RU2507447C2 - Burner - Google Patents

Abstract

FIELD: power engineering.

SUBSTANCE: burner comprises a body, at least one air inlet hole for inlet of air, a mixing chamber, a fuel channel, comprising a fuel inlet hole for inlet of fuel and a fuel outlet hole for fuel exhaust, and designed for delivery of the fuel into the mixing chamber, the first channel for air flow, which comprises an inlet hole communicating with the specified at least one air inlet hole, and an outlet hole arranged near the fuel inlet hole, and which is designed to deliver air into the mixing chamber, and substantially a circular assembled chamber for collection of air that communicates with the specified at least one air inlet hole, substantially a circular mixing chamber for mixing of the air flow, substantially a circular wall, which substantially separates the specified assembled chamber and the specified mixing chamber, the first hole for air flow stretching between the specified assembled chamber and the specified mixing chamber, and having the first height being a part of height of the specified substantially circular wall.

EFFECT: invention makes it possible to increase quality of fuel burning, to reduce hazardous emissions to atmosphere.

28 cl, 42 dwg

Description

FIELD OF TECHNOLOGY

[0001] According to this application claims priority to provisional application US No. 61/099,200, filed September 22, 2008.

FIELD OF TECHNOLOGY

[0002] The present invention relates to burners and, in particular, to burners where air or oxygen is mixed with gaseous or vaporized fuel.

BACKGROUND

[0003] Burners that use gaseous or liquid fuels are used in many devices, including boilers, track heaters, furnaces, other gas equipment, and much more. Essentially, these burners introduce gaseous fuel or liquid fuel into the air or oxygen stream. If liquid fuel is used, it must first be vaporized or sprayed. The resulting stream of fuel and air or oxygen ignites and exits the burner nozzle either as a visible flame or as an extremely hot gaseous mixture stream.

[0004] In an attempt to improve the components of the prior art in various devices, such as boilers, track heaters, furnaces and other gas equipment, an in-depth study was conducted to determine the qualitative and quantitative characteristics of the prior art in each of these areas. The study showed that improvements can be made in each of these areas without exception, in particular with regard to lower operating costs and reduced or eliminated emissions. In today's global markets, operating costs and environmental issues, such as reducing or eliminating emissions, are usually two of the most important problems, and possibly the most important problems that most enterprises face.

[0005] It is noteworthy that from the prior art, it is obvious that the improvements that can be made to these various types of devices using burners to generate heat will not lead to a significantly improved end result. It is also obvious that the fundamental problem for all of these various devices, without exception, is the low efficiency of the burner. Most burners known in the art have an efficiency of only about 60% -70%. Combustion of low-efficiency fuels is a major problem inherent in all of these devices. Moreover, this problem of low combustion efficiency is the main cause of the two above-mentioned problems of the enterprise, namely operating costs and environmental pollution.

[0006] Thus, conclusions were drawn about the need for significant and fundamental improvements in the design of burners with the aim of fundamental improvement of devices such as boilers, track heaters, furnaces and other gas equipment. Namely, to maximize the performance of boilers, track heaters, furnaces and other gas equipment related to costs, efficiency, etc., it is necessary to fundamentally change the design of the burners that supply them with energy. Improvement of the boiler, track heater, furnace, etc. it makes no sense if the efficiency of the burners used in them is extremely low.

[0007] It is noteworthy that attempts at such improvements to various types of burners have been made over the years in various fields without significant success. In this regard, other types of improvements to burner systems and devices that use burners are commonly used.

[0008] The most common design improvement used to solve the problem of protecting the environment from emissions is the reuse of exhaust gases. It was found out that usually the reuse of exhaust gases can be successfully applied to reduce the total emissions of the burner system. However, there are problems associated with the reuse of exhaust gases. The most serious problem is that reuse of exhaust gases requires a lot of extra energy to pass the flow of the mixture, consisting of combustion air and added exhaust gas, through the system. For example, a 10% increase in the amount of exhaust gas returned to the burner usually results in about 40% -45% increase in the required power of the fan, which pumps air into the burner system. Obviously, this attempt to solve is unacceptable in terms of efficiency, and, consequently, costs. The situation is exacerbated when you consider that most of the exhaust gas passes through the burner system several times.

[0009] In addition, there are burner systems that use energy from high speed nozzles supplying combustion air to facilitate recycling within the burner system. The effectiveness of this technique depends on many factors, and usually the return of a large part of the combustion products to the burner is difficult if this technique is used, thus making it difficult to apply in many situations.

[00010] It is understood that reuse of exhaust gases to reduce emissions is not a viable solution for improving the design of burner systems. Burning fuel with the highest possible efficiency in one pass through the burner system is the only reasonable solution, however, burners with a sufficiently high efficiency do not exist.

[00011] Only a fundamental change in the design and principle of operation of the burner will allow you to create a burner with high efficiency and producing low emissions. The basic principle of burner operation has not essentially changed over the past few decades. In a study of the prior art, two examples of burners were found that are relatively effective in terms of efficiency and emission, but not sufficiently effective in comparison with the present invention described below.

[00012] US Pat. No. 7,484,956, issued February 3, 2009, authored by Kobayashi et al., Discloses combustion with a low emission of nitrogen oxides (NOx) using generated oxygen and nitrogen flows. Combustion of hydrocarbon fuels with a lower formation of nitrogen oxides is achieved by supplying fuel to an atmosphere slightly enriched in oxygen and separating air into oxygen-enriched and nitrogen-enriched streams that are supplied separately to the combustion chamber.

[00013] US Pat. No. 7,429,173, issued September 30, 2008, authored by Lanary et al. Discloses a gas burner for use in a furnace and a method for burning gas in a furnace, in particular, but not exclusively, a process furnace used in cracking or refining process. The gas burner contains two channels with adjacent exhaust openings. The first channel communicates with a source of compressed fuel gas and has an opening through which reused exhaust gas can enter the first channel, and the second channel communicates with an air source. During operation, the fuel gas is injected into the first channel, and the reused exhaust gas is thus drawn into the first channel so that it mixes with the fuel gas. The fuel gas partially burns out, and the mixture of partially burnt fuel gas and reused exhaust gas flows upward through the first channel, comes into contact with air from the second channel and burns out. The use of recycled exhaust gas keeps the nitrogen oxide emissions low, and since the recycled exhaust gas is drawn into the first channel by a stream of compressed fuel gas, there is no need for complex pumping mechanisms.

[00014] US Pat. No. 7,422,427, issued September 9, 2008, authored by Lifshits, discloses a burner having a high efficiency and low emission of nitrogen oxides and a method for its operation. The burner is intended to be installed in a furnace containing a mixing chamber bounded by at least the front wall of the furnace, two side walls, an upper wall and a lower wall; as well as heat-conducting pipes through which the heat-conducting medium flows, and which are located on at least one of the following walls: the upper wall, lower wall and side walls. The burner assembly is mounted on the front wall of the furnace and has a tubular element with an open distal end, which is located in the mixing chamber. The other end of the tubular element is attached to the front wall of the furnace. Several openings for combustion air pass into the tubular element from its other, proximal end and are connected to a source of combustion air. Several nozzles injecting fuel gas also pass into the tubular element from its other end and are connected to a fuel source. The furnace gas openings formed in the tubular element are located at some distance from the distal end, are located along the periphery of the tubular element, and are located relative to the mixing chamber so that the furnace gases circulate past some of the heat-conducting pipes before they reach the furnace gas openings with the formation of a mixture of combustion air, fuel gas and furnace gas. The fairing at the far end of the tubular element creates a reuse zone for the mixture downstream of the fairing and the tubular element.

[00015] In US Pat. No. 6,485,289, issued November 26, 2002, Kelly et al. Disclose a burner system and a combustion process with significantly reduced emission of nitrogen oxides. Gases from the zone of the fuel modification and enrichment reactor are mixed with products from the zone of the fuel depletion reactor in the zone of the low-temperature burnout reactor and reduced formation of nitrogen oxides. The fuel modification and enrichment reactor stabilizes combustion by reusing hot gases to the reactants. The decomposition reactions of nitrogen-containing products in the fuel enrichment zone inhibit the production of nitrogen oxides. Nitrogen-containing products from the fuel enrichment zone and nitrogen oxides from the fuel depletion zone then react in the burnout zone at the optimum temperature, and nitrogen-containing products are mixed if the amount of nitrogen oxides is reduced to a minimum. The temperature in all zones and, in particular, in the burnout zone can be controlled by involving furnace gas, initiated reuse of flue gases and active cooling using radiative and / or convective heat transfer. The release of nitrogen oxides can be further reduced by introducing ammonia or similar amine-containing products into the low temperature burnout zone. By balancing the reactions that inhibit combustion and emission formation, a small amount of emissions can be achieved in several zones with good stability characteristics - flame, fault tolerance, heat transfer and noise level.

[00016] It is an object of the present invention to provide a fuel nozzle for use in a burner and resulting in a very high efficiency in burning the fuel in the burner.

[00017] Another objective of the present invention is to provide a fuel nozzle for use in a burner and causing a minimum production of undesirable emissions by the burner.

[00018] Another objective of the present invention is to provide a fuel nozzle for use in a burner, wherein the fuel nozzle and burner can be used with various types of gaseous and liquid fuels.

[00019] Another objective of the present invention is to provide a fuel nozzle for use in a burner, the fuel nozzle and burner being cost-effective.

SUMMARY OF THE INVENTION

[00020] According to one aspect of the present invention, a novel fuel injector for use in a burner is provided. The fuel nozzle comprises a housing having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end. The fuel channel contains a fuel inlet for fuel inlet and a fuel outlet for exhausting fuel and is intended to deliver fuel to the mixing chamber of the burner. The first channel for air flow contains an inlet and an outlet located next to the fuel outlet for the release of fuel, and is designed to deliver air to the mixing chamber. Part of the first channel for air flow, located near the outlet, is directed at an angle with respect to the longitudinal axis.

[00021] According to another aspect of the present invention, there is provided a new fuel nozzle for use in a burner. The fuel nozzle comprises a housing having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end. The fuel channel contains a fuel inlet for fuel inlet and a fuel outlet for exhausting fuel and is intended to deliver fuel to the mixing chamber of the burner. The first channel for air flow is located on the outer part of the elongated housing, contains an inlet and an outlet located next to the fuel outlet, and is designed to deliver air to the mixing chamber.

[00022] According to yet another aspect of the present invention, there is provided a new fuel nozzle for use in a burner. The fuel nozzle comprises a housing having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end. The fuel channel contains a fuel inlet for fuel inlet and a fuel outlet for exhausting fuel and is intended to deliver fuel to the mixing chamber of the burner. The first channel for air flow contains an inlet and an outlet located next to the fuel inlet, and is designed to deliver air to the mixing chamber. The second channel for air flow contains an inlet and an outlet located next to the fuel outlet, and is designed to deliver air to the mixing chamber. The first channel for air flow and the second channel for air flow essentially surround the fuel channel.

[00023] Other advantages, features and features of the present invention, the operating principles and functions of the respective structural elements, as well as the connection of parts and production savings are more clearly understood from the following detailed description, the attached claims and drawings. A brief description of the drawings is given below.

BRIEF DESCRIPTION OF THE DRAWINGS

[00024] The novelty of the burner according to the present invention, relating to its design, organization, operation, principle of operation, as well as its other tasks and advantages, are clear from the following drawings, which depict a preferred embodiment, given as an example. It should be understood, however, that the drawings are for purposes of explanation and description only and do not limit the invention. In the attached drawings:

[00025] Fig. 1 is a perspective view of a first preferred embodiment of a burner according to the present invention;

[00026] Figure 2 shows a perspective view with the separation of parts of the first preferred embodiment of the burner shown in figure 1;

[00027] FIG. 3 is a left side elevational view of a first preferred embodiment of the burner of FIG. 1;

[00028] FIG. 4 is a right side elevational view of a first preferred embodiment of the burner of FIG. 1;

[00029] FIG. 5 is a plan view of a first preferred embodiment of the burner of FIG. 1;

[00030] FIG. 6 is a bottom view of a first preferred embodiment of the burner of FIG. 1;

[00031] FIG. 7 is a front elevational view of a first preferred embodiment of the burner of FIG. 1;

[00032] FIG. 8 is a rear elevational view of a first preferred embodiment of the burner of FIG. 1;

[00033] FIG. 9 is a side elevational view along line 9-9 of FIG. 8 of a first preferred embodiment of the burner shown in FIG. 1;

[00034] FIG. 10 is a top sectional view taken along line 10-10 of FIG. 8 of a first preferred embodiment of the burner of FIG. 1;

[00035] FIG. 11 is a perspective view of a rear housing element for controlling an air flow that is part of a first preferred embodiment of the burner shown in FIG. 1;

[00036] FIG. 12 is a side elevational view of a rear housing element for controlling the air flow shown in FIG. 11;

[00037] FIG. 13 is a front elevational view of a rear housing element for controlling the air flow shown in FIG. 11;

[00038] FIG. 14 is a rear elevational view of a rear housing element for controlling the air flow shown in FIG. 11;

[00039] FIG. 15 is a side elevational view along the line 15-15 of FIG. 13 of a rear housing element for controlling the air flow shown in FIG. 11;

[00040] FIG. 16 is a side elevational view in line 16-16 of FIG. 13 of a rear housing element for controlling the air flow shown in FIG. 11;

[00041] FIG. 17 is a side elevational view, taken along line 17-17 of FIG. 13, of a rear housing element for controlling the air flow shown in FIG. 11;

[00042] FIG. 18 is a perspective view of a wider rear of an external housing element that is part of a first preferred embodiment of the burner shown in FIG. 1;

[00043] FIG. 19 is a side elevational view of the wider rear portion of the outer housing element of FIG. 18;

[00044] FIG. 20 is a front elevational view of a wider rear portion of the outer housing element of FIG. 18;

[00045] FIG. 21 is a rear elevational view of a wider rear portion of the outer housing element of FIG. 18;

[00046] FIG. 22 is a side elevational view along line 22-22 of FIG. 20 of the wider rear of the outer housing element of FIG. 18;

[00047] FIG. 23 is a perspective view of a fuel injector that is part of a first preferred embodiment of the burner shown in FIG. 1;

[00048] FIG. 24 is a side elevational view of the fuel nozzle of FIG. 23;

[00049] FIG. 25 is a front elevational view of the fuel nozzle shown in FIG. 23;

[00050] FIG. 26 is a rear elevational view of a fuel injector of FIG. 23;

[00051] FIG. 27 is a side elevational view in section along line 27-27 of FIG. 26 of the fuel injector shown in FIG. 23;

[00052] FIG. 28 is a perspective view of a narrower front of an external housing element that is part of a first preferred embodiment of the burner shown in FIG. 1;

[00053] FIG. 29 is a perspective view of a separation of the parts of the narrower front portion of the outer housing element of FIG. 28;

[00054] FIG. 30 is a left side elevational view of a narrower front portion of the outer housing element of FIG. 28;

[00055] FIG. 31 is a right side elevational view of the narrower front portion of the outer housing element of FIG. 28;

[00056] FIG. 32 is a plan view of a narrower front of the outer case member shown in FIG. 28;

[00057] FIG. 33 is a bottom view of a narrower front of the outer case member shown in FIG. 28;

[00058] FIG. 34 is a front elevational view of a narrower front of the outer case member shown in FIG. 28;

[00059] FIG. 35 is a rear elevational view of a narrower front portion of the outer housing element of FIG. 28;

[00060] FIG. 36 is a top sectional view taken along line 36-36 of FIG. 34 of the narrower front of the outer case member of FIG. 28;

[00061] FIG. 37 is a side elevational view along the line 37-37 of FIG. 34 of the narrower front of the outer case member of FIG. 28;

[00062] FIG. 38 is a side elevational view of the burner shown in FIG. 1 with a combustion chamber located in place and during operation;

[00063] FIG. 39 is a side elevational view of a second preferred embodiment of a burner according to the present invention;

[00064] FIG. 40 is a top sectional view taken along line 40-40 of FIG. 39 of a second preferred embodiment of the burner of FIG. 39;

[00065] FIG. 41 is a side elevational view of a fuel injector that is part of a second preferred embodiment of a burner according to the present invention; and

[00066] FIG. 42 is a side elevational view similar to FIG. 41, but in this case, the nozzle tip is removed from the nozzle body.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[00067] Turning to FIGS. 1-42, it should be noted that FIGS. 1-38 display a first preferred embodiment of a burner according to the present invention, and FIGS. 39-42 display a second preferred embodiment of a fuel injector according to the present invention.

[00068] Figures 1-38 illustrate a first preferred embodiment of a burner according to the present invention, indicated at 30. Burner 20 in a preferred embodiment comprises a housing 22 having a front end 24 and a rear end 26. The housing 22 defines a longitudinal axis L extending between the front end 24 and the rear end 26. It should be understood that although for some forms of burners the definition of the front end and the rear end can be rather arbitrary, the front end is usually considered the one where the flame is produced, and the trailing end is the area where air and fuel are admitted, and where the mixing of air and fuel begins.

[00069] It should be understood that for convenience, the term "air" is used to describe the air received from a source of injected or compressed air, as well as oxygen from a source of injected or compressed oxygen. If an air source is used, the oxygen present in the air reacts with a fuel such as propane, natural gas, and the like. The nitrogen present in the air simply separates from oxygen during combustion. It is possible to use hydrogen with oxygen.

[00070] In a preferred embodiment, as shown in the drawings, but not required to be completed, the housing 22 comprises a rear housing element 30 for controlling the air flow and an external housing element 40. The rear housing element 30 for controlling the air flow is removably and removably attached to the outer housing element 40 by means of a threaded connection 23. A substantially direct fuel injector 50 is located inside the rear housing element 30 to control the flow of air and the outer housing element 40.

[00071] The outer housing member 40 includes a wider rear 42 and a narrower front 44. The wider rear has an inclined outer surface 42a and a through hole 43 with an inclined inner surface 43a and a constant diameter part 43b. The inclined inner surface 43a defines the outer wall of the wide air storage chamber 70. A part with a constant diameter 43b receives a substantially straight fuel nozzle 50 and is in close contact with it.

[00072] The narrower front portion 44 comprises a cylindrical tube 44a, a rear flange 44b welded to the rear end of the cylindrical tube 44a, and a front plate 44c welded to the front end of the cylindrical tube 44a. The narrower front 44 is attached to the wider rear 42 by a threaded joint 41. The front plate 44c is supported by three support flanges 44d welded to the cylindrical tube 44 and held in place by a threaded joint 44i. The front plate 44c also includes an annular rim 44e resting on an annular shoulder 44f located on the rear end of the front end portion 44g of the smaller diameter of the narrower front portion 44. Further, the front plate 44c contains a circular recess 44h for receiving the rear end 45b of the combustion chamber tube 45 . The rear end 45b of the combustion chamber tube 45 comprises an external thread portion 45c cooperating threadedly with a corresponding internal thread portion 44h on the front plate 44c. The tube 45 of the combustion chamber forms a chamber in which the flame generated by the burner 20 according to the present invention is enclosed. The length and inner diameter of the tube 45 of the combustion chamber can be selected to achieve the maximum emission of flame, as desired, and can also be selected to create certain resonances associated with the release (flame) of the burner 20.

[00073] The element 30 comprises a housing 32 having a front end 33 and a rear end 34. The longitudinal axis L extends between the end 33 and the end 34. Preferably, the housing 32 is made of metal, but can be made of any other suitable material.

[00074] The element 30 also comprises a channel 36 in the housing 32 for positioning the nozzle. The channel 36 is generally located in the center 32 of the housing 32 and is oriented along the axis L. The element 30 also comprises an annular conical portion 37 protruding forward from the housing 32. The channel 36 passes through the portion 37.

[00075] In the housing 32 there is at least one air inlet for air inlet, and in a preferred embodiment of the invention, as shown in the drawings, in the body 32 there is a first air inlet 38 for air inlet and a second air inlet 39 in particular in element 32. The first air inlet 38 and the second air inlet 39 are 180 ° apart to effectively maximize subsequent mixing of the air flow. Each of the holes 38 and 39 is oriented generally along the L axis, as shown in the drawings, but in other embodiments, the invention can be oriented at a different angle. In said housing 32, additional air inlet openings for air inlet are possible to provide introduction of additional air if necessary.

[00076] In addition, it should be noted that according to an alternative embodiment of the invention, additional inlets may exist for introducing a secondary fuel such as hydrogen, and even introducing unburned emissions from other types of burners and the like.

[00077] The element 30 for regulating air flow comprises, in the housing 32, a substantially annular collection chamber 29 for collecting air. The chamber 29 communicates with the hole 38 and the hole 39. The specified annular passage for the passage of flow has a substantially circular shape.

[00078] In addition, in the housing 32 there is a substantially annular mixing chamber 100 for mixing the air flow. The mixing chamber 100 also has a substantially circular shape.

[00079] The substantially annular wall 110 generally separates the collection chamber 29 and the mixing chamber 100. The substantially annular wall 110 has a substantially circular shape.

[00080] The assembly chamber 29 generally surrounds the chamber 100. The height of the chamber 29 and the height of the chamber 100 are equal to each other. In addition, the chamber 29 and the chamber 100 are substantially longitudinally aligned with each other along the longitudinal axis L.

[00081] The first air inlet 38 and the second air inlet 39 are located behind the collection chamber 29 to provide a forward flow of air properly directed into this chamber 29. Thus, fasteners by which the air pipes are connected to the first air inlet 38 and the second air inlet 39, do not protrude outward in the lateral direction, which could be unreliable.

[00082] A first air flow opening 101 extends between the collection chamber 29 and the mixing chamber 100. The first opening 101 has a first height, which is part of the height of the annular wall 110. There is also a second air flow opening 102, which extends between the collection chamber 29 and mixing chamber 100. The hole 102 has a second height, which is part of the height of the annular wall 110. The height of the first hole 101 for air flow is greater than the height of the second hole 102 for air flow.

[00083] The burner 20 also includes a third hole 103 for air flow passing between the collection chamber 29 and the mixing chamber 100. The third hole 103 has a third height, which is part of the height of the annular wall 110. The height of the first hole 101 for air flow is greater than the height the third hole 103 for air flow, and the height of the second hole 102 for air flow is greater than the height of the third hole 103 for air flow.

[00084] The burner 20 also includes a fourth hole 104 for air flow passing between the collection chamber 29 and the mixing chamber 100. The fourth hole 104 has a fourth height, which is part of the height of the annular wall 110. The height of the first hole 101 for air flow is greater than the height fourth hole 104 for air flow. The height of the second hole 102 for air flow is greater than the height of the fourth hole 104 for air flow. The height of the third hole 103 for air flow is greater than the height of the fourth hole 104 for air flow.

[00085] It was found that the height difference between the first hole 101, the second hole 102, the third hole 103 and the fourth hole 104 provides efficient dynamic mixing of the air flow entering the mixing chamber 100.

[00086] In an alternative embodiment of the present invention, it is possible that the first, second, third and fourth openings for the air flow are oriented at a certain angle such that the air flowing through them enters the mixing chamber 100 at an angle, so that they are annular in the mixing chamber 100 swirling flows.

[00087] The substantially straight fuel injector 50 comprises an elongated housing 55 comprising an inlet end 56 and an outlet end 57, and is substantially circular in cross section. Housing 55 defines a longitudinal axis L extending between end 56 and end 57.

[00088] The fuel injector 50 comprises a substantially straight fuel channel 58 centrally located in the elongated housing 55. A substantially straight fuel channel 58 has a fuel inlet 53 for fuel inlet and a fuel outlet 54 for discharging fuel and is intended to deliver fuel to the mixing chamber 80 of the burner 20 by conducting a fuel flow from the hole 53 to the hole 54. In the first preferred embodiment, as shown in the drawings, the hole 54 actually contains a first fuel outlet a fuel discharge port 54a, a second fuel exhaust port 54b, a third fuel exhaust port 54c, a fourth fuel exhaust port 54a, a fifth fuel outlet 54e and a sixth fuel outlet 54f . The first hole 54a, the second hole 54b, the third hole 54c, the fourth hole 54d, the fifth hole 54c and the sixth hole 54f are oriented at an angle of about ten degrees with respect to the longitudinal axis L, which has been found to allow complete atomization of the fuel, thereby it is ready for evaporation in the air. In another embodiment, any other suitable angle may be used.

[00089] Preferably, the elongated housing 55 comprises a narrow rear portion 55a having a circular cross section, a wider front portion 55b having a circular cross section, and a beveled portion 55c connecting the narrow rear portion 55a and the wider front portion 55b. The fuel inlet 53 is located at the inlet end 56, and the fuel outlet 54 is located at the outlet end 57. The chamfered portion 55 of the fuel nozzle 50 is hermetically connected to the corresponding receiving surface 21 of the burner body 20. There is also a stepped nozzle attachment part 59 located on the fuel channel 58 at the inlet end 56 of the housing 55.

[00090] The fuel nozzle 50 also includes an outer rear 51 protruding from the rear end 26 of the housing 22 of the burner 20. Preferably, the rear 51 of the fuel nozzle 50 is threaded to receive the corresponding nut, thereby holding the fuel nozzle 50 in place case 32.

[00091] To supply the air stream from a compressed air source (not shown) to the mixing chamber 80 of the burner 20, a first channel 90a for air flow, a second channel 90b for air flow, a third channel 90c for air flow, a fourth channel 90a for air flow and a fifth channel 90e for air flow. It was found that it is preferable to perform just such a number of channels for air flow, to achieve a uniform air flow and its distribution, there are two or more channels 90 for air flow. Any suitable number of channels for air flow can be made, depending on the scope of the burner 20, the size of the burner 20 and the fuel injector 50, etc. According to the present invention, various fuel injectors have been tested, including having two channels for air flow or more. It was determined that each specific number of channels for air flow may have its advantages and disadvantages.

[00092] Each of the first, second, third, fourth, and fifth ducts 90a, 90b, 90c, 90d, 90e for the air flow comprises an inlet 91 and an outlet 92 located adjacent to the fuel outlet 54 and is intended to deliver air to the mixing chamber 80 of the burner 20. As can be seen from the drawings, part 93 of each of the first channel 90a for air flow, the second channel 90b for air flow, the third channel 90c for air flow, the fourth channel 90d for air flow and the fifth channel 90e for air flow located next to the issue Ohm of this channel for air flow, is oriented at an angle with respect to the longitudinal axis L. More precisely, almost the entire first channel 90a for air flow, the second channel 90b for air flow, the third channel 90c for air flow, the fourth channel 90d for air flow and the fifth the air flow passage 90e is oriented at an angle with respect to the longitudinal axis L. More specifically, the first air flow passage 90a, the second air flow passage 90b, the third air flow passage 90c, the fourth air flow passage 90d and the fifth flow passage 90e air flow battening form. Each of the spiral-shaped air flow channels 90 is substantially parallel to the adjacent spiral-shaped air flow channels 90. The spiral-shaped air ducts 90 are preferably located on the outside of the fuel injector 50.

[00093] The inlet 91 of the first channel 90a for air flow has a cross-sectional area greater than the cross-sectional area of the outlet 92 of the first channel 90a for air flow; the inlet 91 of the second air flow passage 90b has a cross-sectional area larger than the cross-sectional area of the outlet 92 of the second air flow passage 90b; the inlet 91 of the third channel 90c for air flow has a cross-sectional area greater than the cross-sectional area of the outlet 92 of the third channel 90c for air flow; the inlet 91 of the fourth channel for air flow has a cross-sectional area greater than the cross-sectional area of the outlet 92 of the fourth channel 90d for air flow; the inlet 91 of the fifth channel 90e for air flow has a cross-sectional area greater than the cross-sectional area of the outlet 92 of the fifth channel 90e for air flow. Preferably, the cross-sectional areas of the inlet openings 91 are identical, and the cross-sectional areas of the outlet openings 92 are also identical.

[00094] Further, the ratio of the cross-sectional area of the inlet 91 of the first air flow channel 90a to the cross-sectional area of the exhaust opening 92 of the first air flow channel 90a is about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the second channel 90b for air flow to the cross-sectional area of the outlet 92 of the second channel 90b for air flow is about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the third channel 90 s for air flow to the cross-sectional area of the outlet 92 of the third channel 90c for air flow is about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the fourth channel for air flow to the cross-sectional area of the outlet 92 of the fourth channel 90d for air flow is about 1.6 to 1; and the ratio of the cross-sectional area of the inlet 91 of the fifth channel 90e for air flow to the cross-sectional area of the outlet 92 of the fifth channel 90e for air flow is about 1.6 to 1.

[00095] It was noted that a ratio of about 1.6 to 1 can be more accurately expressed by the term "golden ratio", also known as the "golden number", which is often denoted by the Greek letter φ, and is determined by the mathematical expression (1 + √5) / 2, which is approximately equal to 1.618033987.

[00096] Further, it is preferable if the cross-sectional area of each of the five channels for air flow 90 decreases in the direction from the inlet 91 to the outlet 92. More precisely, it is also preferable if the width of each of the five channels 90 for air flow decreases from the inlet 91 to the outlet 92 for ease of manufacture, but the depth remains constant. It is entirely acceptable if the depth of the five channels 90 for the air flow also decreases from the inlet 91 to the outlet 92, either in addition to decreasing the width of the channels 90, or instead of decreasing the width of the channels 90.

[00097] As can be seen from FIG. 1, the wider front portion 55b of the fuel injector 50 is hermetically connected to the front section 24 of the burner 20 having a constant cross-sectional area. Accordingly, air must pass through the spiral-shaped air flow passages 90 in order to reach the mixing chamber 80.

[00098] As can be seen from the drawings, six fuel exhaust openings 54a, 54b, 54c, 54a, 54e, and 54f are arranged slightly in front of the exhaust openings of the five ducts 90a, 90b, 90c, 90d, and 90e for air flow, allowing air flowing from these five air flow paths 90a, 90b, 90c, 90d and 90e to flow forward and substantially pick up fuel from the six fuel outlets 54a, 54b, 54c, 54d, 54e and 54f of the fuel injector 50 with him.

[00099] The burner 20 also includes a mixing chamber 80 in communication with the openings 54a, 54b, 54c, 54d, 54e and 54f and with the outlet openings 92 of the five channels 90a, 90b, 90c, 90d and 90e. The mixing chamber 80 is located slightly in front of the fuel outlet holes 54a, 54b, 54c, 54d, 54e and 54f of the fuel nozzle 50 and to the outlet holes 92 of the five channels 90a, 90b, 90c, 90d and 90e and aligned with the fuel axis L channel 58.

[000100] The burner 20 also includes a wide accumulation chamber 70 for storing air, located between the first air inlet 38 for air inlet and the second air inlet 39 for air intake and communicating with them, as well as five channels 90a, 90b, 90c, 90d and 90e for spiral flow of air. Preferably, the wide accumulation chamber 70 has an annular shape and tapers from the rear to the front. The wide accumulation chamber 70 comprises a narrow air inlet 72 for communicating with the first air inlet 38 and the second air inlet 39 through the rear housing element 30 for controlling the air flow. Accordingly, the wide accumulation chamber 70 receives air from the first air inlet 38 and the second air inlet 39. The wide accumulation chamber 70 also contains a narrow air outlet 74. Accordingly, the air from the first air inlet 38 and the second air inlet 39 is transferred to five channels 90a, 90b, 90c, 90d, and 90e for the spiral air flow of the fuel injector 50.

[000101] It has been found that a wide accumulation chamber 70 with an air inlet 72 and a narrow air outlet 74 seeks to disperse the air flowing from the substantially annular mixing chamber 100 for air flow to the channels 90 for spiral-shaped air flow. The cross-sectional area of the air outlet 74 is narrower than the cross-sectional area of the wide storage chamber 70 when measured crosswise with respect to the longitudinal axis L.

[000102] During operation, as shown in FIG. 38, air enters the element 30 through at least one air inlet 38 and a second air inlet 39 and is initially collected in the collection chamber 29. Air flows from the collection chamber 29 into the mixing chamber 100 through the first hole 101, the second hole 102, the third hole 103 and the fourth hole 104. The difference in the heights of the first hole 101, the second hole 102, the third hole 103 and the fourth hole 104 is due to the air entering the mixing chamber 100 on four clearly expressed and distinct from each other "levels" (relative to the axis L), resulting in a non-laminar air flow. Due to this, the air is as turbulent as possible, which contributes to the complete mixing of the air downstream with the fuel from the tip 60 of the fuel nozzle. Then, the air passes through the wide chamber to the accumulation chamber 70 and exits through the narrow air outlet 74, which leads to an acceleration of the air flow.

[000103] Further, air from the wide accumulation chamber 70 must enter and pass through the first air flow passage 90a, the second air flow passage 90b, the third air flow passage 90c, the fourth air flow passage 90a and the fifth flow passage 90e air, after which it is immediately supplied to the mixing chamber 80 of the burner 20. A fast air stream then passes through the end of the outlet 57 of the elongated housing 55 of the substantially straight fuel nozzle 50, and through the tip of the fuel nozzle 60, so as to mix with the fuel supplied and the tip of the fuel nozzle 60. Due to the reduction of the cross-sectional area of the five channels 90a, 90b, 90c, 90a, and 90e for the air flow from the inlet openings 91 to the outlet openings 92, the air leaves the outlet openings 92 at a significantly higher speed than that with which he enters inlet 91.

[000104] Further, because the first air flow passage 90a, the second air flow passage 90b, the third air flow passage 90c, the fourth air flow passage 90a and the fifth air flow passage 90e all have a spiral shape, air, exiting the exhaust openings 92 of each of the five air flow channels, it moves along a rapidly rotating spiral path along the mixing chamber 80, as indicated by arrow B, in the direction of the combustion chamber 82, and then even in the combustion chamber 82 itself. The swirl of air in the combustion chamber 82 provides a significantly longer path of air movement inside the combustion chamber 82 compared with the actual length of this combustion chamber 82. Thus, air spends much more time in the chamber, and the amount of fuel that the air “picks up” increases. Fuel is widely dispersed, as indicated by arrows A, in spinning air. Due to the swirling of air, there is enough time for combustion, and thus for heat generation, and thus, there is enough time for heat transfer from the combustion chamber 82 through the tube 85 of the combustion chamber to the environment, where the heat is delivered to the desired point . In tests, it was found that the flame temperature of the burner 20 according to the present invention can easily exceed 2000 degrees, and provide an exhaust temperature of about 400 F, which is 1600 F lower than it took to increase the temperature of the heated object. Typically, in known burners, the flame temperature is about 1600 F and the exhaust temperature is about 800 F, which indicates that the difference in temperature used to heat the object is only 800 degrees.

[000105] FIGS. 39-42 illustrate a second preferred embodiment of the burner according to the present invention, indicated at 220. The burner 220 according to the second preferred embodiment is similar to the burner 20 according to the first preferred embodiment, but the outer housing element 240 is much larger in that as for the thickness of its walls. In addition, the substantially annular wall 210 in the rear housing element 230 is significantly thicker. Further, the fuel nozzle 250 comprises a tip of the fuel nozzle 260 disposed to be removable and replaceable at the front end 257 of the elongated body 255 of the fuel nozzle 250. Preferably, the threaded portion of the threaded fuel nozzle tip 268 is connected to the corresponding threaded front end portion 259 in the fuel channel 258. The tip of the fuel nozzle 260 is removably and removably fixed as described above to allow easy replacement of the tip of the fuel nozzle 260 in in case of damage, as well as selecting the appropriate tip of the fuel nozzle 260 for a specific application, such as an arrangement in a boiler, track heater or furnace.

[000106] The above descriptions and the accompanying drawings make it clear that according to the present invention, there is provided a fuel nozzle due to which the burner has a very high efficiency when burning fuel, produces a minimum of undesirable emissions, is configured to be used with different types of gaseous and liquid fuels, is cost-effective , and is not disclosed in the prior art in its entirety.

[000107] Other changes to the principles described above are obvious to a person skilled in the art to which the present invention relates, and these changes should be considered as falling within the scope of the present invention. In addition, other modifications and changes are possible to perform in the design and manufacture of the fuel injector according to the present invention without departing from the essence of the attached claims.

[000108]

Claims (28)

1. A burner containing:
housing;
at least one air inlet for air inlet;
mixing chamber;
a fuel channel comprising a fuel inlet for introducing fuel and a fuel outlet for discharging fuel, and for delivering fuel to the mixing chamber;
a first channel for air flow, which contains an inlet in communication with said at least one air inlet, and an outlet located next to the fuel outlet, and which is designed to deliver air to the mixing chamber; and
a substantially annular collection chamber for collecting air in communication with said at least one air inlet, a substantially circular mixing chamber for mixing the air flow, a substantially annular wall substantially separating said collecting chamber and said mixing chamber, a first flow opening air passing between the specified collection chamber and the specified mixing chamber, and having a first height that is part of the height of the specified essentially annular wall. 2. The burner according to claim 1, further comprising a storage chamber for storing air located between said at least one air inlet and said first air flow channel. 3. The burner according to claim 2, in which the cross-sectional area of said air outlet is narrower than the cross-sectional area of the storage chamber. 4. The burner according to claim 1, in which essentially the entire first channel for air flow is directed at an angle with respect to the specified longitudinal axis. 5. The burner according to claim 4, in which the first channel for air flow has a spiral shape. 6. The burner according to claim 1, in which the ratio of the cross-sectional area of the inlet of the first channel for air flow to the cross-sectional area of the outlet of the first channel for air flow is about 1.6 to 1. 7. The burner according to claim 1, in which the cross-sectional area of the first channel for air flow decreases in the direction from the inlet to the outlet. 8. The burner according to claim 7, in which the width of the first channel for air flow decreases in the direction from the inlet to the outlet. 9. The burner of claim 8, in which the depth of the first channel for air flow decreases in the direction from the inlet to the outlet. 10. The burner according to claim 1, additionally containing a fuel nozzle located in the housing and containing said fuel channel, a fuel inlet and a fuel outlet. 11. The burner of claim 10, in which the first channel for air flow is located on the outer part of the fuel nozzle. 12. The burner of claim 10, further comprising a second channel for air flow. 13. The burner of claim 12, wherein the first channel for air flow and the second channel for air flow are substantially parallel to each other. 14. The burner according to item 13, in which the first channel for air flow and the second channel for air flow are spiral. 15. The burner according to 14, in which the cross-sectional area of the specified inlet of the second channel for air flow is greater than the cross-sectional area of the specified outlet of the second channel for air flow. 16. The burner according to clause 15, in which the ratio of the cross-sectional area of the inlet of the first channel for air flow to the cross-sectional area of the outlet of the first channel for air flow is about 1.6 to 1. 17. The burner according to clause 15, in which the cross-sectional area of the first channel for air flow decreases in the direction from the inlet to the outlet. 18. The burner according to 17, in which the width of the first channel for air flow decreases in the direction from the inlet to the outlet. 19. The burner according to claim 18, wherein the depth of the first channel for air flow decreases in the direction from the inlet to the outlet. 20. The burner of claim 12, further comprising a third channel for air flow, a fourth channel for air flow, and a fifth channel for air flow. 21. The burner according to claim 20, in which the first channel for air flow, the second channel for air flow, the third channel for air flow, the fourth channel for air flow and the fifth channel for air flow are essentially parallel to each other. 22. The burner according to item 21, in which the third channel for air flow, the fourth channel for air flow and the fifth channel for air flow are spiral. 23. The burner of claim 10, in which the fuel nozzle has an elongated housing containing an inlet end and an outlet end, wherein the fuel inlet is located at the specified inlet end, and the fuel outlet is located at the specified outlet end. 24. The burner according to item 23, in which the specified elongated housing contains a narrow rear part and a wider front part. 25. The burner according to paragraph 24, in which the specified elongated housing of the fuel injector contains an inclined part connecting the narrow rear part and the wider front part. 26. The burner according A.25, in which the inclined part of the fuel nozzle is hermetically connected to the corresponding receiving surface of the specified housing. 27. The burner according to claim 1, further comprising a second air inlet located in said housing, wherein said at least one channel for spiral-shaped air flow communicates with this second air inlet. 28. The burner according to claim 1, additionally containing a tip of the fuel nozzle installed with the possibility of removal and replacement at the front end of the elongated housing of the fuel nozzle.

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