Field of the Invention The invention is in the field of industrial burners, combustors and incinerators and. more particularly. relates to new industrial burners and/or combustors for combustion of either gaseous or particulate fuels including smoke.

Particulate fuels may be wet or dry sawdust and many types of varying moisture content biomass fuels including. agricultural products. wood waste. bagasse. poultry waste, and other cellulosic materials. and especially in the wood products manufacturing or processing operations. Gaseous fuels may mean gases traditionally used as fuels or they may mean so-called off-gases, including smoke or other combustible gases produced by processes relating to such wood products and other gases. such as from kilns or primary burners, including industrial off-gases. Burners of the invention provide high efficiency. Specifically they may operate with high turndown ratios and high heat release ratios. As used herein, the term off-gases connotes gases produced not primarily as fuels but instead those produced by other processes and apparatus, including gases produced by burners whether of the present invention or other types.

Related Art In the general field of burners, combustions and incinerators for industrial purposes, there are myriad different configurations. wherein there has for many years been an increasing focus on efficiency and output. Thus. there have been proposals for swirling or cyclonic combustion and combustion chambers of unusual geometries. as well as many proposals for controlling the entry of air and fuel into the combustion chamber for contributing to swirling or other patterns of combustion motion. There have been various burners proposed for burning, as feed stocks, organics or biomass materials. including so-called green (high moisture content) sawdust, solid cellulosic

or wood-containing waste, waste wood, and fragments of wood. and all of which may herein be referred to as wood products. And. burners of various configurations and capabilities have been proposed for combustion of off-gases.

In burners useful for burning such materials, there has been insufficient emphasis on achieving efficiency and flexibility which can result from achieving a high turndown ratio (which may for convenience be abbreviated"TDR"), which is the maximum firing rate of the burner divided by the minimum firing rate of the burner.

Prior constructions have not achieved sufficiently high TDRs.

The provision of a high TDR for a burner capable of carrying out combustion of wood products is highly desirable, as such a burner would be capable of being operated over a great dynamic range. If. for example, in a manufacturing or materials handling operation which creates such wood products. which are to be combusted (as for heating or energy extraction for other processes or purposes). the use of a burner having a limited TDR can require that burner operation be terminated if wood product supply rates are insufficient to achieve the minimum firing rate of the burner. Or, if combustion of wood products at low feed rates is to be carried out, an auxiliary fuel such as natural gas. liquefied petroleum (LP) gas, propane, or fuel oil. may have to be fed into the burner for maintaining combustion. But, on the other hand. if the burner is designed for burning wood products at low feed rates. its output may be insufficient to handle high feed rates when wood products to be combusted are being produced at high volumes. Further. if TDR can be increased. much less auxiliary fuel will be required to initiate burner operation.

As an example. in a wood products manufacturing or processing operations, very substantial quantities of green sawdust are created during sawing. planing, shaping. etc.. but the rate of production of sawdust will be dependent upon the various wood-handling processes. which vary in rate. time of operation. and volume. so that sawdust may be produced at a highly variable rate.

If the sawdust is to be combusted by a burner for the purpose of extracting heat for other uses (such as heating, boiler operation, drying. etc.). the use of a burner having a high TDR enables its operation on continuous basis or at least for longer periods of operation, as desired.

In the wood products industry, as including also the production of charcoal, there is a need also for dealing with smoke and other gases produced during operations. For example, in cooperage operations where barrels are produced for

aging of beverages. such as wines or brandies. etc., some types of barrels require that they be charred, as for the aging of various kinds of whiskeys. Charring operations produce smoke which may need to be combusted. So also, in charcoal kilns, the off- gases are sources of environmental pollution. and may also need to be combusted, i. e., bv oxvgenation combustion.

It would be desirable to combine a burner, capable of burning wood products for the above-noted purposes, with features for combustion of off-gases in the wood products industry.

Present burners in the wood products industries have not met the needs for these kinds of combustion. and have not achieved satisfactorv TDR and efficiencies for acceptable usage in the wood products industries.

As used for combustion of gases. constructions and methods of the presently claimed invention are of special utility and suitability for burning off-gases such as smoke in situations where other processes and apparatus have produced gases which are amenable to further combustion and which may be rendered less noxious or may be converted to a safer state or destroyed by being burned at relatively high temperatures.

For example, when wood products are charred as in making barrels. smoke may be released which advantageously can be burned.

As a further example, in making charcoal involving partial combustion of wood and other cellulosic or organic substances. including vegetable-based materials smoke may be released from charcoal kilns.

The present invention specifically includes improved gas combustors of high utility in wood products industries and charcoal production.

The general term burner is used herein to encompass both and combustors.

Summary of the Invention Accordingly, the present invention provides various burner embodiments for burning particulate fuel such as so-called green (high moisture content) sawdust. various feed stocks, organics or biomass materials, including solid cellulosic or wood- containing waste, waste wood. and fragments of wood. and all of which may herein be referred to as wood products or particulate organic fuels or materials.

The invention is also concerned with such burners which are capable of combustion of gases, such as off-gases produced in the wood products industry. or other gases which are to be oxygenated or burned for conversion to a condition environmentally non-polluting.

Burners of the present invention achieve high efficiency and flexibility. particularly achieving a very high TDR.

The inventive burners specifically achieve a high TDR while carrying out combustion of wood products. Burners of the invention are capable of being operated over a great dynamic range.

The new burners are especially useful in wood products manufacturing or processing operations. such as stave and barrel-forming (cooperage) operations which create very substantial quantities of green sawdust.

The new burners. because of their high TDR. efficiency and dynamic range, can be used in operation on continuous basis or for longer periods of operation. and at greatly variable output different as may be desired.

The new burners disclosed are capable of combustion of a high-moisture. low- Btu value fuels not only providing high TDR but also achieving a high heat release ratio, meaning heat output per volume per unit of time. This allows a smaller size burner of the present invention than otherwise would be required in a prior art burner. and so the invention results in a burner of lower cost than heretofore.

Another feature of the presently inventive burners is the capability for designing the burners to a desired scale, as according to the intended mode of usage and industry segment in which the burners will serve. Thus, the present burners are easily scalable.

A further advantage of the inventive burners is their use of electronic controls using programmable logic controllers, for achieving precise, efficient. safe and reliable control and operation in all modes of usage.

Yet another feature of the inventive burners is a gas combustor for combustion of smoke and various combustible gases, including off-gases in the wood products industry. such as for example gases produced during cooperage operations and gases produced during the operation of charcoal kilns, as well as other industrial off-gases.

The presently inventive burners achieve satisfactory TDR and efficiencies for acceptable usage in the wood products industries.

In addition, burners of the present invention are economical in construction and operation and are easily installed and operated.

The present invention specifically includes improved burner constructions and methods to provide gas combustors of high utility in wood products industries and charcoal production. as for burning smoke and other gases when wood products are charred as in making barrels. and in charcoal production.

Briefly. the present invention relates to various burner configurations. Each burner of the disclosure exhibits a high TDR for combustion of a principal fuel. The burner includes, or comprises. consists, of or consists essentially of a housing defining an upright combustion chamber lined with refractory material and generally circular in horizontal section. a main combustion region within an upper extent the combustion chamber, an initial combustion zone at a lower end of the combustion chamber of reduced-size cross-section compared to the combustion chamber, a transition region within the combustion chamber increasing in cross-section from the initial combustion zone to the main combustion region. a ceiling of the combustion chamber. a principal fuel feed to supply particulate fuel with combustion air to the initial combustion region, and an auxiliary fuel feed to supply ignition fuel to the initial combustion region for igniting the principal fuel. Multiple sets of tuyeres are provided for controllably introducing combustion air tangentially regions of the combustion chamber for contributing to cyclonic combustion flow in such a manner as to increase diameter of combustion upwardly within the combustion chamber. A counterflow arrangement disrupts cyclonic flow near the ceiling. The ceiling defines an exit for providing escape from the combustion chamber of exhaust gases resulting from combustion in the combustion chamber. The arrangement is such that the principal fuel is ignited in the initial combustion region. and burns with cyclonic flow extending upwardly through the transition region with increasingly greater combustion diameter into the combustion chamber.

Various ignition and control features are also disclosed.

The high TDR burner maybe combined synergistically with a smoke or combustible gas combustor mounted to or connected to the burner for receiving hot combustion exhaust gases of 1.600 degrees F. or greater. which exit into a preheat tube located within a smoke-combustor heating chamber. Smoke or other combustible gases such as off-gases from another process enter the heating chamber through gas tuyeres tangential to walls of the heating chamber. The smoke or gaseous combustibles are heated by the preheat tube. The combustor includes a venturi which creates a negative pressure in the heating chamber for drawing the combustible gases from the heating chamber and from the combustible gas tuyeres. Controlled high- velocity air is forced through the venturi tuyeres, causing the venturi action.

Controlling the amount of high-velocity air forced into the venturi tuyeres and the cyclonic tuyeres regulates negative pressure created by the venturi. The high-velocity air also serves as combustion air for ignition of the combustible smoke or gases.

More combustion air is forced into the top of the venturi chamber through cyclonic tuyeres. enhancing mixing of the air and combustible gases and causing the gases to burn in a cyclonic pattern in the combustion chamber of the combustor. The combustor can be operated to maintain proper negative pressure for optimum draft control while maintaining the correct amount of air and temperature for combustion of the combustible gases in the combustion chamber.

The high TDR burner may alternatively be combined with a smoke combustor including a housing configured for receiving the heated exhaust gases from the burner. the housing defining a combustible gas heating chamber including coaxial inner and outer combustion chambers, one or more inlet tuyeres connected to the inner combustion chamber for introducing combustible smoke or other gases to be burned into the inner combustion chamber at one end thereof with cyclonic flow, means for mixing combustion air with said combustible smoke or other gases to form a combustion gas stream moving through the inner combustion chamber with cyclonic movement. a preheat tube within the combustible gas heating chamber into which the heated exhaust gases are ducted for preheating. the preheat tube being of substantial thermal mass and communicating with the inner combustion chamber exit through a plurality of apertures for controlled flow of said heated exhaust gases into the gas stream for preheating the combustible gas stream by mixing the exhaust gases with the stream of air and combustible gases for combustion thereof to provide combustion gases. means at an opposite end of the inner combustion chamber for redirecting

counterflow movement of said combustion gases from the inner combustion chamber to the outer combustion chamber for counterflow of combustion gases therein relative to the inner combustion chamber. whereby combustion gases thence travel though the outer combustion chamber along a separating wall which separates the inner and outer combustion chambers. the outer combustion chamber including means for causing continued cyclonic movement of the combustion flow in the outer combustion chamber, and an outlet at an end of the outer combustion chamber remote from the redirection means for delivery of completely burned combustion gases.

Other objects and features will be in part apparent and in part pointed out below.

Brief Description of the Drawings Fig. I is a vertical cross-section of a burner, including an ignition-can. in accordance with and embodying the present invention.

Figs. I A-A through 1 G-G are horizontal cross sections taken along correspondingly numbered section lines of Fig. 1.

Fig. 2 is a vertical cross-section of another embodiment of a burner of the invention, including an ignition tower.

Figs. 2 A-A through 2 F-F are horizontal cross sections taken along correspondingly numbered section lines of Fig. 2.

Fig. 3 is a vertical cross-section of another embodiment of a burner of the invention. including a gas or smoke-combustor.

Figs. 3 A-A through 3 G-G are horizontal cross sections taken along correspondingly numbered section lines of Fig. 3.

Fig. 4 is a vertical cross-section of another embodiment of a burner of the invention, including an ash removing system.

Fig. 5 is a circuit schematic layout diagram of a programmable logic controller. and its connections to various components of a burner of the invention.

Fig. 6 is a circuit schematic layout diagram of a programmable logic controller and its connections to various components of a combined burner and smoke- combustor of the invention.

Fig. 7 is a vertical cross-section of another embodiment of a burner of the invention. including a gas or smoke-combustor of a further improved type and which combustor will herein be called the Smoke-eater to distinguish it from the version of Fig. 3.

Corresponding reference characters indicate corresponding parts consistently throughout the several views of drawings.

Detailed Description of Practical Embodiments A burner 100 as shown in Fig. 1 is designed to burn many types of varying moisture content biomass fuels. and they may also be used to burn fuel gases. such as natural gas or liquefied petroleum gas or fuel oil. For descriptive purposes the words sawdust or wood will be used to connote such materials delivered to burner apparatus of the invention as fuel.

Burner 100 has an external housing 100h of generally cylindrical form defining a having a lower extension 3 of smaller diameter which extension 2 may for convenience be referred to as an ignition can 2. Can 2. having an inside diameter of constant cross-section. is lined interiorly with refractory-material 3. Can 2 provides for ignition of introduced particulate fuel. e. g., sawdust. and transitions from its reduced diameter initial combustion region 2r into a funnel-or cone-shaped transition region 5 and thence upwardly into a main combustion chamber 9. similarly refractory line. such that the horizontal cross-section increases from the initial combustion region 2r of can 2 upwardly within the burner to a constant diameter cross-section of combustion chamber 9 which is each generally circular in horizontal section. Upper portion of chamber 9 joins a substantially flat combustion chamber ceiling 9a. lined similarly with refractory material. through which an choked exit 11 (or, simply. choke 11) opens centrally into a suitable exhaust stack 11 s.

Stack 11 s may communicate, for example with a heat exchanger 11 e having a shroud 11 e'through which air may be forced by a fan 11 If. so as extract heat for other purposes (as for building heating, lumber drying, etc.) for extracting heat from the hot exhaust gases (e. g., at temperatures approaching or exceeding 2000 degrees F. which emerge from the combustion chamber. Thus. stack 11 s may have an extension 11 s' extending many feet in length through heat exchanger 11 e.

A suitable so-called ID (interior diameter) fan 11 i may be located at a suitable location for extracting the hot gases. and serving to induce a partial pressure within combustion chamber 9. The location and configuration of fan 11 i will be understood to be symbolic in Fig. 1 rather than representative of actual size and placement. Fan 1 li is controllable in speed under a PLC control system described below. Fan I I i associated with choke or outlet 11 for drawing gases from the outlet to maintain a

partial pressure within the combustion chamber so that combustion air is drawn through the tuyeres into the combustion chamber.

It may be seen then that can 2 defines a lower region or extension of combustion chamber 9 via transition region 5, within which the refractory lining may preferably take the form of relatively stepped regions 5a, 5b, including a short constant-diameter intermediate region 5c, for step-wise sloping transition from the interior cylindrical form walls 3 of can 2 upward into combustion chamber regions 9a and 9b for reasons which will be understood from the following description.

Sawdust is tangentially blown pneumatically into can 2 with combustion air through a tube 1 to inner refractory 3 lined wall of ignition can 2. A small material handling fan 50 is close-coupled to a sawdust entry nozzle 1 in ignition can 2. This allows material handling fan 50 to sling the sawdust into ignition can 2. Bv this burner configuration and method. less air is needed to transport the sawdust. contributing to high TDR of the burner.

In a practical configuration of burner 100 for sawdust burning, pneumatic sawdust transfer may normally be carried out with a minimum air velocity preferably about 4200 ft. per min., thus at such a velocity which necessarily keeps the sawdust in suspension and therefore transportable even if very small amounts are moved.

However. this velocity results in a volume of air much greater than what is needed for complete combustion at lower firing rates. This excess air cools burner 100 causing flames to extinguish in a burner without the features here described. This is one of the main reasons a conventional pneumatically fired burner cannot achieve a high TDR.

A gas or oil fired burner 4 introduces an auxiliary fuel to supply primary startup temperatures for sawdust ignition. Therefore. the auxiliary fuel, whether it be gas or fuel oil, is provided by burner 4 for ignition of the particulate fuel. The contribution of auxiliary fuel by burner 4 also stabilizes combustion temperatures in the ignition can 2 during normal firing operations. The sawdust as thus ignited and combustion takes place in an annulus or torus concentric about the vertical central axis of the burner and combustion chamber, occurring within the initial combustion region. As combustion occurs cyclonically, as with counterclockwise rotation about such axis. it produces a combustion cyclone, specifically a swirling tornado of flame, which is caused to pass up through combustion chamber 9. The cyclonic action causes the larger particles to wipe outer walls of can 3. stepped cone shaped funnel or

transition section 5, and combustion chamber 9, which results in a longer retention time for these particles to achieve combustion. Primary combustion starts to occur in ignition can 2. The fuel particles rise in temperature, moisture is driven off, and small particles are pyrolized completely. Larger particles rise up in funnel section 5 and combustion chamber 9 and are pyrolized.

More combustion air is added in funnel section 5 through cold tuyeres 6 and 7.

The cold tuyeres enter air tangentially to funnel section 5 walls. This air entering tangentially aids the cyclonic action, and helps keep the walls of funnel section 5 from becoming too hot and keeps sawdust from building up on funnel section 5 walls.

Cold tuyeres 6 and 7, arranged in two tiers or zones, use controlled high-velocity air.

(A cross-section view of the first zone is shown in Fig. 1. B-B. Cross-section views of the second zone are shown in Figs l. C-C. l. D-D, and 1. E-E.) This allows the right amount of combustion air to be supplied to each zone maintaining correct temperatures in funnel section 5 throughout the firing range. Combustion air is injected tangentially into combustion chamber 9 of burner 100 in four tuyeres 8. The combustion airflow through each of the tuyeres is individually controlled by a programmable logic controller (PLC) 37. PLC 37 controls the combustion airflow by valves and the rotations per minute (RPM) of fans in tuyeres 6,7 and 8.

Valves installed in each line providing a means of completely sealing off each tuyere. The combustion air completes combustion of the wood and further enhances the cyclonic action causing unburned particles of wood to be thrown against the outer wall until they are burned. This also keeps the outer walls from becoming too hot.

A shear counterflow tuyere 10 is designed to inject controlled high-velocity air tangentially in the top area of combustion chamber 9 in an opposite direction to the flow created by tuyeres 6,7 and 8. Shear tuyere 10 air creates a shear zone between the two masses of air, thereby causing a better mixing of air and its components. This mixing action causes improved combustion at higher firing rates. The shear action also extends the flame radially outward closer to the walls. Consequently, the shear tuyere air enables burner 100 to be fired at a higher firing rate. thus further improving the burner's TDR. Choke 11 prevents unburned particles of wood and charcoal, which are cyclonically driven to the outside walls, from escaping combustion chamber 9.

Ignition-can 2 is a separate lower extension of the combustion chamber, being bolted onto burner 100 and can be removed for general maintenance. An ignition

tower 13 is designed such that it may be bolted onto burner 100 at bolt points of ignition can 2. This modular arrangement allows for installation of ignition tower 13 without necessitating any modifications to the burner. The purpose of the ignition tower 13 is to create a higher TDR as explained in the following paragraphs.

In Fig. 2, a second embodiment comprises a gas or oil fired burner 12 mounted to the bottom of burner 100. Gas or oil fired burner 12 again introduces auxiliary fuel for ignition purposes. Burner 12 fires vertically up into a hollow interior of ignition tower 13 which is in the form of a hollow cylinder having a bullet-shaped upper head or end 16. Burner 12 introduces combustion heat into the combustion chamber in this manner, and for this purpose tower 13 includes through its side wall openings (tuyeres) 14 for ignition fuel and ignition air entry into transition section 5.

Alternative arrangements can be utilized in which a gas or oil fired burner fires tangentially into an ignition can arrangement, similar to ignition can 2 in Fig. 1.

Hot exhaust gases then enter the interior of ignition tower 13 from ignition can 2.

Ignition tower 13 is constructed of a suitable heat and abrasion resistant refractory material such as those commercially available under the trademarks"Coral Plastic"or'Mizou Castable".

Hot ignition gases from an auxiliary gas or oil burner 12 exit the hot tuyeres 14 and radiate out tangentially from the outer wall of ignition tower 13 into an annulus 19 and into funnel-shaped transition section 5. These annular or toroidal ignition gases initiate cyclonic combustion. and the combustion gases travel the same direction as the burning wood gases in burner 100. A small portion of the gas exits through a top opening 15 in a bullet-shaped stabilizing cone 16, which helps form and smooth the flow of flame and gases exiting funnel section 5.

Hot gases exiting the hot tuyeres initially heat ignition tower 13. bullet-shaped stabilizing cone 16, and the surrounding refractory forming funnel section 5 and annulus 19. After these elements are heated to the point where combustion of the sawdust can begin, the hot exhaust gases exiting the hot tuyeres 14 stabilize the burning of the sawdust and at low fire rates are critical in maintaining combustion.

The hot exhaust gases stabilize the burning of the sawdust by driving out moisture and raising its temperature to ignition temperature. These exhaust gases also help keep ignition tower 13 hot, which radiates heat into the incoming stream of sawdust causing ignition.

Fuel enters into burner 100 by means of a drop chute 17. The fuel drops directly into an area very close to vertical center 18 of funnel section 5. On positive pressure burners, an air curtain is formed by air from a tube 21 which equalizes pressure in the fuel feed tube and prevents gases and sawdust from being blown out of the burner. The downward momentum of the fuel carries the heavier particles such as sawdust and wood into annulus 19. Combustion air 20 is injected tangentially through tuyeres 6 in the outer walls of annulus 19. This air in combination with the hot gases exiting from hot tuyeres 14 causes the sawdust particles to spin with a high velocity inside annulus 19. The radiant heat created from the burning particles heats the walls of the annulus 19 to very high temperatures. The momentum of hot gases exiting the annulus 19 prevent excess sawdust from entering the annulus 19. This causes more burning in the funnel section 5 during high fire rates. As fuel burns in the annulus 19, the temperature drops allowing more fuel to enter the annulus 19, thereby maintaining an equilibrium temperature when firing at higher firing rates.

The annulus 19 is a hot spot allowing only enough fuel into the annulus 19 for complete combustion and preventing a buildup of fuel. Proper airflow is utilized to keep the annulus 19 hot and free of fuel buildup.

The hot gases exiting hot tuyeres 14 also cause the sawdust particles to heat up faster and burn quicker. The small volume and large area of annulus 19 results in a large amount of heat release area with high radiant heat causing the particles to heat up fast and burn quickly. This ability to heat the particles quickly is critical to the success of burner 100 in burning high moisture content fuel because moisture is driven out fast. Wood pyrolysis begins followed by complete combustion. The quicker the wood starts to burn the more stable the fire is and the more responsive the burner is to changes in heat demand. This burner can go from a minimum-firing rate to full fire in a matter of minutes. Another advantage of fast heating and drying of the particles is a smaller burner size. As a result of all of the wet sawdust can be burned efficiently with an extremely high TDR. For example. a TDR of at least 35: 1 can be achieved when burning green sawdust.

As wood particles in annulus 19 burn and become lighter. the cyclonic action causes the particles to rise out of the annulus into funnel section 5. Ignition tower 13 continues to provide heat for rapid heating and combustion of particles and gases in funnel section 5 of burner 100. More combustion air is injected tangentially into funnel section 5 through tuyeres 7. This air also adds to the cyclonic action and keeps

the sawdust in motion. This air also prevents fuel particles from building up on the walls of funnel section 5. Funnel section 5 expands in area allowing for the expansion of gases coming from the burning fuel. Bullet-shaped stabilizing cone 16 helps to form and smooth the flow of flame and gases exiting funnel section 5. Other shaped structures can be fitted on top of ignition tower 13 creating other flame patterns. The hot gases exiting the top of bullet-shaped stabilizing cone 16 help ignite the gases in the center of the tornado of flame, which helps stabilize the burning gases as they swirl past the cone and meet at the apex of the cone. Controlled high-velocity combustion air is forced into tuyeres 7. The right amount of air is injected to both keep the particles moving cyclonically and to continue combustion of the sawdust.

Funnel section 5 walls are angled up to keep the sawdust in the lower section to enhance combustion of the particles while at the same time preventing piling up of the material which would occur on a flat horizontal surface. More combustion air is injected tangentially to the combustion chamber 9 wall through tuyeres 8. Shear- tuyere air 10 is injected tangentially at a high velocity in an opposite direction to the direction of combustion airflow below. The shear-tuyere air also creates a shearing action and additional turbulence allowing for better air mixing with the gases and therefore better burning. The counter-flow also expands the flame out closer to the wall of the burner 100. The ignition tower 13, funnel 5 and counter-flow air 10 results in a high heat release ratio. For example, 100.000 Btu/cu. ft./hr. has been achieved burning green sawdust. Choke 11 in conjunction with the cyclonic action minimizes the unburned particles of wood from exiting burner 100.

Another embodiment of the burner is shown in Fig. 4. This embodiment utilizes a continuous ash removal system. In this arrangement, refractory floor 54 of annulus 19, as shown in Fig. 2, is removed and replaced with a revolving grate removal system 36. The level of ash is maintained at a proper level by means of a temperature-measuring device 35. An ash removal device maintains a solid plug of ash discharge 38 from a container 56 under burner 100 and discharges the ash into a suitable external container. This method of ash removal is for high ash density and high ash content fuels. The alternative method mentioned previously for burning with ignition tower 13 utilizing ignition can 2 must be used with this ash removal system.

In Fig. 3, a smoke-combustor 200 is mounted to the top of burner 100. Burner 100 produces hot exhaust gases of 1.600 degrees Fahrenheit or greater, which exit through choke 11 into a preheat tube 31 located in smoke-combustor heating chamber

22. Smoke or other combustible gases enter heating chamber 22 through one or more tuyeres 23 tangential to heating chamber 22 walls. The smoke or combustibles are heated by preheat tube 31 in heating chamber 22. A venturi 25 is built into smoke- combustor 200, which creates a negative pressure in heating chamber 22 drawing the combustible gases from heating chamber 22 and combustible gas tuyeres 23.

Controlled high-velocity air is forced through venturi tuyeres 26, causing the venturi action. Thus, the venturi tuyeres opening though the sidewalls of the venturi in upwardly incline. angular relation so as to emerge in the neck of the venturi, controllably and forcibly introducing high-velocity combustion air into the venturi at its narrowest section, accelerating flow venturi with venturi action. Controlling the amount of high-velocity air forced into venturi tuyeres 26 and cyclonic tuyeres 24 regulates negative pressure (i. e., partial pressure) created by venturi 25. If a larger negative pressure is desired, more air is forced into venturi tuyeres 26 and less air is forced into cyclonic tuyeres 24. If less negative pressure is desired more air is forced into cyclonic tuyeres 24 and less air is forced into venturi tuyeres 26. The high- velocity air is also the combustion air for ignition of the combustible gases. More combustion air is forced into the top of the venturi chamber 25 through four cyclonic tuyeres 24 in which the air exiting from these tuyeres intersects in a box pattern 32.

This method of entering air into the upper venturi chamber enhances the mixing of the air and combustible gases and causes the gases to burn in a cyclonic pattern in combustion chamber 28. Shut-off valves 34 are located on each venturi tuyere 26.

This allows air to be forced into one tuyere or in any combination up to all 6 tuyeres.

The ability to force air through one venturi tuyere 26 or any combination gives the capability of creating a high draft with a low volume of air due to the high velocity of air in the venturi tuyeres 26. Because of these capabilities, smoke-combustor 200 can maintain proper negative pressure for optimum draft control while maintaining the correct amount of air and temperature for combustion of the combustible gases in combustion chamber 28. A manifold 27 supplies the controlled pressurized air to venturi tuyeres 26. A second manifold 33 supplies controlled pressurized air to cyclonic tuyeres 24. A thermocouple in the combustion chamber 28 monitors the temperature, which is used to control the firing rate of burner 100 and the amount of air coming through venturi tuyeres 26 and cyclonic tuyeres 24. A stainless steel screen 29 is placed over the exhaust opening of the chamber to prevent anything from entering combustion chamber 28 and to create more surface to radiate heat back into

the exiting gas stream insuring that all the gas is completely burned. A refractory deflector 30 is also placed above the exhaust opening to radiate heat back into combustion chamber 28 to aid in maintaining temperature in combustion chamber 28 for proper combustion. This deflector 30 also prevents anything from entering combustion chamber 28.

The smoke-combustor can also be mounted at ground level and the exhaust gases from a burner can be ducted into the preheat tube in the smoke-combustor.

Fig. 5 displays a typical burner control scheme. A programmable logic controller (PLC) 37 automatically controls burner 100 and smoke-combustor 200.

PLC 37 can be any one of the various commercially available systems, such as those commercially sold under the trademarks"Allen Bradley'and"Modicon". PLC 37 accepts temperature inputs 36 from a heat demand source 35. The burner increases or decreases the amount of heat supplied to the heat demand source 35 based on parameters programmed into PLC 37. These parameters consist of temperatures that heat source 35 should be maintained at during any time in the process cycle of heat demand source 35. To maintain the correct temperature. PLC 37 sends electronic output signals to frequency changers 47 controlling the speed of motors on air blowers 38 and motors on fuel feed motors 41. Air blowers 38 supply all of the air to the burner as described in the previous paragraphs. PLC 37 also sends electronic signals to valves 40 located in the air supply lines to tuyeres 6,7,8 and 10 to further regulate the airflow to burner 100. PLC 37 receives temperature signals 39 from burner 100. It uses temperature signals 39 to monitor the internal condition of burner 100 and to make corrections if necessary. Electronic input signals are also received from gas or oil fired burner 12, which tell PLC 37 if burner 100 is operating properly.

Other input signals can be transmitted to PLC 37 signifying the status of motors. blowers. fuel handing equipment, etc., as conditions may dictate. Output signals can be added to operate other peripheral equipment, turn on alarms, provide current data, stored data. etc. as may be required. PLC 37 also regulates the speed of the ID fan (such as that designated 11 i in Fig. 1) when the latter is part of the system for thereby controlling the extent of partial pressure which results in air being drawn into the tuyeres.

Fig. 6 shows a typical control scheme of a burner and smoke-combustor system. A PLC 37 controls both burner 100 and smoke-combustor 200 for proper temperature and draft to completely combust the combustible gas or smoke produced

by a combustible gas source 43. PLC 37 receives temperature inputs 36 from smoke- combustor 200. PLC 37 increases or decreases the firing rate of burner 100 to maintain a proper temperature for complete gas combustion at temperature input 36 location. PLC 37 controls the burner firing rates as described previously. PLC 37 also receives pressure inputs 44 from combustible gas source 43. PLC 37 sends electronic output signals to frequency changers 47 controlling the speed of motors directly coupled to air blowers 46 attached to venturi tuyeres 26 and cyclonic tuyeres 24 on smoke-combustor. PLC 37 also sends electronic output signals to shutoff valves 34 located in venturi tuyeres 26 and to damper valves 45 located in combustible gas tuyeres 23 coming from combustible gas source 43. PLC 37. utilizing smoke-combustor venturi 25, maintains the correct draft in combustible gas source 43 by being able to control the flow in each venturi tuyere 26 and combustible gas tuyere 23. PLC 37 does this with valves and the ability to control the volume of air supplied to the tuyeres bv varying the speed of air blower 46. Other input signals can be transmitted to PLC 37 signifying the status of various pieces of equipment.

Output signals can be added to control other pieces of equipment, turn on alarms, provide data, etc.

EXAMPLES EXAMPLE 1 A practical embodiment of the new burner as according to Fig. 1 or 2 is scaled for small-scale use to provide a maximum output (firing rate) of 3MBtu/hr. but is capable of operation down to a minimum output of 1 OOKBtu/hr, and so provides a TDR of 30.

EXAMPLE 2 A practical embodiment of the new burner is constructed according to Fig. 2 for relatively large-scale use. When operating at maximum output. it achieves a firing rate of about 6.2MBtu/hr. and is capable of turndown to a minimum output of 100KBtu/hr. and achieves a TDR of about 62. A heat release ratio of 100.000 Btu /cu. ft./hr. is achieved burning green sawdust.

EXAMPLE 3 A practical embodiment of the new burner is constructed according to Fig. 2 for burning green sawdust. Ignition is achieved by firing the burner with fuel level to achieve a minimum starting level of 100 Btu/hr. When operating at maximum output, it achieves a firing rate green (wet) sawdust of 3. 5MBtu/hr. so that with operation capable of turndown to a minimum output of 100KBtu/hr. and thus achieves a TDR of 35. The burner can go from a minimum-firing rate to maximum output in a few minutes.

Description Of Further Version Of Gas Combustor Refer to Fig. 7 which is a vertical cross-section of another embodiment of a burner of the invention, namely a smoke combustor 300 which forms an assembly with a burner 100, including an ignition can 2, as generally according to Fig. 1, which has a high TDR for combustion of a principal fuel and which includes a gas or smoke- combustor 300 of a further improved type. It should be noted that the smoke combustor 300 can function quite satisfactorily with other styles of burners, e. g., natural gas burners, oil burners etc.

Thus. in a representative system, combustor 300 is mounted atop burner 100, including ignition can 2, generally according to Fig. 1. Burner 100 will not here be described again in detail. Burner 100 produces hot exhaust gases of typically 1600 deg. F. or greater. which exit through its choke 11. The incoming heated gases are used for preheating within combustor 300. and so may be referred to as hot preheat gases. They pass into a preheat tube 331 located in an inner burning chamber 352 of combustor 300. Preheat tube 331 is of relatively substantial thermal mass, being a hollow cast refractory material, herein called simply"castable."Tube 331 has a series of multiple tuyeres 364 opening through the cylinder walls and arranged circumferentially around and along the cylinder and oriented in such a way, that is, they are radially skewed, that they duct substantially tangentially to the outer wall allowing the burned gases from burner 100 to exit preheat tube 331 with a counter- clockwise cyclonic) flow. The top of preheat tube 331 is sealed off. i. e.. closed, with a castable top 365 (e. g., of material similar to preheat tube 331) which is bullet- shaped and closes the upper end of preheat tube 331. It is important to observe that preheat tube 331 is thus closed upwardly except through tuyeres 364 for causing all of the hot gases from burner 100 to exit through tuyeres 364 into the inner combustion chamber 352. Thus, the hot gases enter the latter chamber to burn smoke or off gases.

Smoke or other combustible gases to be burned enter inner burning chamber 352 through a large diameter tuyere 323 at a lower end of inner burning chamber 352, which tuyere directs flow of the gases to be burned tangential to inner burner chamber wall 352 for counterclockwise cyclonic flow in the inner combustion chamber. The gases to be burned may be smoke or other combustible gases produced by processes relating to such wood products and other gases, such as from kilns or primary burners, including various kinds of industrial off-gases. any of which are characteristically

combustible and may be degraded or converted from their present state to a safer state by more complete combustion.

Although a single large tuyere as that designated 323 is shown, there may be multiple tuyeres entering the inner combustion chamber, for example. from opposite sides of combustor 300. as in the embodiment shown in Fig. 3, and multiple such tuyeres may be in staggered or longitudinally stacked or arrayed relation, so that gases to be burned are introduced at or substantially near the lower end of the inner burning chamber. The vertical arrangement of preheat tuyeres 364 and the gas exit direction together ensure complete mixing of gases to be burned and preheat gases exiting burner 100 and entering combustor 300 for combustion therein. This complete mixing causes the mixed gases to burn faster and more completely within combustor 300 than would otherwise occur. The inherent relative high mass of (the refractory) cast preheat tube 331 also radiates heat into the incoming unburned gas stream for causing faster combustion and a more complete burn than otherwise could occur.

Controlled high-pressure air is forced through tangential tuyeres 353. Note Fig. 7 A- A showing a single row of ten tuyeres evenly spaced in the base of the inner burning chamber 352.. However, the number and size of tuyeres and number of rows of tuyeres will change depending on the size of the smoke combustor. This air, at 1 to 2 psig, as a representative pressure, is used as combustion air to burn the mixed gases and also for cooling to prevent inner combustion chamber 352 and outer combustion chamber 356 from becoming too hot. This method of forced entry of air into inner burner chamber at high velocity, preferably approximately 7000 fpm and higher. provides in this arrangement an essentially non turbulent laminar flow which results in a low Reynolds number, and enhances the mixing of the combustion air and gases causing the gases to burn in a cyclonic pattern in inner burning chamber 352. A manifold 327 supplies controlled pressurized combustion air to the tuyeres 353. A shutoff valve 334 is located on the inlet of manifold 327 if combustion air is not needed. If enough combustion air comes in with the smoke or off gases or enough excess air comes in with the external burner to complete combustion no other combustion air would be needed. so that valve 334 may be closed under these conditions.

A thermocouple 354 in inner combustion chamber 352 monitors the temperature and is used primarily to control the firing rate of burner 100 and combustor 300 and also the volumetric flow rate of air directed through tuyeres 353.

Stainless steel deflectors 355t are radially skewed and spaced around the periphery at the top of inner combustion chamber 352 additionally force the burning gases to exit chamber 352 and to enter outer burning chamber 356 with continued cyclonic rotation in a counter-clockwise direction for movement down chamber 356. Wall deflectors 355w are angled at approximately 35 deg. to outer wall 352w of the inner burner chamber in one horizontal row located approximately half way vertically down the wall, so that deflectors 355w cause the burning gases to continue to turn counter- clockwise as they travel down outer combustion chamber 356. The counter-clockwise path, which is thus essentially helical or cyclonic, of movement of the burning gases in outer combustion chamber 356 increases their dwell time, i. e.. the period of time required for them to transit outer combustion chamber 356, and so provides for much more complete combustion than otherwise would occur. Thus, there results a dwell time is approximately 0.81 seconds at maximum firing rate in the combustor 300 and approximately 0.94 seconds in a current example of the preheat duct.

After their cylonic or helical path up the inner combustion chamber. redirection, and then down the length outer combustion chamber, the burned gases exit outer combustion chamber 356 through an outer duct 357. which coaxially surrounds delivery duct 358. Outer duct 357 not only provides an outlet for exhaust flow of gas combustion products but also services as a heat exchanger. That is, duct 357 transfers heat from the burned gases to the unburned gases in input duct 358 entering combustor 300. and so preheating the entering gases. This preheating causes unburned gases or partially burned gases to ignite immediately when they enter an oxygen rich environment within inner combustion chamber 352. The preheating of the smoke is an important and critical part of the design enabling smoke combustor 300 to use very little outside fuel for smoke combustion.

As an example of using the system, incoming unburned gases may range in temperature from 1100 deg. F. to 1800 deg. F as opposed to 120 deg. F. to 160 deg. F with out the preheating duct. An ID fan 359 is used in a closed circuit duct to pull the gases into the smoke delivery duct 358. both inner and outer combustion chambers (respectively 352 and 356) and outer duct 357.

The burned gases in outer duct 357 can also be used to preheat combustion air for burner 100 by ducting the burned gases through a duct that transports combustion air to the burner creating an air heat exchange system. While such preheating is an advantage, being especially beneficial during very cold weather, it may be optional.

A thermocouple 359 in the smoke delivery duct 358 monitors incoming unburned gas temperature. Another thermocouple 360 in outer duct 357 monitors the burned gas temperature of the gases leaving combustor 300. Thermocouple 360 is used to regulate firing rates of burner 100 and the amount of air going into tuyeres 357. also advantageously may be used to regulates the amount of air going into tuyeres 8 of burner 100 in the system shown, to ensure the proper temperature is maintained for complete burning of the gases. (Feedback is from the thermocouples in the inner burner chamber and the smoke-eater outlet i. e. 359 and 360. The control is through PID i. e. proportional. integral, and derivative loop. The temperature can be maintained readily to a tolerance of +/-10 deg F. Six inches of insulation 362 in the form of high temperature ceramic fiber completely surrounds the outer burning chamber of combustor 300. Six inches of high temperature ceramic fiber insulation also surrounds outer duct 357. An outer laver of stainless steel or other suitable material 363 of. for example. 16 gauge 304 stainless steel which has moderate high temperature resistance surrounds the several inches of insulation, thereby protecting the insulation. The inner wall 357 and outer wall 356 of the burning chamber can be made of high temperature stainless steel or other suitable metal or castable.

The temperature inside the smoke combustor 300 and at its can be maintained easily at 1200 deg F up to 1900 deg F or higher without any outside burner support after a time period ranging anywhere from 0.5 hr to 8 hr of burner 100 startup depending on moisture content of the wood or comparable fuel fed to burner 100.

The reason for such small dependence on outside burner support is due mainly to the fact that the smoke is preheated to such high temperatures (1100 deg. F to 1700 deg. F in the heat exchange duct before it entry into the combustion chamber of smoke combustor 300. It will be noted that if oxvgen were introduced into the smoke carrying duct 358 the smoke would burn in the duct In general. dwell time as discussed above is a function of how much smoke is drawn into the kiln and the temperature it is heated to before it enters combustion chamber of smoke combustor 300 as well as the temperature of burned smoke maintained in smoke combustor 300. While the dwell times noted above are characteristic of a practical prototype. it is expected that in a construction of the invention using the inventive concepts of combustor 300 used with slower kiln charcoal production rates, the dwell time will increase.

Although combustor 300 is shown with burner 100, it should be emphasized that a combustor using the principles of combustor 300 can function with many other kinds of burners. Smoke combustor 300 is very efficient in that once it gets hot and starts burning smoke it needs little if any outside burner support to maintain combustion temperatures at 1525 deg F or higher. One of the main reasons smoke combustor 300 is able to maintain these temperatures without outside burner help is the tremendous temperature rise in the smoke (or other gas being combusted) resulting from the heat exchange duct system

EXEMPLE 4 An experimental prototype of smoke combustor 300 as initially heated with combustion output from burner 100 has been tested numerous times. All tests resulted in very little heat being supplied, after startup, from burner 100. As a matter of fact during the last test. the only outside heat needed was to warm up burner 100 and smoke combustor 300. A kiln was used with the experimental arrangement. and smoke from the kiln was made available to combustor 300 to be burned. Once the a kiln started producing smoke. the smoke combustor 300 maintained temperatures of 1600 deg F or more by simply burning the smoke from the kiln. In the worst case. the burner 100 supplied heat in the range of 500,000 btu to 200,000 btu per hour for 8 hours before it was turned off and operation of combustor 300 continued.

Temperatures as operation of combustor 300 continued were easily maintained between 1600 deg. F and 1700 deg. F and could have been still higher if permitted.

During these tests. temperature could be maintained +/-10 deg F. of desired setpoint with the possible exception of the first two hours of the kiln startup during which time the temperature varied more. The temperatures of the smoke entering smoke combustor 300 ranged from 1100 deg. F to 1800 deg. F. The total time to complete a kiln cycle ran from a high of 5 days for the first test to 3 days for the last two of several tests. This time was dependent on the amount of smoke being pulled from the kiln.

---end of Example 4---

Rather than mounted atop burner 100 for direct entry of gases from burner 100 into burner 300 as shown, combustor 300 can instead be mounted at ground level in an arrangement by which exhaust gases from burner 100 are ducted into combustor 300. Thus. if appropriate in such an arrangement. a booster fan could be utilized to "push"unburned gases to smoke combustor 300 but is preferable to maintain smoke combustor 300 at negative pressure wherein smoke is drawn into it.

Burner 100 is illustrated as having the previously-described configuration especially useful for burning particulate fuels such as wood or wood products, and when so used with burner 100, combustor 300 is intended for receiving at least start- up heat from burner 100, which produces no smoke but only essentially completely combusted gases. But combustor 300 may be used with other burners configured for burning other organic fuels such as fuel oil or fuel gases. capable of providing sufficient thermal flow of high temperature exhaust gases into combustor 300, including possibly smoke, so that such off-gases or smoke from other sources will be entrained into the exhaust gases entering combustor 300 and therein burned at still higher temperatures. It will be seen, therefore, that smoke combustor 300 may receive its heating (or preheating) gases from various kinds of burners, and its smoke or off-gases from various kinds of sources, including charcoal kilns and other smoke- producing processes.

In substantially the same way as for combustor 200, a control system is also provided for combustor 300 in accordance with the disclosure of Fig. 6. The control system provides the important function of controlling gas and air flows in response to said temperature to maintain proper partial pressures within combustor 300 for optimum draft control while maintaining the correct amount of air and temperature for combustion of the combustible gases in the gas combustion chamber.

Therefore, it is seen that combustor 300 comprises or consists essentially of a combustor housing mounted to or connected to burner 100 (or any other burner producing suitable exhaust heat) as a combustion source of hot preheat gases so that the combustor is situated for receiving the hot preheat exhaust gases from the combustion chamber exit of burner 100 or other burner, and such gases may for convenience here be called either combustion source gases or hot preheat gases, for they are used for preheating purposes. The housing defines a combustible gas heating chamber having coaxial inner and outer combustion chambers (respectively 352 and 356). having an inlet duct 358 and an outlet or discharge duct 357 coaxial with inlet

duct 358 for outward flow of burned gases from the outer combustion chamber (and for the purpose of preheating smoke or off gases before they enter the combustor 300.) Inlet duct 358 communicates with one or more inlet tuyeres 323 so that preheated combustible gases to be burned within the combustor are introduced into the inner combustion chamber at one end thereof with cyclonic flow. Preheat tube 31 located within inner combustion chamber 352 provides communication with the combustion chamber exit 11 (or exit chamber or nozzle of any other style or type of burner) from which hot gases are emitted, and so preheat tube 31 receives the preheat gases and thus introduces them through multiple tuyeres 364 opening through side walls of the preheat tube into inner combustion chamber 352, these tuyeres 364 being arranged circumferentially around the cylinder and along its so they duct substantially tangential to the outer wall for allowing burned gases from burner 100 or other burner to emerge from preheat tube 331 with cyclonic flow.

Inlet tuyere 323 (or multiple such tuyeres) similarly introduce combustible gases into inner combustion chamber352 combustible gas heating chamber cyclonically, by injection tangentially to outer walls of inner combustion chamber352 with the same direction of rotation about the vertical longitudinal axis of the heating chamber, such that the combustible gases in the inner combustion chamber 352 will be heated by the preheat tube 331 and their combustion there initiated. Also, combustion air tuyeres 353 open into the inner combustion chamber 352 though the side walls of the end of the heating chamber. and are so oriented for controllably and forcibly introducing high-velocity combustion air into the inner combustion chamber 352 for mixing of the air and combustible gases to burn with cyclonic pattern in the combustor. A redirector, in the form of slotted vents 361 at the closed upper, opposite end of the apparatus and which vents open from inner combustion chamber 352 to outer combustion chamber 356, serves as means for redirecting counterflow movement of combustion gases from inner combustion chamber 352 to outer combustion chamber 356 for say counterflow relative to the inner combustion chamber, so rotation of the gases continues flowing counterclockwise but vertically downward. The combustion gases accordingly travel though outer combustion chamber 356 along the separating wall 352w which separates the inner and outer combustion chambers. Vanes 355w are located in outer combustion chamber 356 for causing movement of the combustion flow in the outer combustion chamber 356 to be cyclonic. An outlet tube (duct 357) communicates with the outer combustion

chamber 356 at an end thereof remote from the redirection means, for delivery of completely combusted gases.

Outlet duct 357 extends away from outer heating chamber 356. and because this duct is coaxially outside inlet duct 358 which thus transports preheated combustible gases to be burned within combustor 300. heat is transferred from outlet duct 357 from the burned gases for initial preheating of the combustible gases to be burned.

Temperature measuring apparatus measures temperature in the gas combustion chamber.

As according to the description of Fig. 6, a control system controls gas and air flows (and burner 100 or other burner firing rates) in response to said temperature to maintain proper partial pressure within the smoke combustor for optimum draft control while maintaining the correct amount of air and temperature for combustion of the combustible gases in the inner and outer combustion chambers.

When combined with burner 100 9 (or any other burner), smoke combustor 300 will be appreciated to provide a system advantageously formed by the combination of a principal fuel burner having a high turndown ratio for combustion of at least a particulate primary fuel, such as wood sawdust, but may also or alternatively burn a secondary fuel such as natural or liquefied petroleum gas, or fuel oil, in which the fuel of whatever type is burned with combustion air to provide heated exhaust gases having thermal content and volume useful for preheating a further combustion process. and the smoke combustor carries out that combustion process. in that it defines a housing configured for receiving the preheated burner gases for complete combustion. The housing defines a combustible gas burning chamber having an inlet and an outlet. the burning chamber including, as herein described, coaxial inner and outer combustion chambers. One or more inlet tuyeres are connected to the inner combustion chamber for introducing combustible smoke or other gases (which will have been substantially preheated by the duct carrying the burnt gases away from the combustion chamber 300) to be burned into the inner combustion chamber at one end thereof with cyclonic flow. The combustor defines means for mixing combustion air with said combustible smoke or other gases to form a gas stream moving through the inner combustion chamber with cyclonic movement. A preheat tube is located within the combustible gas heating chamber into which the heated exhaust gases are ducted for preheating so as to cause heating of smoke to combustion temperatures. The

preheat tube is of substantial thermal mass and communicates with the inner combustion chamber exit through a plurality of apertures for controlled flow of said heated exhaust gases into the gas stream for heating the gas stream by mixing the exhaust gases with the stream of air and combustible gases for combustion thereof to provide combustion gases. The combustor also defines means at an opposite end of the inner combustion chamber for redirecting counterflow movement (counterclockwise flow) of said combustion gases from the inner combustion chamber to the outer combustion chamber for counterflow (counterclockwise flow) of combustion gases therein, whereby combustion gases thence travel though the outer combustion chamber, and along a separating wall which separates the inner and outer combustion chambers. The outer combustion chamber includes means for causing continued cyclonic movement of the combustion flow in the outer combustion chamber. and an outlet at an end of the outer combustion chamber remote from the redirection means for delivery of completely burned combustion gases.

Therefore, those skilled in the art will perceive that the combination of a high- output. high TDR burner such as burner 100 with smoke combustor 300, having a capability for burning smoke produced by various wood combustion processes. including charcoal production and waste wood combustion, as well as other smoky combustion of organic materials, offers a special synergism of features and advantages will be especially noteworthy in the wood products industries or any other industry that produces smoke or off gases suitable for burning, but it will be emphasized again that combustor 300 can be fired with any suitable type of burner.

In view of the foregoing description of the present invention and practical embodiments it will be seen that the several objects of the invention are achieved and many other avantages are attained.

The embodiments and examples were chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated.

As various modifications could be made in the constructions and methods herein described and illustrated without departing from the scope of the invention, it is intended that all matter contained in the foregoing description or shown in the accompanying drawings shall be interpreted as illustrative rather than limiting.

The breadth and scope of the present invention should not be limited by any of the above-described exemplary embodiments. but should be defined only in accordance with the claims appended hereto and their equivalents.