5 cm (4.15 inches), L 3 is 10.9 cm (4.31 inches), L 4 is 8.6 cm (3.40 inches) with a combined length of the combustion chamber from inlet port 100 to exit port 101 of 71.2 cm (28.03 inches).
  • the angle ⁇ is 40°, length R1 is 63.9 cm (25.15 inches).
  • length R2 is 16.4 cm (6.46 inches), length R3 is 10.9 cm (4.31 inches and length R4 is 8.6 cm (3.40 inches).
  • Pulse combustor systems of the present invention regulate their own stoichiometry within their range of firing without need of extensive controls to regulate the fuel feed to combustion air mass flow rate ratio.
  • the strength of the pressure pulsations in combustion chamber 14 increases, which, in turn, increases the amount of air aspirated by the aerodynamic valve.
  • the combustor automatically maintains a substantially constant stoichiometry over its designed firing range.
  • the induced stoichiometry can be changed by modifying the aerodynamic valve fluidic diodicity.
  • FIG. 3 An aerovalve as shown in Figure 3 may also be employed in the present invention so that the acoustic pressure wave of the pulse combustor is tunable.
  • a stationary sleeve is in communication with combustion chamber 14, with the aerovalve 12 located therein for to and from movement therealong.
  • Valve 12 is in turn connected to a control means such as a linear actuator 48 which imparts desired movement to valve 12.
  • movement of valve 12 modifies the fuel residence time in advance of combustion chamber as well as the stoichiometry.
  • valve 12 is closer to chamber 14, less residence time is available. Increased residence time permits more fuel-air mixing as well as more devolatilization of the fuel.
  • a fuel-air mixture may be introduced through inlet pipe 45 extending through plenum 18, a sorbent injection site 47 may be employed therealong, with axial adjustment afforded as by a linear actuator 49.
  • FIG. 6A and 6B A further illustration of the diodic effect of the chamber's inlet and exit diffusers using the attributes of the diffuser-based aerodynamic valve design is shown in Figures 6A and 6B.
  • two simple, opposite conic diffuser sections comprise the aerodynamic valve.
  • a steep diffuser angle is used which can be between 40° and 60° (half cone angle).
  • a generous shallow angle diffuser is used to provide for efficient pressure recovery (4° to 7°).
  • the length of the diffuser sections and the minimum aerodynamic valve diameter are selected to meet the combustor integration and performance requirements. Through these variables the overall fluidic diodicity and minimum recharge resistance for a given mean flow rate can be modified.
  • Air intake flow characteristics are shown in Figure 6A.
  • the boundary layer build-up which is monotonic in the direction of the flow, is compensated for by the diverging cross-sectional area of the shallow diffuser section.
  • the intake stream also draws from a large area near the valve intake since there is no flow separation on intake from the steep diffuser because of the flow acceleration from a large to a narrow cross-section.
  • two (2) pulse combustors may be arranged in a tandem configuration wherein the combustion chambers and tailpipes constitute a common fire tube (not shown).
  • the tandem operation employs a 180° phase lag between each combustor unit and results in super-positioning of acoustic waves and cancellation of the fugitive sound emissions.
  • a tandem configuration also provides for automatic fuel phasing and super charging. However, the amount of fuel forcibly injected into the pulse combustor during the exhaust phase is reduced in some tandem designs. Such injection may be undesirable since fuel particles are rapidly and prematurely conveyed out of the pulse combustion chamber, thereby resulting in a low combustion efficiency.
  • FIG. 7A and 7B An alternative embodiment utilizing tandem combustors that more effectively reduces injection of fuels during the exhaust phase and is preferred is shown in Figures 7A and 7B.
  • fuel feeds along a main fuel line tee 150 with one leg of the tee connected to each of the tandem combustors.
  • Fuel tee 150 acts as a coupling allowing automatic fuel biasing between pulse combustor chambers 160 and 170.
  • Efficient phasing of fuel in fuel tee 150 is effected by the ability to operate tandem pulse combustor chambers 150 and 160 180° out of phase. Under these conditions, one combustion chamber achieves a low pressure phase just as the other chamber simultaneously achieves a high pressure phase.
  • Tailpipe coupling is an effective approach due to the super-charging action of the high momentum exhaust fluids which allow unburned particles to be retained within the influence of the intense fluctuating combustion product flow field at the exhaust region for a longer period of time.
  • the apparatus of the present invention may also be designed to run in a slagging mode where the temperature of the system is at least that required to cause the particulates within the gas stream to slag.
  • a design for a slagging combustor according to the present invention is shown in Figure 8 wherein like numerals represent like members discussed with respect to Figure 1.
  • a slag tap 310 is kept hot with an auxiliary burner so that slag remains molten and flows into a slag collection vessel without plugging the collection port.
  • Resonance tube 16 and water-cooled decoupler section 300 are configured in a U-shape in Figure 8 to accommodate limited space requirements.
  • a refractory-lined combustion chamber 14 and resonance tube 16 may be required.
  • a slag tap 310 is provided at the bottom of decoupler 300 and may be any type of outlet capable of removing slag from the system. As shown, slag will generally form on the inner walls of resonance tube 16 and decoupler section 300 and drain towards slag tap 310 where it will remain heated for removal in conventional fashion.
  • Figure 8 also shows previously-mentioned thrust augmenter 19 in communication with valve means 12 and contained within air plenum 18.
  • means When operated in the slagging mode, means should be provided for introducing sorbent for contaminant capture downstream from pulse combustor means 10.
  • the lower temperatures downstream allow the sorbent to remain in solid form, thus allowing the sorbent to adequately effect sorption of the contaminants.
  • such means for introducing the sorbent are shown downstream from decoupler section 300 at inlet 330.
  • the means for introducing the sorbent may include any conventional port for allowing introduction of particles into a pressurized chamber.
  • a scrubber unit 360 is shown for further cleaning of the particulates from the gas stream prior to emitting the gas into the atmosphere.
  • FIG. 9 Another embodiment of pulse combustor means 10 which can be used in this invention, showing additional features thereof, is shown in Figure 9.
  • Figure 9 shows resonance tube 16 water cooled with a water jacket 90 therearound.
  • Figure 9 shows the previously-described configuration of resonance tube 16 wherein resonance tube 16 flares outwardly immediately from combustion chamber 14, but then becomes straight therebeyond.
  • length A is 95.9 cm (14.15 inches)
  • length B is 91.4 cm (36.00 inches)
  • length C is 194.7 cm (76.67 inches).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Feeding And Controlling Fuel (AREA)

Claims (13)

  1. Appareil pour chauffer un fluide utilisant un récipient (20) de chauffage de fluide, tel qu'une chaudière à tubes de fumée, dans lequel ledit récipient comporte des moyens dans sa partie interne pour contenir un fluide à chauffer et des moyens (30, 35) d'entrée et de sortie du fluide en communication avec ceux-ci, le récipient (20) comportant des moyens (40, 41) dans sa partie interne qui comprennent un tube (40) de fumée en vue d'un échange de chaleur entre des gaz chauds traversant les moyens (40, 41) échangeurs de chaleur et ledit fluide, des moyens de sortie étant prévus à partir des moyens (40, 41) échangeurs de chaleur ; et l'appareil comportant de plus des moyens (10) de combustion à impulsions, par exemple quadratiques ou accordables, en communication avec les moyens (40, 41) échangeurs de chaleur du récipient (20) de chauffage du fluide, les moyens (10) de combustion à impulsions étant adaptés pour brûler un mélange de combustible et d'air afin de produire un flux pulsé de produits de combustion chauds et une onde acoustique à une fréquence comprise dans une gamme de 20 à 1500 Hz, les moyens (10) de combustion à impulsions comprenant aussi un moyen (12) formant vanne pour recevoir un mélange de combustible et d'air sur demande, une chambre de combustion (14) en communication avec le moyen (12) formant vanne et au moins un tube (16) à résonance en communication avec la chambre de combustion (14) et les moyens (40, 41) échangeurs de chaleur du récipient de chauffage du fluide pour fournir des gaz chauds aux moyens (40, 41) échangeurs de chaleur, ledit appareil comprenant de plus des moyens, tels qu'un cyclone (70), pour éliminer des gaz une matière en particules, les moyens (10) de combustion à impulsions coopérant avec les moyens (40 41) échangeurs de chaleur de sorte que le flux pulsé de produits de combustion chauds et l'onde acoustique fournissent de la chaleur et des vibrations acoustiques directement aux moyens (40, 41) échangeurs de chaleur et une partie du au moins un tube (16) à résonance étant située à l'intérieur du tube de fumée (40) dudit récipient (20) pour transférer la chaleur depuis celui-ci vers le fluide dans cette partie du récipient (20) de chauffage du fluide.
  2. Appareil tel que défini dans la revendication 1, dans lequel ledit appareil peut être utilisé à une pression comprise dans une gamme allant de 1 à moins de 2,1 bars.
  3. Appareil tel que défini dans la revendication 1, dans lequel une partie desdits moyens (10) de combustion à impulsions et l'au moins un tube (16) à résonance des moyens (10) de combustion à impulsions sont munis d'une enveloppe (17, 90) pour un refroidissement par eau.
  4. Appareil tel que défini dans la revendication 1, dans lequel les moyens pour éliminer la matière en particules sont situés en aval du récipient (20) de chauffage du fluide.
  5. Appareil tel que défini dans la revendication 4, comprenant de plus des moyens (60) situés le long d'une partie initiale des moyens (40, 41) échangeurs de chaleur pour éliminer partiellement desdits gaz les traversant, la matière en particules.
  6. Appareil tel que défini dans la revendication 5, dans lequel les moyens (40, 41) échangeurs de chaleur comprennent au moins un tube (41) qui traverse le récipient (20) selon un trajet sinueux qui fait plusieurs passes en va-et-vient à travers le récipient, et dans lequel les moyens (60) d'élimination partielle de la matière en particules sont situés en amont d'un emplacement où le tube inverse le sens de son trajet dans le récipient.
  7. Appareil tel que défini dans la revendication 1, dans lequel le moyen (12) formant vanne d'alimentation en combustible des moyens (10) de combustion à impulsions est réglable dans les deux sens par rapport à ladite chambre de combustion (14).
  8. Procédé pour chauffer un fluide comprenant les étapes consistant à :
    a) faire passer un fluide à chauffer à travers un récipient (20),
    b) faire brûler par impulsions un combustible dans un dispositif (10) de combustion à impulsions communiquant avec le récipient (20), le dispositif (10) de combustion à impulsions comportant au moins un tube (16) à résonance, une partie du au moins un tube à résonance (16) étant située à l'intérieur d'un tube (40) de fumée du récipient (20), ledit au moins un tube (16) étant opérationnel pour produire un flux pulsé de produits de combustion et une onde de pression acoustique à une fréquence d'environ 20 à environ 1 500 Hz, et introduire directement le flux de produits de combustion et l'onde de pression acoustique dans le récipient (20) pour effectuer ainsi un transfert de chaleur vers le fluide contenu dans le récipient (20) afin de chauffer le fluide d'une manière prédéterminée,
    c) éliminer du flux de produits de combustion les matières en particules, et
    d) transférer ledit fluide chauffé pour qu'il remplisse la fonction à laquelle il est destiné de servir de source de chaleur à divers moyens de chauffage.
  9. Procédé selon la revendication 8, dans lequel les moyens (10) de combustion à impulsions sont utilisés à une température inférieure au point de scorification des produits de combustion du combustible qui y est brûlé.
  10. Procédé tel que défini dans la revendication 8, dans lequel la pression dans le récipient où le fluide est chauffé est maintenue à un niveau inférieur à 2,1 bars.
  11. Procédé tel que défini dans la revendication 8, comprenant de plus l'étape d'introduction dans le flux de produits de combustion, d'une matière en particules ayant une distribution de grosseur ou granulométrique différente de celle de la matière en particules résultant de ladite combustion par impulsions pour effectuer une agglomération bimodale de ladite matière en particules, et, facultativement la matière en particules introduite est un sorbant pour les contaminants contenus dans le flux de produits de combustion.
  12. Procédé tel que défini dans la revendication 11, dans lequel ledit contaminant est un produit du soufre et la matière en particules est un sorbant pour celui-ci.
  13. Procédé tel que défini dans la revendication 8, comprenant une étape d'élimination partielle de la matière en particules agglomérée du flux de produits de combustion avant que le flux ne sorte dudit récipient (20).
EP93915114A 1993-05-17 1993-05-17 Procede et appareil de chauffage de fluides au moyen d'un bruleur par impulsions Expired - Lifetime EP0698198B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1993/004715 WO1994027087A1 (fr) 1993-05-17 1993-05-17 Procede et appareil de chauffage de fluides au moyen d'un bruleur par impulsions

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EP0698198A1 EP0698198A1 (fr) 1996-02-28
EP0698198B1 true EP0698198B1 (fr) 1999-12-08

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AT (1) ATE187541T1 (fr)
AU (1) AU4522193A (fr)
DE (1) DE69327256T2 (fr)
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ES (1) ES2139015T3 (fr)
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US9039407B2 (en) 2006-11-17 2015-05-26 James K. McKnight Powdered fuel conversion systems and methods
EP2094970B1 (fr) 2006-11-17 2017-01-11 Summerhill Biomass Systems, Inc. Combustibles en poudre, leurs dispersions, et dispositifs de combustion y relatifs

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DE1066313B (de) * 1959-10-01 Deutsche Babcock &. Wilcox-Dampfkessel-Werke Aktien-Gesellschaft, Oberhausen (RhId.) Feuerung zur Verbrennung von feinkörnigen Brennstoffen mit Hilfe von Longitudinalschwingungen der Feuergase
US4708159A (en) * 1986-04-16 1987-11-24 Nea Technologies, Inc. Pulse combustion energy system
DE3839861A1 (de) * 1988-11-25 1990-05-31 Rudi Pedersen Heizanlage
US5059404A (en) * 1989-02-14 1991-10-22 Manufacturing And Technology Conversion International, Inc. Indirectly heated thermochemical reactor apparatus and processes

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DE69327256D1 (de) 2000-01-13
AU4522193A (en) 1994-12-12
ATE187541T1 (de) 1999-12-15
WO1994027087A1 (fr) 1994-11-24
DK0698198T3 (da) 2000-04-17
EP0698198A1 (fr) 1996-02-28
DE69327256T2 (de) 2000-03-30
ES2139015T3 (es) 2000-02-01
GR3032607T3 (en) 2000-05-31

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