|Publication number||CA2122829 C|
|Application number||CA 2122829|
|Publication date||18 Jun 2002|
|Filing date||9 Nov 1992|
|Priority date||18 Nov 1991|
|Also published as||CA2122829A1, EP0679206A1, US5205728, US5366371, WO1993010398A1|
|Publication number||CA 2122829, CA 2122829 C, CA 2122829C, CA-C-2122829, CA2122829 C, CA2122829C, PCT/1992/9740, PCT/US/1992/009740, PCT/US/1992/09740, PCT/US/92/009740, PCT/US/92/09740, PCT/US1992/009740, PCT/US1992/09740, PCT/US1992009740, PCT/US199209740, PCT/US92/009740, PCT/US92/09740, PCT/US92009740, PCT/US9209740|
|Inventors||Momtaz N. Mansour|
|Applicant||Momtaz N. Mansour, Manufacturing And Technology Conversion International, Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Classifications (14), Legal Events (2)|
|External Links: CIPO, Espacenet|
<<,....~ ~~ 9~/1039~ ~ PCTlUS92l09740 l~ PROCESS AIdD APPARATUS USING A PI1Y~SE COP~iBUST4~
g'C7Fi ~.T~IvtTZING ~IQUIl7S ~1ND aLURFZ3ES
~~~i~ld of th~~,'~Yg. on ~hi.s imrenti~n relates to apparatus and processes wing a pulse combustor to atomize liquids or aav~ri~s.
,~,~ckarau~l~l of the Invention 1~ atomization of li.~quids .and ~lurri.es is important f~r ~t~ny syst.~ms. Particularly, ato:a.i~atic~n of fuels for co~rbustion and ga~ification app~.ications is a key a~tep in attaining proper performance in such ~pp~i~.rati~~~AS..~u~ltha4 ~a~.~r b~~n. at~~i?r~d .LnLa ~.5 s:nall,er partio~.es typically enables mare eo:npl~te oc~~bustian, taigh~~r cambust~.on ten~p~raaures, and better aiding of the fuel witty air sc~ as to increase c~~u~t~~n~~~~~.r.l.~n~iyo ~rian~ril~, two types e~f atomisers are in use tAd~y: (1) ~ic~h ~~'essure single-tZuid at.omize~es (~h~wn in Fic~are 1) end (2) dual-fluid atomizers (Btaown irt Fic~re~ 2,~~ ~~ and 3 ) : In the h~.gh pressure single-f'luidl ~t~mi~ers, a liquid ~x' slurry 9~uel is pres~ur3.~Qdl t~ an el~vat~d pressure ~ataich ~rape2s the ~~el ~t h~c~h kin~t~.c ~nerc~y through an orifice into a ~e~~~l~ injector. The atomised u.~l, heaving 'the n~zzle ~~~~~t~r ~~~ t~~r~ ~pr~.y~d:~nto. a ~ra~bust~r ~..ha~b~s~a the. high velocity of the fuel s~pra~ in tusrn provides tsar better ~ixinc~ of the fuel ' and eair and results in ~cxre ~~fi~cien~ c~mbustor performance:
A high pressure jingle-~l,uic3' ato~ni~er as shown i.n ~'fgear~: 1 employs ~ high pressure pump to rare the $
.i ~~~~~u~~ ~f t~~: ~i~u~d LuGI ~~d. t.~dr~~~ th~ at~~~.~r~~r s ~''1 .~
ii i f i .~
~uriz~d fluid:.:-expandst~r~ur~?at'~~ noz~l~a Boas es ~
a a ~
e ~5 tc~ impart a high vel~ci~ty to the ~~.uid, resulting in a~ a~~~i~ed sprayp the pump oper~t on may be ~;J~S"~1T~JT~ ~~f~~'1"
WO 93/10398 PCT/L~S92/(t~"'~U
continuous or intermittent, with intermittent pumps being employed for fuelinjected internal combustion piston applications such as diesel and gasoline engines.
an dualfluid atomizers, a separate atomization fluid is employed to achieve atomization of the liquid or slurry fuel. Generally, dual-fluid atomizers are either internally mixed as shown in Figures 2A and 2B
or externally mixed as shown in Figure 3. In internally mixed, dual-fluid atomizers, the atomizing fluid meets the fuel within an atomization chamber and the mixture is ejected at high velocity from a nozzle to form the atomized fuel spray. One such dual-fluid atomizer shown in Figure 2A emplays a Y-jet design where the atomization fluid (generally gas or steam) meets the liquid or slurry fuel at an acute ani~le.
Another dualfluid atomizer shown in Figure 2B employs an eductor Tjet design where the atomization fluid flow meets the liquid or slurry fuel at a right angle.
Such-atoanizers may operate as eductors and, in some applications, no pump is required for fuel introduction. In both of the internally mixed, dual-fluid atomizers described, mixing of the atomization fluid and the liquid or slurry fuel occur internally 25 within the body of the atomizer before the atomized fuel spray leaves the atomizer.
~n externally mixed, dual-fluid atomizers such as tie one shown in Figure 3, the atomizing fluid meets the liquid ~r slurry fuel s~uts~.de the body of the ' i~tixing of the atomization fluid with the atomizer 3~ , , f~~l~ outside the atdmi~er is particularly useful when coal slurries and viscous liquid fuels such as . r~~iduai ofls are employed. Such highly abrasive or highly viscous fuels tend to cause rapid erosion of 35 the .inner surfaces of the atomizer when an internally .. ~7L»~
2 ~ ;,~ i;: 0 r:~ .
<-' ' dV~ 93/1Q398 - . PCTIL~S921~19~'49~
mixed atomizer is employed. By mixing the atomizati~n fluid and fuels outside the body of the atomizer, rapid erosion is lessened.
In the particular externally mixed, dual-fluid atomizer shown in Figure 3, an annular cavity distributes the liquid fuel or slurry around a supersonic jet of atomizing fluid. A film of liquid fuel is sheared by the supersonic flow of the atomizing fluid through the cavity to produce an atom~.zed fuel spray. Fuel enters into the path of an atomization fluid after the atomization fluid exits from a supersonic nozzle. The atomization fluid i.s pr~vided with sufficient velocity to sheer the fuel droplets ~.nto an acceptable atomized fuel spray.
As previously mentioned, high pressure, single--fluid atomizers are generally employed in diesel enga.nes and'similar fuol-injection applications, particularly when the flow rate profile versus time is to be controlled. Pressures employed in such singhe-~0 fluid atomizers can be in exdess of l0,aoa pounds per square inch, Where large power plants and boilers are inv~lved, dual-f7:uid atomizers are generally preferred. Liquid fuel in such applications need nat 25 be pressurised to high levels, with pressures in the range of from aborat 50 to. about 250 pounds per square inch'being acceptable, In each of the dual=fluid ystems previously described, the atomization fluid typically employed is 30 a compressible fluid such as air or seam. In dompre~ssed air sxstems, 'pressures in the range of ~r~~a abotat 20 to about 180 pounds per square inch are generally used. Where steam is employed, th:~ pressure.
range is general~:y from about 50 pounds per square NJC~ 93114398 FCT/L~S92J~"""'~,40 :, r 2~.~~u~~~ ~
inch to about 600 pounds per square inch depending on the application requirements.
With respect to the internally mixed atomizers, the ratio of atomization fluid to liquid fuel varies ' g from about 0.07~to about 0.60 pounds of atomization fluid per pound of liquid fuel being atomized. For the externally mixed, dual-fluid atomizers, more atomization fluid flow is required. The amount of atomizativn.fluid in such atomizers ranges from about 1,p 0..40 to about 3.0 pounds per pound of liquid fuel being atomized.
As may be expected with such prior art atomizers, a large amcaunt of parasitic power is consumed by the . - aix~ compressors to supply the atomization fluid.
Although in internally mixed dual-fluid atomizers, as little as 1.50 of the entire plant output comprises the parasitic air power, externally mixed, dual-fluid atomizers typically require as much as 1~% of total Parker plaht output to operate the compressors>
20 Moreover, as more viscous and more abrasive fuels are employed, the amount of air required for atomization increases substantially. In addition, large amounts of atomization air are required, particularly in tie externally mixed atomizata:on processes, resulting in ~5 the need for onormous compressors which require a s~:gnificant parti~n o~ .p~.ax~t output for operating.
In summary, typical prior art atomizers require large amaunts of compressed air or other fluid for atomisation. Moroover; the ~.nternally mixed, dual-30 fluid atomizers often incur erosion problems.
p~ocorcli.ngly, an efficior~t, ion-eroding atomiz'atiori pr~cess which does not require a substantial amount of parasitic power is needed.
the ,~ppsrstus and processes 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 combustion apparatus to atomize fuels. The present atomization apparatus may be designed to supply atomized fuel to combustion, gasification, and other systems which employ atomized liquid or slurry streams.
Summary of the Invention The present invention provides improved atomization apparatus and processes for liquids and slurries.
The present invention also provides an improved atomizer employing a pulse combustor for atomization of liquids and slurries.
The present invention also provides a high efficiency fuel atomizer employing a pulse combustor to atomize the fuel.
The present invention also provides a novel atomizer for liquids and slurries that does not have the parasitic power requirements of atomizers heretofore known.
The present invention also provides a fuel atomizer that does not suffer from rapid erosion when atomizing highly abrasive slurries or highly viscous liquids.
The present invention also provides a combustor system employing a pulse combustion apparatus to atomize the fuel combusted in the combustion system.
The present invention also provides a gasification system employing a pulse combustion based atomizer.
Generally speaking, apparatus according to the present invention includes an atomization apparatus comprising pulse combustion means for generating a stream of atomization fluid and a means for providing a fuel to the pulse combustion means so that atomized liquids or slurries are produced by the stream of atomization fluid acting thereon. The method for atomization according to the present invention generally comprises the steps of producing a stream of atomization fluid by pulse combustion and providing a liquid or slurry to be atomized to the stream of atomization fluid so that an atomized liquid or slurry is created that may be provided for further application.
Although the present invention is directed to atomization of liquids and/or slurries, the explanation of the claimed invention is generally exemplified by reference to the atomization of fuels. More specifically, one particular embodiment of the present invention includes an apparatus for creating and/or utilizing an atomized fuel comprising a pulse combustor for producing a stream of atomization fluid wherein the pulse combustor includes a combustion chamber, a valve in communication therewith for admitting fuel or air to the combustion chamber, a first fuel injector for admitting fuel to the pulse combustor and a resonance tube in the communication with the combustion chamber. The apparatus further comprises a second fuel injector for admitting fuel to the pulse combustor so that the fuel admitted thereto may be atomized by the stream of atomization fluid. Furthermore, the resonance tube of the pulsed fuel atomizer is in communication with apparatus for utilizing the atomized fuel created therein such as combustion and gasification systems, and other similar types of devices wherein atomized fuel is preferred or acceptable.
,~,.', ~N~ 9311039 ~ ~ ,~ "~~ ~ ? ~ PC°T/L1S92/U9740 7 .
A method for atomizing a fuel according to the present invention more specifically comprises the steps of supplying a pulse combustion fuel to a pulse combustor having a combustion chamber, a valve means far admitting'f~tel or air to the combustion chamber, and at least one resonance tube. The method further includes pulse combusting the pulse combustion fuel to produce a combustion stream of atomization fluid e~~.ting from the combustion chamber and entering into 1,~ the resonance tube. A liquid or slurry to be atomized is supplied to the pulse combustor after the stream of atomization fluid has been produced so that the liquid or slurry to be atomized is atomized by the stream of atomization fluid. Further, the method includes 1~ providing the atomized liquid or slurry, preferably a fuel, for further applications such as combustion and gasification.
As described herein, one particular and preferred apparatus of he present invention includes a pulse combustion mans having a combustion chamber in eommunic~tion with an aerodynamic valve for admitting fuel or air on demand to the pulse combustion chamber.
The pulse combustion means includes one or more resonance. tubes in communication with the combustion 25 chamber. A means is provided for supplying fuel to the pulse combustion chamber so that a pulsating flow bf atomization fluid is crated. The apparatus further includes means downstream from the combustion ~ham,~er for supplying fuel to be atomized, and 30 preferably takes the foam of an injector. This second injector thus supplies the slurry or liquid fuel which is to be atomized to the atomization fluid so that atomization of the fuel occurs under the influence of he oscillating ~r pulsating flow field described 35 herein. The pulse combustion means, when fired, WO 93/1(1398 _ ~ ~ ~' ~~ 'j ~~' ~ PC,'TJUS92/~?~''~i0 produces a pulsating flow of combustion products which serves as an atomization fluid for the fuel supplied downstream. The fuel, which is preferably injected near the interface of the resonance tube and the . combustion chamber, is then supplied to a main combustor cavity or other device such as a gasifier to utilize the atomized fuel in the combustion or gasif ication process.
Another, particular embodiment of the present invention employs a supercharger for increasing the velocity of air admitted through the aerovalve descri?aed above. The supercharger may employ a forced draft fan; an air blower, an air compressar, or other device to pressurize the air provided to the x5 combustion chamber through the aerovalve. When such high pressure air is supplied, the pulse combustion means operates under a supercharged air inlet dondition.
Brief Description of the Drawings ~p The'construction designed to carry out the invention will be hereinafter descried, together with other features thereof. The invention will be more readily understood from reading of the following specification and by reference to the accompanying 25 drawings forming a part thereof, wherein an example of the invention is shown.and whereas:
Figure 1. is a schematic illustration of a prior art high pressure,, single-fluid atomizer.
Figure 2A is a schematic il.lustratian of a prior 3p art Y--jet internally mixed, dual-fluid atomizer.
Figure 2B is ~ eche~aatic illustration of a prior art eductor-T-jet internally mixed, dugl-fluid atomizer.
Figure 3 is a schematic illustration of a prier 35 art externally anixed, dual-fluid atomizer.
Figure 4 is a schematic illustration of one particular embodiment of a pulse combustor-atomizer apparatus of the present invention.
Figure 5 is another particular embodiment of a pulse combustor-atomizer of the present invention wherein an air supercharger has been added thereto.
Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of the invention in the various illustrations.
Description of the Preferred Embodiments As previously mentioned, the invention is directed to the atomization of liquids and slurries. The description herein employs fuel as an example of a particular liquid or slurry that may be atomized accordingly.
The preferred apparatus for atomizing fuels according to the present invention employs a pulse combustor to produce an atomization fluid which is then utilized to atomize a further liquid or slurry. Heretofore, the use of a pulse combustor for the atomization of fuels has not previously been known. In essence, the present invention is a dual-fluid atomizer apparatus. A pulse combustor means creates an oscillating combustion product stream (or atomization fluid) which engages and atomizes a second fluid or slurry (preferably fuel) which is then provided in an atomized state for further use as desired, such as downstream combustion or gasification.
Figure 4 depicts one particular pulse combustor fuel atomization apparatus according to the present invention.
Referring to Figure 4, a pulse combustor is shown generally by the numeral 10. Pulse combustor 10 generally comprises a combustion chamber 12, a valve means 14 in communication with combustion chamber 12, and one or more resonance tubes 16 in communication with combustion chamber 12. One particular pulse combustion means that may be employed in the present invention is generally and specifically described in U.S. Patent No. 5,059,404 to Mansour et al.
Specifically, pulse combustor 10 may employ an aerodynamic valve (fluidic diode), a mechanical valve or the like as valve means 14, a combustion chamber 12, and one or more tailpipes or resonance tubes 16. Additionally, pulse combustor 10 according to the present invention may include an air plenum and thrust augmenter or supercharger as described below with respect to Figure 5.
The pulse combustor fuel atomizer of the present invention further includes a first fuel introduction means 18 for admitting of fuel for operation of the pulse combustor, through the combustor fuel could be admitted along with air through valve means 14. An additional fuel introduction means 20 is provided for introducing fuel which is to be atomized by the combustor apparatus 10. First fuel introduction means 18, preferably a fuel injector, provides fuel to combustion chamber 12 for firing the pulse combustor 10. Any conventional means may be employed to supply a fluid to the apparatus through first fuel and additional fuel introduction means 18 and 20. For example, conventional injection apparatuses which utilize pressurized fluid f,or spraying liquid fuel may be employed. Pressurized injectors, however, are not necessarily required because combustion chamber 12, acting as a vacuum source during operation as described herein, would draw fuel from first and l''"'~y VlrO 93110398 ~ ~ ~ :.~ ~ ~ ~ PCTlCJS92O49740 additional fuel introduction means 18 and 20 without pressurization.
As also shown in Figure 4, pulse combustor first fuel introduction means 18 preferably introduces fuel for (firing the pulse combustion means to at an area near the junction of air valve means 1~ and combustion chamber 12. Such positioning of first fuel introduction means 18, however, is not required in the present invention. Tn fact, and as mentioned abave, 1i~ first fuel introduction means 18 may be eliminated altogether. Instead, as described herein, valve means 14 may admit a fuel/air mixture to combustion chamber 12 so that an additional fuel path exemp~.ified by first fuel introduction means 18 is not xequired.
As seen in Figure ~, combustion.chamber 12 is in communication with resonance tube 16 for receipt of an oscillating stream of combustion products. Additional fuel introduction means 20, which adds fuel to be atomized; is preferably located near the juncture of the resonance tubes) 16 and combustion chamber 12.
However, as wall be appreciated, additional, fuel a:ntroduction means 2~ may be Located anywhere along resonance tubes) 16 provided the stream of at~mization fluid created by pulse combustion in combustion ~hamber'12 can act thereon under influence of the oscillating flow field to atomize the fuel.
~r~mbustibn chamber 12 and resonance tube (s) 16 form a tuned He~mhaltz resonator as described herein.
Valve means 14 acts as a diode such that self-air asp~.ration is affected in response to an oscillating 'pr~ss~are in combustion chamber 12 induced as a result of heat'and mass release from combustion therein. As described below, va~'~.ations of the present invention include the use of a mechanical valve instead of an 3~ aerodynamic valve for valve means 14.
WO 93/~039~ ~'CT/L'S92/(~:r,°~a0 2~~~~ w~ 12 1 A pulse combustor, such as that employed in the present invention, typically operates in the following manner. F'uex enters combustion chamber 12 through first fuel introduction means 18 or, alternatively, through valve~means 14. Air enters combustion chamber 12 through valve means 14. An emission or spark source (not sfiown) detonates the explosive mixture during start°up. A sudden increase in volume, triggered by,the rapid increase in temperature and evolution of combustion products, pressurizes combustion chamber 12. As the hot gas expands, valve means 14 in the gorm of a fluidic diode, permits preferential flow in the direction of resonance tubes) or tailpipes) 16e The gaseous combustion .
product stream; which is the atomizat~.on fluid in the present invention exiting combustion chamber 12, possesses significant momentum. A vacuum is created in'combustion chamber 12 due to the inertia of the atomization fluid within reson~nee tubes) 16 and permits only a small fraction of atomization fluid to return to combustion chamber 12, with the balance of the atomization fluid, or gas, exiting through res~nance tubes) 16. Because the chamber pressure is then below atmospheric pressure, air and fuel mixtures 2~ are drawn i-nto'chamber I2 where auto-ignition takes place. Again, valve means 14 constrains reverse flow, and the cycle begins anew. once the first cycle is initiated, engine operation is thereafter self-sustaining or self-aspirating.
The val~tte 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 flaw by a'mechani~cal seating arrangement.
7 FC.'T/LiS92/a9740 ~.~.,. VVt? 93/10398 Although such mechanical valves may be used in conjunction with the present system, an aerodynamic valve without moving parts is preferred. With an aerodynamic valve, a boundary layer builds in the valve during the exhaust stroke and turbulent eddies choke off much of the reverse flow. Moreover, the exhaust gases have a much higher temperature than the inlet gases. Accordingly, the viscosity of the gas is much higher and the reverse resistance of the inlet 1~ diameter, in turn, is much higher than that for forward f low through the same opening. These phenomena, along with the high inertia of the atomization fluid exhausting in resonance tubes) 16, combine to yield preferential and mean flow from inlet 25 to exhaust. Thus, pulse combustion creates a self-aspirating enc3ine, drawing its own air and fuel'into c~mbustion chamber 14, auto-igniting, and creating co~mbustie~n products to form the atomization fluid utl.lized in the present invention.
A preferred pulse combustor used herein, and as noted above; is based on a Helmholtz configuration w,~th an aerodynamic valve: The pressure fluctuations, which are combustion-induced in the Helmhaltz xes~natdr-shaped combustor, coupled with the fluidic 25 r~iodicity of the aerodynamic valve, cause a bias f low ~f air and fluid from °~he combustor's inlet to the exit of resdnanc~ tubes) ~.6. This results in the combustion air being self-aspirated by the combustor and for an average,pres~ure bcaost to develop in the 3p combustion chamber t~ expel the products of combustion ~.': ~ ~t a h gh average flow velocity (typically over'1,t7~0 Et:/s~c.) into and through resonance tubes) 16.
The production of an intense acoustic wave is an inherent' characteristic of pulse combustion. Sound 35 intensity adjacent to the wall of combustion chamber ~Y~ 9311098 ~ ~ ~ ~ ~ ~ ~ ~ P~'lL~S92/0.~''.;~.,~
12 is normally in the range of 110-190 dB. The range may be altered depending on the desired acoustic field frequency to accommodate the specific application undertaken by the pulse combustor.
, A rapid pressure oscillation through combustion ., chamber l2 generates an intense oscillating flow field. The fluctuating flow field causes the atomization fluid, or products of combustion, to be swept away from the fuel which is firing the pulse edmbustor, thus'providing access to oxygen with little or no diffusion limitation. Secondly, pulse combu.st~rs experience very high mass and heat transfer gates within the combustion zone. While these combustors tend to have very high heat release rates (typically 20 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, resulting in a significant reduction in nitrogen oxides (NOx)-formation as described in U. S. latent No. 5,059,404. The high heat release rates also results ix~ a smaller combustor size required for a given firing rate and a r~ductioz~ in the required ~5 resonance time.
Pulse c~~nbustor ystem~ of the present invention xegulate their own s~oichiometry within their range of firing withoutt need of extensive controls to regulate the fuel feed to combustion .air mass flow rate ratio.
As the fuel feed rate is increased, the strength of ,'- ' the pressure pulsaticans,in dombu~tion chamber 22 ~.ncreases which, in turn; increases the amount of air aspirated by'the aerodynamic'valve. Thus, the combustor automatically maintains a substantially ''~V~ 93!10398 ~ ~ a :~ ~ s ~ ~ P(:T/LfS92/097~i0 constant stoichiometry over its designed firing range.
3'he induced stoichiometry can be changed by modifying the aerodynamic valve fluitlic diodicity.
Tn certain embodiments of the present invention, 5 two (2) pulse'combustors may be. arranged in a tandem configuration wherein two pulse combustors as shown in Figure 4 are operated in close proximity. The tandem operation employs a 180 phase lag between each combustor unit and results in super-positioning of 10 acoustic waves and cancellation of the fugitive sound emissions.
Such tandem combustors may be configured so that a fuel "T' acts as a coupling allowing automatic fuel biasing between each of the in-tandem pulse combustion 15 units. Under these conditions, one combustion chamber achieves a low pressure phase just as the other' chamber simultaneously achieves a high pressure phase.
l~ue to the pressure gradient existing in the fuel coupling, combustion products are accelerated from the high pressure chambor to the low pressure chamber.
The moment~.m of the accelerated gases biases a flaw of fuel from the main full source into the fuel line T"
and eventually into the low pressure combustion chamber. ~ half-cyc~.e hater, a sima.lar phenomenon occurs ~.n the opposing direction. By these mans, fuel can be properly phased w~.thout the use of mechanical flapper valves or an independent phasing chamber. The natural instability of the tandem units employing a common fuel-coupling line is sufficient to automatically pull he'two combustion units 180 out of phase because the units inherently hunt for the most stable and robust operating state. That state results in efficient fuel phasing, i.a., a 180 phase lag ~~ 93/1039 ~ ~ ~ ) ~ ~ ~ lP~f/L~~9~/'~,.,'~40 .. 16 Various other modifications can be made to pulse combustor 10 of the present invention. For example, if desired, water-cooled jackets may be utilized for withdrawing heat from resonance tubes) 16 for directing to a boiler or other heated fluid device.
Furthermore, resonance tubes) 16 may employ a number of different designs. For example, the tube may flare continucausly outwardly allowing the entire resonance tube to act as a diffuser to reduce gas exit velocity from combustion chamber 1~ prior to entry into a main combustor cavity or gasification system. Moreover, resonance tubes) 16 may be essentially straight, but have at its outer end a diffuser section that consists of an outwardly faring tailpipe section, or alternatively, may integrate a diffuser section at the end nearest combu Lion chamber 1~ with an essentially straight tube extending therefrom.
When operated according to the present invention, pulse combustor mews 10 produces a pulsating flow of atomization fluid and an acoustic wave having a frequency ih a range of-from about 20 to about 1600 Hz: As fuel is combusted, a pulsating f low of atomization fluid exits combustion chamber 12 and passes into resonance tube() 26. The stream of '25 atomization fluid leaving combustion chamber 12 is at a sufficient'' velocity s,o as to atomize the fuel being injected or,prova.ded by additional fuel introduction means 20e After the atomisation fluid meets the fuel to be atomized, fuel' is atomized and travels along resonance tubes) 16 gaining further speed until the atomized fuel is provided to 'a main combustor cavity ~r ~ther application:
~ suitable pulse jet fuel is pr~~rided to combustion chaznb~r 12 through first introduction means 18 and/,or valve means 14. Typically, a highly r,,....,~ ,~O 93/1039 - r~ ~:~ r~ ;~ a P~/U592109'7d0 flammable fuel such as natural gas, propane, hydrogen-rich synthesis gas, and other such gases are preferred to f ire pulse combustion means 10. It is possible, however, to use liquid fuels, preferably light distillates such as gasoline and kerosene.
Furthermore, solid fuel such as lignite coals, sawdust, and other highly reactive solids may be used for firing the pulse combustion means 10. The higher the flammabi~.ity of the fuel employed, the higher the attainable dynamic pressure amplitude induced by the spontaneous resonance of the Helmholtz resonator.
Furthermore, highly flammable fuels provide higher heat release rates per unit volume of the Helmholtz resonator.
As prev~.ously described, the oscillating dynamic pressures in combustion chamber 12, in the presence of an aerovalve or properly designed mechanical valve, give rise to a pressure boost in combustion chamber 12 that propels the atomization fluid through resonance tubes) 16 at high velocity. The high kinetic energy in the flow of atomization fluid through the resonance tube is employed to atomize fuel provided by fuel injector means 20. From resonance tubes) 16, the atomized fuel is introduced into a main combustor csvity 50 where addiaional combustion air is added and the atom~:zed fuel is combusted.
gy vary,i.ng the amount of excess ait provided to pulse combustion means 10 snd the amount of fuel being atomised for consumption by the main combustor, the 3~ temperature'of'the atomized spray can be modified.
Furthermore; in the case of a slurry fuel, adjustments to ~.he pulse c~mbu~tion ~toichiometry and the ratio b~twsen the firing rate o~ the pulse combustion to the main combustor firing rate results in dry coal or 35 other salid fuel emanating from the pulse jet atomizer W~ 93/10398 ;~~ f ~ PCT/L~S92/~"'0 .2~~~~;~~ 1$
into the main combustor cavity. Furthermore, f icing the pulse combustion means at near stoichiometric air conditions (e.g., 3% excess air in the flue) and at a sufficiently high firing rate, allows the atomized fuel emanating from the atomizer to produce pre-ignited volatiles and ignited fines together with the volatilized larger solid fuel particles from the fuel slurry. This, in turn, anchors the flame within the main combustor cavity and allows higher turndown of ~,p the main comlbustor without flame-out. Furthermore, when operating under such atomization/drying, devolatilizing and pre-ignition parameters, preheating or the main combustor's combustion air to stabilize the combustion of the atomized slurry can be 1~ eliminated.
The pulse combustor atomizer apparatus of the present invention is operated in the following manner.
A'fuel for combusting in the pulse combustor is provided to pulse combustion chamber 12 through first 2p fuel introdu~t~:on means 18 or, alternatively, is prcwided through valve means l4 as an air/fuel mixt~zre. Air-is provided through valve means 14 and 'an ignition'source (not shown) ignites the fuel for combustion in combustion chamber 12e Combustion of 2g the fuel cr~eate~ a pulsating flow of combustion products used as the atomization fluid of the present inventi~n. The pulsating combustion is self-aspirating-as described herein. The flow of atomization fluid laving combus~a~on chamber 12 travels to and through one or mare resonance tubes 16.
At a~ locati'on at or near the juncture of resanance tube(s). 16 and combustion chamber 12, an additional fuel introduction means 20 provides the fuel to be ato~ni.zed by the pulse combustor 10. Fuel to be 35 atamized and which is supplied through additional fuel PC:T/L X92/09740 t,:".. ,S 1VVVCD 93/ l X1398 ~ ~ :d N ~ ~ ~ ~ ' introduction means 2~ is provided to the f low of atomization fluid so that the oscillating, or pulsating, f low field previously described can act thereon so as to cause atomization of the fuel. The fuel which is'then atomized is provided downstream for further processing such as combustion, gasification, etC.
~lith such a pulse combustion atomization apparatus, drying, devolatilization, and pre-ignition ~.0 of the fuel injected into the pulse combustion means are achieved at a very high rate in the hot oscillating flow field found in resonance tubes) 16.
This allows deep staging of the main combustor to reduce NoX production as previously described.
Furthermore, high turndown without flame-out and moderate combustion temperature which further seduces thermal NOX formation and a high combustion efficiency with little to no air preheating is 'thereby achieved.
This, of corarse, eliminates the need for costly ~combus~tion air preheaters as required by the prior art and saves on capital and maintenance costs while providing superior main combustor performance with slurry and liquid fuels.
Therefore, taken the.de~cribed pulse combustion fuel atomizer is em~~.oyed to atomize slurry and liquid ~uele, several desirable benefits are achieved: F'or example, the need'for compressed air far atomization of the fuels is eliminated. This, of course, eliminates both the ~aara~itic power required for generation o~ the compressed air and he capital and mainfi~nance costs required to grovide the comp~essdb equipment. Furthermore, the erosion problems incurred with the previously-described internally mixed, dual-'fluid atomization devices are avoided. In addition, VV~ 9311039 PCT/L'5921'"'~..'..40 20 , the high parasitic power requirements of the externally mixed, dual-fluid atomizers are reduced.
The pulse combustion atomizer of the present invention essentially operates as an externally mixed, dual-fluid atomizer having lower erosion rates. The atomization fluid is generated in a self-aspirating pulse combustion means by burning fuel. such generation occurs in a system which requires no essential moving parts and no air compressors.
p Finally; superior fuel preparation for efficient combustion and for gasification with flame stability, high turndown; and decombustion staging potential is recognized over the current internally mixed and externally mixed, dual-fluid atomizers. In conventional dual-fluid atomizers, the droplet size of an atomized slurry is generally larger than the size of some of the coal particles present in the initial slurry, resulting in a water-laden fuel. Water-laden cowls requige a number of additional combustion p processes to'v~porize the'wate~ from the droplets as well as for devolatilization and ignition of the fuel.
yn addition, when certain cracking coals (such as bituminous coals: typically used to manufacture slurry fuels) are used, agglomerates ~f fine particles are ~g formed from mufti-particle r~roplets resulting fn a reduced surface-to-mass ratio of the burning fuel.
Furthermore,'the presence of water in the slurry generally requires signigicant-preheated combustion air in crder'to'avoa:d flame~cut in the main combustor.
30 Even with coanbustion air preheating, the combustor turndown and extent of ataging, particularly deep staging, are' limited with slurry fuels because of ,the preeence of water in the fuels. Such is not the case with slurryfu~ls atomized by the present invention i~~1 CVO 93/10398 - ~ ~ 7 ~ ~ 7 ~ PCT/l.'S92/09740 iJ IJ
which undergo significant drying, devolatilization, and pre~ignition.
Additionally, the pulse combustion atomizer results in increased mixing of fuel with air due to the pulsation~of the combustion products stream.
Moreover, the presence Of solids in the atomization fluid stream give rise to an increase in the atomization ability of the stream.
1Cn another embodiment of the present invention, a 1p pulse combustion atomizer may be operated under a pressurized or supercharged inlet air condition. As depicted in Figure 5, an air plenum 24 may be connected through conduits to a supercharger 26.
Supercharger 26 may lie a forced draft fan employed for supplying primary air to air plenum 24. Air plenum 24 -operates as a capacitor and seeks to provide primary air to pulse combustion means 10 at approximately constant static pressure. The pressure boost dweloped due to-pulse combustion within the present ,~~,bodim~nt allows a reduction in the size, power requirements, and cost of forced draft supercharger 26. Supercharger 26 may; instead, consist of an air blower, an air compressor, or other device for supercharging the air fed to valve means 14.
x5 As shown ~.n Figures 4 and 5, fuel that has been atoanized by pulse-combustion means 1n may be supplied o a main combustor cavity 50: In addition, atomized fuel produced by h;e present apgaratus may be supplied to a gasification device as generally known in the art and described in U. 5: Patent NO. 5,059,404. The main comb'ustor cavity may consist of a further pulse' combustion mans or may, ' instead, Doe a typical ccynventional combustion unit.
Although preferred embodiments of the invention 35 have been described usi~ig s~aecif is terms, devices, ~O 93/10398 ~ ~ ~ ~ r? ~ PCT/LjS92/0"" ~':0 concentrations, and methods, such description is for .illustrative purposes only. The words used are words of description rather there of limitation. It is to be understoad that changes and variations may be made without departing from the spirit or the scope of the following claims.
|International Classification||F23C6/04, F23D11/10, B05B1/08, F23D1/00, F23C15/00|
|Cooperative Classification||F23C6/047, F23D11/10, F23D1/005, F23C15/00, F23C2201/301|
|European Classification||F23C6/04B1, F23D11/10, F23D1/00B, F23C15/00|