MXPA97009200A - Inte combustion gas generator - Google Patents

Abstract

The present invention relates to an apparatus for reducing nitrogen oxide emissions by mixing hydrogen prepared from a portion or all of the engine fuel within a single burner. The apparatus includes an insulated burner (10) having an internal combustion chamber (17, 40) to receive either a portion or all of the gaseous or liquid fuel for mixing with the air and subsequent ignition by a spark plug (27) . The camera is inside a preheater assembly of the power supply. A mixing chamber (17, 40) is included which has a series of diverters (22, 23, 32, 37) against which the injected steam of air and fuel collides causing complete and complete mixing of the air / fuel in a mixture. Subsequently burned and ignited, and then discharged into the combustion chamber of the engine itself. The preheat assembly (15, 31) increases the temperature of the incoming air / fuel mixture via a heat exchange process with the post-combustion gases from the combustion chamber. The apparatus improves operability and performance by conserving energy by isolating the burner, placing the burner section inside the feed preheater assembly, and placing the flow to the outer insulation (12), and the production or output of hydrogen can be increased by the reaction between carbon monoxide and the water produced by the main reaction or added separately

Description

INTERNAL COMBUSTION GAS GENERATOR BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of reduction of the emission of nitrogen oxide from turbines and internal combustion engines; and more particularly to a new means and method for conducting a feed mix stream from a preheater assembly to a fully insulated burner having an insulated internal burner that supplies gases from a portion or portion of the main fuel of the engine if it is gaseous or liquid to an isolated external burner. 2. Brief Description of the Prior Art It is well known that nitrogen oxides (NOx) are formed at high temperatures normally associated with combustion processes and operating in a motor at poor conditions with excess air at low temperatures and therefore decreases NOx. However, decades of motor studies and REF: 26217 turbines have shown that the limits of poor combustion are above those where the emissions of N0X are below specified targets. Natural gas and gasoline are examples where poor combustion has been pushed to its limit and where it has been found that the addition of hydrogen increases this limit to where the outlet of N0X is acceptably low. However, means to obtain hydrogen for this purpose are associated with problems. Problems and difficulties have been encountered when hydrogen supply is provided by materials carried in a separate tank which can be extremely heavy and requires pressurization. As examples, methanol, hydrogen or ammonium nitrate can provide or produce hydrogen when added to an engine combustion chamber. However, these take the place of fuel and reduce the volumetric storage capacity which reduces the overall performance, and results in complications through the use of secondary materials. Hydrogen stored in the pressurized container which maintains methane (hydrogen) can also be used, but this causes approximately 0.75 percent reduced engine interval for each percent of hydrogen used because of its very low energy contained in a volumetric base, and also requires special means to allow safe storage of hydrogen. The present invention teaches the use of a suboxylated burner using the main fuel to obtain hydrogen. Previous attempts have been made to improve the suboxidated burner described in the two previous patent applications of the applicant by pre-mixing air and fuel, preheating the fuel-air supply by exchanging heat with the products of the burner, and affecting the circulation of the combustion products. These previous attempts have been successful in reducing the emission of nitrogen oxide. Thus, the two-stage burner described in the first description uses technology to effect the chemical equilibrium with air-fuel formulations that contain a large excess of fuel and a second stage in the previous descriptions uses a related technology to try the balance between the products of the first stage and the excess of air.

Conventional burners operate rich air and react in two stages abruptly. The first stage includes regions with almost stoichiometric air-fuel ratios where high temperatures occur, which induces the start of an undesirable chemical reaction with the fuel. These temperatures result in high concentrations of N0X. A second stage operates rich air to achieve an air-fuel, global, final ratio. Its temperature is low but it is not low enough, so that N0X can not be formed, and this stage does not usually remove the N0X that has been formed in the first stage. The overall result is that the N0X formed in both stages appears in the exhaust gases of the burner. In the second patent application mentioned above, technology is described to obtain a chemical equilibrium between the air and a large excess of fuel in a suboxido heater through a process where the air-fuel mixture undergoes a certain investment of rapid flow. This technology results in a balance at a reasonably high temperature, without resulting in the formation of N0X, since its excessive concentration of fuel preferably causes a reaction between air and fuel instead of air and N3 to form N02. It has been found that the technology of the co-patents us. 07-858, 840 and 07-997, 450 results in products that are easily burned with additional air. As a consequence, a combustion chamber with excess air to drive motors that produce virtually zero NOx can be achieved by a two-stage related process. The first stage comprises a fuel-rich burner of the type taught in these co-patents. The second stage is a similar technology but it operates rich air. The first stage products and the excess air needed to obtain the final air-fuel mixture are introduced in the second stage. At this stage, a mixture of the latest air and latest products undergoes the same rapid flow reversal taught by the co-patents technology, which results in its rapid chemical equilibrium. In view of the improved reactivity of the fuel products obtained from the suboxylated burner, the induced flux reversals and the high relative concentration of hydrogen, equilibrium in the second stage can be induced at a high air-fuel ratio than that used usually. This results in very low temperatures where the formation of N0X is very low. The technology of the co-patents results in a suboxised burner replacing the almost stoichiometric regions usual in the first stage of a burner. While the latter produces N0X that eventually appear in the exhaust gases, the N0X can not be formed in the fuel rich, suboxylated burner. In contrast, this easily balances the CO and H2 of the fuel, and very small amounts of non-decomposed fuel. As a consequence, the injection of a mixture of these products and the air necessary to obtain the desired global air-fuel ratio in a second stage burner in which means are incorporated to achieve the same rapid fluid inversion taught in the -patents, results in a rapid chemical equilibrium. These factors, aided by the relatively high concentration of H2, allow stable combustion at an extremely poor air / fuel ratio at a relatively low temperature where N0X is not formed. Therefore, there has been an ancient need to provide new means and methods to achieve a breakthrough in technology; for a simple means of producing hydrogen from a fuel in a completely insulated, simple burner without the catalyst and without pressurized hydrogen, special or storage media related hitherto normally considered as required and by means of which improved results are obtained, using the first and second stages that are virtually free of N0X, as in the combustion chamber, global, which leads to a burner without N0X.

BRIEF DESCRIPTION OF THE INVENTION Consequently, the above problems and difficulties are avoided by the present invention; which provides a new means and method that utilizes a fully insulated burner to burn air and hydrocarbons at fuel-rich stoichiometric air / fuel ratios of 0.3 to 1.0, which includes a first stage burner having a combustion chamber properly coupled to a main source of fuel including means for diverting a portion of the main fuel in the burner with a portion or all of the main air so that the fuel portion and the air portion collide against a first arranged diverter whereby the shock mixes carefully the fuel / preparatory air combination for ignition in the combustion chamber. Means are provided for exhausting the burnt gases from the burner of the first stage in the combustion chamber of the burner of the second stage via a second diverter arrangement and then to the exhaust. The excellent mixing is provided by the shocks, resulting in the conclusion of a theoretical equilibrium of the fuel-rich reaction, despite the low reactivity of the original fuel in excess. Accordingly, it is a main object of the present invention to provide a completely insulated burner means having means for intimate premixing of the fuel; and an air deficiency which is achieved by putting the air and fuel together in a first separate chamber and then to a second chamber where the flow is induced to move back and forth via a series of derailleur assemblies in each of the preparatory chambers to enter the combustion chamber where the ignition of the mixture occurs.

Still another object is to provide a new means and method of burner apparatus which is very simple; means and non-catalytic burner method for producing hydrogen from a portion or all of the main fuel of the engine for injection into the main combustion chamber of the engine; with the fuel surplus or total fuel flow to achieve high air-fuel ratios that lead to a minimum or zero formation of nitrogen oxide. A further object of the present invention is to provide a hydrogen generator for use in connection with the reduction of nitrogen oxide in an engine emission, which does not require additives that degrade fuel performance and contribute a little to the complexity the motor. Still another object of the present invention is to provide a new means and apparatus and method that utilizes a fully two-stage insulated burner to reduce the nitrogen oxides of internal combustion engines and turbines; by the use of a simple hydrogen generator fed by a small portion or all of the main fuel of the engine, by means of which the resulting hydrogen produced to make co-heated or fluid in the engine with the rest of the main fuel, or as the gas. A further object resides in the provision of a means of preheating the air / fuel mixture and methodology to provide a high combustion temperature to assist the balancing process. Another object resides in the use of a burner preferably insulated with two fuel-air mixing chambers to ensure the vaporization of the liquid fuel with the increased production of hydrogen.

BRIEF DESCRIPTION OF THE DRAWINGS The features of the present invention that are believed to be new are set forth in the appended claims with particularity. The present invention, both in terms of its organization and form of operation, together with additional objects and advantages thereof, should be better understood with reference to the following description, taken in connection with the accompanying drawings in which: FIGURE 1 is a diagram of the theoretical equilibrium calculations for the methane-air combinations; FIGURE 2 is a longitudinal, elongated, schematic view, in section, illustrating the new burner medium without two-stage N0X which is used in a motor for the generation of hydrogen; FIGURE 3 is a diagram illustrating the theoretical temperatures and schematic sectional views of the hydrogen generator for the fuel / air feed (designated "normal") before and after (designated VOB) by heating to 1000 ° F, using a preheater medium that use the principles of the heat exchanger; FIGURE 4 is a cross-sectional, longitudinal, schematic view of a single stage burner of the prior art; FIGURE 5 is a schematic sectional view of another version of a two-stage burner having heat exchanger combustion chambers, individually isolated and separate; FIGURE 6 is a view similar to the mustard burner in Figure 5 showing a modified heat exchanger; FIGURE 7 is a cross-sectional view of the burner shown in Figure 5 as taken in the direction of arrows 7-7 thereof; FIGURE 8 is a cross sectional view taken in the direction of the arrows 8-8 in Figure 6; Y FIGURE 9 is a view similar to the burner shown in Figure 6 showing a preferred modified heat exchanger and also illustrates a cement or ceramic insulation ring between the heat exchanger and the back of the burner.

FIGURE 10 is a side elevation view of the non-assembled ceramic ring of the burner shown in Figure 9.

DETAILED DESCRIPTION OF THE PREFERRED MODALITY In conventional burners, as shown in Figure 1; the air relations (formula, 02 +3.76 N2) to fuel are established with more than enough oxygen (02) to react all carbon atoms (C) to carbon dioxide (C02) and all hydrogen (H) to water (H20) . With methane (CH) as fuel, this is represented by the equation (1) CH4 + S x 2 (02 + 3, 7 6 N2) = C02 + 2 H2 + S x 2 x 3. 7 6 N2 + 2 x (S - 1) 02, where S, the "stoichiometric ratio" of air / fuel, is the unit when there are just enough oxygen atoms to react with all the fuel atoms. The burners of the state of the art, used, for example, with motors normally operated with S greater than one, with excess air molecules (02 and N2) emerging relatively unchanged, except that at high temperatures excessive concentrations of NOx that are difficult to disassociate from the elements. This is an undesirable contaminant. The results of theoretical equilibrium calculations for methane-air combinations are assembled in Figure 1 for air / fuel S from 0.1 to 3.0, reaction to one atmosphere, and feed at 78 ° F. The species are given as moles of product per mol of methane feed against S, except NOx which is percent by volume, 10 times. The temperature is in degrees F divided by 1000. Virtually all potential products are included in the calculations. However, N2 is excluded because it exceeds the product of origin; can be calculated from S x 2 x 3.76. As shown, the NOx is 0.19 to 0.34% almost S = l where the temperature is high. These are excessive values. Because the excess air lowers the temperature, the N0X is .8% at S = 2 and only 0.01 at S = 3. At the last conditions, the reaction between N2 and 02 is slow, so the actual concentration of N0X is even less. However, normal burners do not operate stably at these poor conditions.

Copatent technology can result in a sub-oxidized burner that replaces the almost stoichiometric regions common in the first stage of a burner. While the latter produces N0X, which eventually appears in the exhaust, the N0X can not be formed in the sub-oxidized burner very rich in fuel, it is very easily balanced to CO and H2 of the fuel, and to very minor amounts of fuel without decomposing. As a consequence, the injection of a mixture of these products and the air necessary to achieve the desired total air-fuel ratio in a second stage burner incorporating a means to achieve the same rapid flow inversions taught by the copatentes, results in the rapid chemical balance. These factors, aided by the relatively low H2 concentration, allow stable combustion at extraordinarily poor air / fuel ratios with a relatively low temperature where NOx is not formed. The results are the first and second stages that are virtually NOx-free, as is the complete combustion chamber, which leads to a burner without NOx.

Figure 2 is an example of a burner without non-NOx incorporating the present invention and illustrated in the general direction of the arrow 10. A burner enclosure 11 is internally covered with an insulation material 12. The air is introduced via an inlet 13 with the flow that is controlled by a valve 14. A portion of the air controlled by the valve 14A passes to a heat exchanger 15 in a heat exchange relationship without the gases 16 inside a burner 17 of the first stage. The fuel is introduced to the heat exchanger through an inlet 18 and passed through a valve 19 to the heat exchanger 15. The preheated air / fuel mixture leaves the heat exchanger via a hole 20 and is introduced into the heat exchanger. a ring 21 enclosed by a tube 22. The gases pass through the ring and collide against the cover of a sleeve 23 which causes a 90 ° turn to be taken and eventually, the gases leave the sleeve 9 via an orifice 24. gases then collide against the isolated rear wall 25 where another 90 ° turn takes place. The gases are again turned 90 ° to the outer wall 26 and burned by a spark plug 27. The combustion mixture then moves through the first stage burner 17 to the fire wall 30 and exits the first stage chamber. via a tube 21. The remaining air from the valve 14 is moved to a heat exchanger 31, tubular, flat in a heat exchange relationship with the gases 24 and the heated air leaves the exchanger 31 and is introduced into the tube 32 via an inlet 33. This exchanger can be replaced by a straight tube leading to the tube 21. The mixed projects of air and burner leave the tube 32 via a hole 34 and move up to a second ring 35. The gases now collide on the closed end of a sleeve 37 where the gases now rotate 90 ° and leave the sleeve via an outlet opening 38 to collide in the fire wall where the flow is again rotated 90 °. The gases are then moved to the wall 26 of the cylinder in the second chamber or burner 40 of the second stage. The gases eventually exit the burner through an orifice 41. Acceptable formulations for the first and second stage burners can be induced from Figure 1. In this way, for the first stage sub-oxidized burner, S must be above 0.3 to prevent the solid carbon formulation from interfering with the operation of the burner or methane that could be difficult to burn in the second stage and be below approximately 0.6 to prevent NOx formation. For the second stage, S must be up to 3, preferably in 3 to prevent the formation of NOx. This last relationship includes the total air and fuel flows for both stages. Additional means are described to improve the operability and performance of the sub-oxidized operator while the energy is conserved through the isolation of the complete burner, the burner section is placed inside the feed preheater assembly, the mixture flow is placed feeding the preheater adjacent to the outer insulation and increasing the hydrogen output when the reaction between the carbon monoxide and the water produced by the main reaction or added separately. The previous copending descriptions noted above revealed a means to improve the sub-oxidized burner by premixing air fuel, preheating the fuel / air feed by exchanging heat with the products of the burner, and effecting the circulation of the combustion products. Additional means for improvement are discussed, as follows: Figure 3 includes theoretical temperatures for the air-fuel feed before and after heating at 1000 ° F, with an increase in the latter case from 600 ° to 800 ° F. As indicated in a previous application, the higher temperature greatly increases the probability of achieving the theoretical equilibrium necessary to provide hydrogen. Nevertheless, the achievement of these temperatures, requires the reduction of thermal losses. A methane burner operating at a stoichiometric ratio on the unit of C02 and H20, main products provides approximately 22,000 Btu / lb of methane, with the result that thermal losses in the range of 1000 Btu / lb or more are relatively unimportant and in this way its combustion temperature can achieve its theoretical 3300 ° F where chemical equilibrium is likely. On the other hand, much less energy is released in the reaction of the sub-oxidized burner because its oxidized byproducts are hydrogen and carbon monoxide. In this way, the curve marked "Btu / lb" in Figure 3 refers to the theoretical heat yields for the methane reaction of an air at sub-oxidized stoichiometric ratios from .25 to .75. This shows the energy output as low as approximately 500 Btu in the lowest practical ratio from approximately 0.3 and approximately 7500 to the upper ratio of approximately .5. To these productions of low energy, minor thermal losses become significant. The "normal" marked curve in Figure 3 refers to the theoretical temperature for the 78 ° F supply of sub-oxidized burners at stoichiometric ratios from .25 to .75. At the low practical ratio of .3, the production of heat is easily covered by heat losses, so that the theoretical temperature is virtually impossible to achieve. Even at the practically high ratio of 0.5, the theoretical temperature of 2300 ° F is hard to achieve unless the thermal losses are severely diminished. A means to reduce normal thermal losses is with insulation. As described in the copending applications and as shown in Figure 4, the burner wall 45 is always composed of material that is insulating to some degree.; however, this burner wall still results in heat losses because the thermal conductivity is proportional to the temperature difference and the insulation makes contact with the highest burner temperature on one side and the lowest external temperature on the burner. other side. Also, the thermal conductivity of the insulation of most of the insulation increases with temperature, as indicated in the following table from Carborundum for Fibrefax filter.

Temperature Conductivity F Btu-in / hr-ft2- ° F 500 .394 100 .643 1500 1.041 2000 1.504 2500 2.572 3000 6.300 Figure 3 also shows the theoretical hydrogen formed against the stoichiometric ratio. Due to the formation of water at low ratios, hydrogen decreases with the ratio increased from a maximum of at most 2 mol / mol of methane. Figure 3 also shows how a more or less constant mole of CO is formed per mole of methane. At low temperature, the CO reacts easily with water in a downstream change reaction to reform the hydrogen through the reaction, CO + H20 = H2 + C02, up to the stoichiometric ratio of .5 when all the CO is converted with the result that the total hydrogen remains about 2 moles per mole of methane. At very low ratios, additional hydrogen can be formed by adding excess water, as shown in the figure. These "change" reactions require cooling, perhaps in a cylinder located downstream of the burner, cooled as by a spiral heat exchanger with air flowing through it. In addition, the heat loss is proportional to the external areas, and the configuration of Figure 4 does not minimize this area. The burner of the prior art is indicated by the number 45 having a housing 46 with an internal combustion chamber 47. The heat exchanger 48 accepts fuel via the air inlet 48 via the inlet 50 with a portion of the fuel that is introduced via the inlet 51. The fuel / air is initially combined in a tube 52 having an open end so that the combined fuel / air is directed towards a diverter 53, as indicated by the flow of the arrows such that the flow reverses itself and exits through the tube 52 into a cup 53 where the streams collide on the diverter 53. The direction of flow is changed to 90 ° radially outward and then 90 ° to an opening 54 of a plate 55 in the combustion chamber 47 to exit via conduit 56. Additional description is found in the copending applications, noted previously. The heat loss can be reduced by placing a burner section with the feed heat exchanger, as indicated in Figure 5, which tends to "bend" the burner itself to more closely resemble a sphere. Although the embodiment shown in Figure 2 employs a thicker and more efficient insulation than the prior art, the version of Figures 5 and 7 as shown in the direction of the arrow is 60, is more efficient. The burner 60 has an outer section 61 with heavy insulation 62 that surrounds an interior section 63 that is hollow and open at one end at the number 64 closed in a wall 65. A first chamber 66 is defined between the interior section 63 heavily insulated and the outer section 61 while the number 67 indicates a second chamber within the inner section 63. A spiral heat exchanger 68 containing the feed mixture is placed in the first chamber 66 and having an inlet 70 and an outlet 71 of discharge in the second chamber 64. The air / fuel mixture enters the heat exchanger 68 via an inlet coil 72 and passes to an exit coil 73 via an intermediate coil 74 that surrounds the interior section 63. The ignition is achieved by the spark plug 73 inside the second chamber 67 the preheated air / fuel mixture is discharged from the outlet 71 when the gases collide against the wall 65 and reverse the direction of flow. The gases then flow from the second chamber 67 through the opening 64 to the first or outer chamber 66, to discharge the exhaust gases through the exhaust outlet 75. Therefore, the spiral heat exchanger 68 containing the feed mixture is surrounded by high temperature gases from the burner chamber 67. These hot gases are brought into contact with the inner surface of the insulating wall of the outer section 61 while the outer surface is in contact with the cold outside. As a result, the temperature chain through the insulation is higher which causes a considerable oscillation in the values of the heat flow. The embodiment of Figures 6 and 8 describe a section of heat exchanger that greatly reduces or decreases the oscillation values of the heat flow. The burner device is illustrated in the direction of the arrow 80 which includes an outer section 81 and an inner section 82, moreover of which are composed of insulated and arranged walls in a separate coaxial relationship defining a first chamber 83 and the chamber 84 internally of the burner that is open at the end 85. An inlet 86 carries air / fuel supply to a heat exchanger 87 which consists of a plurality of separate parallel tubes, coaxial with the burner and having opposites joined in tubes 88 and 89 ring. The tubular spokes 90-94 connect the parallel tubes of the heat exchanger with the inlet 86 while the similar tubular spokes 103 connect the other end of the parallel tubes with a feeding tube 95. The end of the tube 95 supports a diverter or cup 96 having a terminal wall against which the feed mixture strikes, which reverses the flow and then exits to the chamber 84 of the burner. The flow is struck against the terminal wall 98 which causes another directional reversal of the flow. The ignition is achieved by the spark plug 100 and the flow of the exhaust gases exits through the opening 85 to the first chamber 83 partially occupied by the heat exchanger 87. The discharge of the gases is via the outlet 102 of the exhaust gases. leak connected to the first chamber after the flow of the gases passes the heat exchanger. The heat exchanger forms an outer ring and an inner ring. The exterior contains the cooled feed mixture and is located adjacent to the outer wall of the insulation. Then, the complete heat loss from a burner is given to the difference between the feed mixture and the ambient temperature, rather than the much greater difference between the burner's exhaust gases and the environment. Also, as noted above, because the conductivity of normal insulation at high temperature increases with temperature, the heat loss to the environment is less than it would be if the burner gases at higher temperature were adjacent to the external insulation . For the thermal passage through the cylindrical insulation that surrounds the burner with the conductivity as given in the previous table with ID of 7 inches, OD of 10 inches and height of 7 inches and the gases of the burner that average 2100 degrees F, the 900 degree F feed gases, and the environment at 78 degrees F, the heat flux is 790 Btu / hr for a normal heat exchanger and only one heat flux 136 with the burner of the invention, which is a reduction to 30% Referring now to Figure 9, another burner version is illustrated in the general direction of the arrow 110 which, as previously described, includes an isolated, exterior wall 111 positioned co-axially with respect to an interior section 112 having a opening 113 in fluid communication with an interior, closed chamber 114. An outer chamber 115 is separated therefrom by a metal separator 116 similar to a "can". The outer chamber is in communication with an inlet 117 to drive the air / fuel mixture to a fully isolated injector-mixer 118 that includes an insulator plate or cup 120 to effect reversal of the flow of the feed mixture as previously described. A wall 121 of the inner section 112 causes another flow reversal. The spark plug 122 burns the gases in a burner chamber 123 to exit through the inner chamber 114 to an exhaust gas outlet 124. The feed gases enter the burner 110 through the inlet 117 and move radially through the outer space or chamber 115. The gases move against the insulated wall with 111 inside the ring and pass radially inwardly along the chamber 115 to the injector-mixer 118. The hot gases formed in the chamber 123 of the burner collide on the interior surface of the separator 116 and then pass radially outward to a bound ring by the separator and the interior section 112, isolated. Finally, the gases exit at outlet 124. The separator is the surface of the exchanger between the gas of the burner and the gases of supply. Its area is large enough, so there is no requirement for any of the "extended" surfaces. The flows are parallel, instead of counterflow, to limit the heat exchange and prevent the uncontrolled temperature caused by any conventional "start of combustion" process. This is not a requirement and counterflow can also be used. The burner concept of the invention can be used with diesel fuel and in diesel-type engines. A major problem with these engines is the particles (smoke) expelled from the back tube, which includes toxic material and provide a visual and auditory discomfort. These particles could be eliminated by using the first section of the burner of the invention to gasify all diesel fuel before injection into the engine, together with the additional air necessary to obtain the final air-fuel ratio. By doing so, diesel fuel can not produce particles. The process would also result in the engine burner's ability to operate at low air-fuel ratios, where NOx is not formed. The various air / fuel mixture shocks result in an intimate mixture that easily ignites and burns to completion in a certain volume. This volume can be decreased by approximately 25% by placing a preferably ceramic ring 125 inside the burner below the location where the fuel stream leaves the mixer, as shown in Figure 9. Apparently, the ring causes the Combustion will move from the sides of the burner and to its center, after which a portion spontaneously moves back toward the wall, and thus results in the most complete authorization of the burner volume. While the particular embodiments of the present invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made, without departing from this invention in its broader aspects, and therefore, the The aim of the appended claims is to cover all these changes and modifications as they fall within the true spirit and scope of this invention.

It is noted that in relation to this date, the best method known by the applicant to carry out the present invention is that which is clear from the present description of the invention.

Having described the invention as above, the content of the following is claimed as property:

Claims (24)

1. In an internal combustion apparatus, the improvement is characterized in that it comprises: a burner means having a pair of combustion chambers for burning air and hydrocarbons at fuel-rich stoichiometric air / fuel ratios of 0.3 to 1.0 to provide air vapors / gas; each combustion chamber includes a mixing means that intimately combines the vapors of air / fuel for injection into the internal combustion apparatus; the burner means have an input means which communicates with each of the combustion chambers of the pair, to receive a supply of fuel and air; a preheater means connected with each of the inlet means for heating the fuel and air supply; the mixing means in each combustion chambers of the burner means includes a diverting wall positioned in each combustion chamber to receive the combined / preheated air / fuel supply from the intake means in forced shock relation to create a mixed vapor; and the diverter wall receives and redirects the combined / preheated air / fuel mixture into the combustion chamber to further mix the air / fuel mixture.

2. The invention according to claim 1, characterized in that: each mixing means includes a tubular coil for receiving and mixing the air / fuel supply; and the preheater means constitutes a heat exchanger that uses burned gases in the combustion chambers to be conducted adjacent to the tubular coil in each combustion chamber to increase the temperature of the preparative air / fuel mixtures to enter the internal combustion apparatus .

3. The invention according to claim 2, characterized in that: each coil ends in an open outlet pipe immediately adjacent the diverting wall.

4. The invention according to claim 3, characterized in that: each coil is of sufficient length so that the internal air / fuel mixture is heated within the range of 500 ° to 1000 ° F.

5. The invention according to claim 4, characterized in that: the pair of combustion chambers are positioned with respect to each, to be along a common longitudinal axis in end-to-end relationship.

6. The invention according to claim 1, characterized in that it includes: each of the combustion chambers covered by an insulated layer separating the combustion chambers from the ambient atmosphere.

7. The invention according to claim 6, characterized in that: the combustion chambers are placed in relation to the ends and separated by a firewall.

8. The invention according to claim 1, characterized in that: the pair of combustion chambers is placed with a first chamber of the pair covered by a second chamber of the pair in separate coaxial relation; the preheater associated with the second chamber positioned between the second chamber and first chamber with the preheater associated with the first chamber positioned within the first chamber.

9. The invention according to claim 8, characterized in that: each combustion chamber is fixed by an insulating, reinforced wall.

10. The invention according to claim 9, characterized in that: the first chamber is open at one end to be in fluid communication with the second chamber.

11. In an internal combustion apparatus, the improvement characterized in that it comprises: a burner means for burning air and hydrocarbons to provide air / fuel vapors at fuel rich ratios of 0.3 to 1.0 times in the stoichiometric ratio; the burner means includes a pair of chambers having a mixing means in a first chamber of the pair that intimately combines the vapors of fuel air for injection into the internal combustion apparatus; the burner means includes a means of entering a second chamber of the pair to receive a supply of fuel and air; and a preheater means in a second chamber for heating the air fuel supply and which constitutes a heat exchanger using burnt gases in the first chamber to be conducted in the adjacent tubular coil in the second chamber to increase the temperature of the Preparatory air / fuel mixture to enter the first chamber.

12. The invention according to claim 11, characterized in that: the pair of chambers are each covered by an insulating layer to retain the heat inside the chambers.

13. The invention according to claim 12, characterized in that: the chambers are placed coaxially with respect to one or the other; the first chamber constitutes an internal chamber covered by the second chamber constituted an external chamber in separate relation; and the first chamber is open at the end in fluid communication with the second chamber.

14. The invention according to claim 13, characterized in that it includes: a separating plate placed in the space area between the first chamber and the second chamber defining an intake conductor channel to the mixing medium of the first chamber and an exit conduit of the first chamber to the internal combustion apparatus.

15. The invention according to claim 11, characterized in that it includes: an ignition means operably placed in the first chamber to ignite the air / combustion vapors.

16. An internal combustion apparatus, the improvement is characterized in that it comprises: a burner means for burning air / hydrocarbons to provide air / fuel vapors; the burner means has a first chamber surrounded by a second chamber fixed in a separate relation; each of the chambers are defined by an insulating wall; the preheater carrier medium in the burner means surrounding the second chamber, and ignition means placed in the second chamber to ignite air / fuel vapors.

17. The invention according to claim 16, characterized in that it includes: a mixing means in the second chamber that intimately combines the air / fuel vapors in the second chamber.

18. The invention according to claim 18, characterized in that it includes: a heat exchanger coil placed between the first and second chambers.

19. The invention according to claim 18, characterized in that: the heat exchanger is a spiral coil.

20. The invention according to claim 18, characterized in that: the heat exchanger is a helix.

21. The invention according to claim 18, characterized in that it includes: a separator plate placed in the first chamber defining a pair of fluid conduits with one selected in fluid communication with the second chamber and with the other conduit in fluid communication with the second chamber; internal combustion apparatus.

22. The invention according to claim 21, characterized in that: the first chamber is coupled in a mixer and air / fuel intake means with a selected conduit in fluid communication with the internal combustion apparatus.

23. The invention according to claim 22, characterized in that it includes: a ceramic ring placed in the second chamber placed coaxially with respect to the mixing means, to cause the flow of hot gases to go towards the center of the chamber.

24. An internal combustion apparatus, the improvement characterized in that it comprises a burner means for burning air and hydrocarbons to provide air / fuel vapors at fuel rich ratios of 0.3 to 1.0 times of stoichiometric ratio; the burner means includes a pair of totally insulated chambers having a mixing means in a first chamber of the pair that intimately combines the air / fuel vapors for injection into the internal combustion apparatus; the burner means includes a means of entering a second chamber of the pair to receive a supply of fuel and air; a preheater means in the second chamber for heating the fuel and air supply; the mixing means includes a diverting wall placed in the first chamber to receive the preheated and combined air / fuel supply in forced shock relation to create a mixed vapor; the diverter wall receives and redirects the preheated and combined air / fuel mixture into the first chamber to further mix the air / fuel mixture; the mixing means includes a tubular coil for receiving and mixing the air / fuel supply; and the preheater means constitutes a heat exchanger that uses burned gases in the first chamber to be conducted to the adjacent tubular coil in the second chamber to increase the temperature of the air / fuel mixture preparatory to entering the first chamber. SUMMARY OF THE INVENTION An apparatus for reducing nitrogen oxide emissions by mixing the hyen prepared from a portion or all of the engine fuel within a single burner is described herein. The apparatus includes an insulated burner (10) having an internal combustion chamber (17,40) to receive either a portion or all of the gaseous or liquid fuel for mixing with the air and subsequent ignition by a spark plug (27) The camera is inside a pre-heater assembly of the power supply. A mixing chamber (17, 40) is included which has a series of deviators (22, 23, 32, 37) against which the injected steam of air and fuel collides causing complete and complete mixing of the air / fuel in a mixture subsequently burned and ignited, and then discharged into the combustion chamber of the engine itself. The preheat assembly (15, 31) increases the temperature of the incoming air / fuel mixture via a heat exchange process with the post-combustion gases from the combustion chamber. The apparatus improves operability and performance by conserving energy by isolating the entire burner, placing the burner section within the feed preheater assembly, and placing the flow of the preheater feed mixture adjacent to the outer insulation (12); and the production or output of hyen can be increased by the reaction between carbon monoxide and water produced by the main reaction or added separately.