A low-nox gas burner

Abstract: A fuel-lean mixture burns in rows of flame ports (b) each located between a pair of rows of flame ports (a) burning a fuel-rich mixture. The fuel-rich flames (8a) support and stabilize the fuel-lean flames (8b) to stabilize combustion and to avoid flame liftoff and noise. The fuel-lean flames reduce the temperature of the overall flame, and thereby reduce the production of No x compounds produced by the burner. Stepwise and proportional burner control techniques are disclosed.

Description: The present invention relates to burners low in the generation of nitrogen oxides used in a small combustion apparatus for domestic or commercial according the pre-characterising part of claim 1 (EP-A-0 331 037). Nitrogen oxides (NO X ) in the exhaust gases from burners of various combustion devices are toxic by themselves and are believed to cause acid ran and photochemical smog. Various measures for decreasing the generation of NO X in burners of combustion apparatus have been developed and utilized. However, this measures are mainly directed to solving the problems of legally regulated large combustion apparatus for industrial and other use. Such measures are not satisfactory for small combustion apparatus for domestic or small commercial use because of noise and/or cost problems. In a large combustion apparatus, the large static pressure produced by the combustion fan permits easy flow control of the combustion gas and air. This permits a high degree of freedom of layout, and easy noise control. So, with easy control of noise, and with large combustion chambers a possibility of slow combustion can be used to decrease NO X emissions while still achieving perfect combustion. These advantages are not available in small combustion devices. It is therefore difficult to attain decreases in NO X emissions comparable to what which are attainable in large combustion systems. It is therefore an object of the present invention to solve the above problem and to expand the control range of heat input, by rationally applying rich-lean combustion to small combustion devices. It is a further object of the invention to provide a small combustion apparatus which decreases the generation of NO X without increasing noise. It is a further object of the invention to provide a small combustion apparatus which permits stepwise control of combustion. It is a still further object of the invention to provide a small combustion apparatus which permits both stepwise and proportional control of combustion. This objects could be obtained by the measures according claim 1. Briefly stated, the present invention as claimed in claim 1 provides a burner in which a fuel-lean mixture burns in rows of flame ports each located between a pair of rows of flame ports burning a fuel-rich mixure. The fuel-rich flames support and stabilize the fuel-lean flames to stabilize combustion and to avoid flame liftoff and noise. The fuel-lean flames reduce the temperature of the overall flame, and thereby reduce the production of NO X compounds produced by the burner. The rows of fuel rich flame ports and the fuel-lean flame ports are positioned so that, when one or more sets fuel gas supply systems are supplying fuel to their respective sets of flame port groups, the two extreme outermost rows of flame ports are fuel rich flame ports. Stepwise and proportional burner control techniques are disclosed. The above, and other objects, features and advantages of the present invention will become apparent from the following description read in conjunction with the accompanying drawings, in which like reference numerals designate the same elements. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view showing flame port section of a burner according to an embodiment of the present invention. Fig. 2 is a systematic illustration conceptually showing the entire constitution of the burner of the present invention. Fig. 3 is an illustrative perspective view showing the constitution of the flame port section in a further embodiment of the burner of the present invention. Fig. 4 is an illustrative sectional view illustrating the combustion rate of the burner of fig. 3. Fig. 5 is an illustrative sectional view showing the constitution of the flame port section in the burner of the present invention. Fig. 6 is an illustrative perspective view showing the constitution of the flame port in the burner of the present invention. Fig. 7 is a diagram showing the NO x concentration generated by the burner of the present invention in comparison with the conventional Bunsen burner. Fig. 8 is an illustration showing the lift limit of the flames of the burner portions or flame port groups supplied with the fuel lean mixture in the burner of the present invention, in comparison with others. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to Figs. 1 and 2, a low-NO x burner according to the present invention employs pluralities of first and second flame port groups A and B. Each flame port group A includes a row of flame ports a. Similarly, each flame port group B includes a row of flame ports b. Flame port groups A and B alternate with each other. The combination of flame port groups A and B make up a flame port section. The flame port groups at both extremes of a flame port section are flame port groups A. A plurality of fuel gas supply systems 2, 3, 3' and 3'' supply fuel gas to the flame port sections. Each of the plurality of fuel gas supply systems 2, 3, 3' and 3'' includes a fuel rich mixture producing means 5a for feeding fuel gas to the first flame port groups A and a fuel lean mixture producing means 5b for feeding fuel gas to the second flame port groups B. The fuel gas supply systems are controlled to establish one of the first flame ports groups A at both extreme ends of its flame port section. Fuel gas supply systems 2 and 3 each have fuel rich mixture producing means 5a corresponding to the first flame port groups A and fuel lean mixture producing means 5b corresponding to the second flame port groups 5B. Valves 4, 4'and 4'' permit independently cutting off the second (lean) fuel gas supply system. With two fuel gas supply systems 2 and 3, fuel gas from both the first and second gas supply systems 2 and 3 feed a rich fuel mixture through the fuel rich mixture producing means 5a to the flame ports a of first flame port groups A. The second flame port groups B receive a lean fuel mixture from fuel gas supply systems 2 and 3 through the fuel lean mixture producing means 5b. The fuel lean mixture exits the respective flame ports b for combustion. The flames 8b in the second flame port groups B produced by the combustion of fuel lean mixture (that is, with a high ratio of air to fuel) are unstable. Thus, unstable burning would result from burning the air rich mixture alone. However, the flames 8a produced by the fuel rich mixture in the first flame port groups A are stable. Since the flames 8b are always adjacent on both their sides to the stable flames 8a produced by the fuel rich mixture in the first flame port groups A, the stable flames 8a act as pilot flames, to stabilize the flames 8b of the air rich mixture. This structure prevents flame lift of flames 8b. In addition, this structure prevents the oscillation of the flames, and thereby reduces noise. The combustion of fuel lean mixture stabilized by the flames 8a alongside the fuel rich mixture flames 8b permits the cooling action of the air rich mixture to keep the temperature of the flames 8b low, thereby decreasing the generation of NO x . The fuel gas supply systems 3, 3' and 3'' may be cut off independently, while leaving the first fuel gas supply system 2 turned on. It will be noted that flame ports a are located at extreme end positions fed by fuel gas supply system 2. This permits controlling the total flame port area stepwise while maintaining low NO x production. Therefore, an adjustable range of heat input can be expanded. Also in the combustion state as above, since each of the flames 8b of the second flame port groups B is adjacent on its both sides to the flames 8a of the first flame port groups A, the stabilizing action of flames 8a on flames 8b caused by the combustion of air rich mixture is not inhibited, and stable combustion of the air rich mixture decreases the generation of NO x . The stabilization of the flames 8b of the second flame port groups B by the flames 8a of the first flame port groups A can be achieved also when there exist three or more fuel gas supply systems 2, 3, 3' and 3'', if a first flame port groups A is located at both ends of every range which it is desired to keep operating while shutting off fuel supply in adjacent fuel gas supply systems. In the embodiment of Fig. 2, four fuel gas supply systems are provided; a first fuel gas supply system 2 has no control valve. Three second fuel gas supply systems 3, 3' and 3'' have respective valves 4, 4' and 4''. Fuel gas for these second fuel gas supply systems 3, 3' and 3'' can be independently cut off by their respective valves 4, 4' and 4''. The flame port section corresponding to the first fuel gas supply system 2, has a first burner portions 1a located at each of its extreme ends. The adjacent flame port section fed by second fuel gas supply system 3, to the right in the drawing, a second burner portions 1b is located at its left end while a first burner portions 1a is located at the right-hand end. Thus, fuel gas supply systems 2 and 3 can be turned on while all of the other fuel gas systems are turned off while still providing a first burner portion 1a at both ends of the operating portions of the burner. Similarly the adjacent flame port section fed by second fuel gas supply system 3', to the left of the drawing, one of the second burner portions 1b is located at the right-hand end while one of the first burner sections 1a is located at the left-hand end. Thus, the flame port section fed by second fuel gas supply system 3' can be turned on with the portion fed by first fuel gas supply system 2, or with the portions fed by first fuel gas supply system 2 and second fuel gas supply system 3. Similarly the flame port section fed by the second fuel gas supply system 3'' can be operated with those fed by fuel gas supply systems 3' and 2, and with those fed by 3', 2 and 3. The burner combinations fed by the following combinations of fuel gas supply systems that can be employed: Fuel gas supply system: 2 2 + 3 2 + 3' 2 + 3 + 3' 2 + 3 + 3' + 3'' As is clear from the preceding, any combination of fuel gas supply systems is permitted as long as the result is a type-a flame at both ends of the active portion of the burner. The respective fuel gas supply systems 2 and 3 supply air-fuel mixtures through the fuel mixture producing means 5 to the respective burner portions 1a and 1b. The air-fuel mixture producing means 5 consist of the fuel rich mixture producing means 5a for supplying a fuel rich mixture to the first burner portions 1a and the fuel lean mixture producing means 5b for supplying a fuel lean mixture to the second burner portions 1b. These air-fuel mixture producing means 5 can be constructed as Bunsen burner or other partially or fully premixed burners. In each of the air-fuel mixture producing means of this example, fuel gas is emitted from nozzle 6 into mixer tube 7, and is mixed with the air drawn into the mixer tube 7 by the flow of gas or by a blower. The mixing ratio fuel gas and air can be adjusted by adjusting the diameter of the bore of nozzle 6. The air-fuel mixture producing means 5 permits easy adjustment of the fuel/air mixture produced by the fuel rich mixture producing means 5a, corresponding to the first burner portions 1a, and the fuel lean mixture producing means 5b corresponding to the second burner portions 1b. In the above construction, if all of valves 4, 4' and 4'' are open, fuel gas is supplied from the first and second fuel gas supply systems 2, 3, 3' and 3'', and through the respective air-fuel mixture producing means 5, air-fuel mixtures are supplied to all the burner portions 1a and 1b for combustion. That is, the fuel gas through the first fuel gas supply system 2 is emitted from the nozzles 6 constituting the air-fuel mixture producing means 5a and 5b corresponding to the burner portions 1a and 1b of the system 2 into the mixer tubes 7 of the respective burner portions and mixed with the air sucked simultaneously, and at the flame port groups A and B, the air-fuel mixtures are emitted from the respective flame ports a and b. In this case, the fuel rich mixture producing means 5a corresponding to the respective first burner portions 1a produce the fuel rich mixture using the above mentioned adjustment, and the fuel lean mixture producing means 5b corresponding to the respective second burner portions 1b produce the fuel lean mixture. Also for the burner portions 1a and 1b corresponding to the second fuel gas supply system 3, the fuel rich mixture is supplied to the first burner portions 1a and the fuel lean mixture is supplied to the second burner portions 1b as described above. For example, the air to fuel ratio for the fuel rich mixture may be adjusted to 1:0.4, and the fuel to air ratio may be adjusted to 1:1.2 or 1:1.4 for the fuel lean mixture. Furthermore, the ratio of the fuel gas quantities supplied to the first and second burner portions 1a and 1b are adjusted to be in a ratio of about 3:7, to ensure that the quantity of fuel gas supplied to the second burner portions 1b is larger than that fed to the first burner portions 1a. The above supply of the air-fuel mixtures form flames 8a by the combustion of the fuel rich mixture in the flame port groups A of all the first burner portions 1a constituting the burner and flames 8b by the combustion of fuel lean mixture in the flame port groups B of the second burner portions 1b, as shown by solid lines and two-dot-dash lines in Fig. 2. The first burner portions 1a and the second burner portions 1b are arranged adjacent to one another alternately, and one each of the first burner portions 1a is positioned at both the ends of the burner. So, each of the flames 8b of the second burner portions 1b has the flames 8a of the first burner portions 1a on both of its sides. The flames 8b of the second burner portions 1b are unstable if they exist alone since they are formed by the combustion of an air rich mixture. However, since the flames 8a of the first burner portions 1a existing on both sides of the flames 8b are stable, they act as pilot flames, thus stabilizing the flames 8b of an air rich mixture. Therefore, the flames 8b of the second burner portions 1b avoid the lift and oscillating combustion characteristic of a fuel lean mixture, thus avoiding the instability and noise usually accompanying the burning of a fuel lean mixture. The combustion of the fuel lean mixture stabilized by the flames 8a of fuel rich mixture results in a combination in which the combustion temperature produced by the combustion of air rich mixture is reduced by the presence of the fuel lean mixture, thereby reducing the generation of NO x . If the valve 4 is closed, to cut off the supply of fuel gas fed through the second fuel gas supply system 3, the flames of the burner portions 1a and 1b fed by the fuel gas supply system 3 are extinguished, and only the burner portions corresponding to the flames shown by solid lines in Fig. 2 continue burning. Then, if the supply of fuel gas through the second fuel gas supply system 3" is also cut off, the flames of the two burner portions 1a and 1b on the left-hand side corresponding to the system 3" are extinguished. In addition, if the supply of fuel gas through the second fuel gas supply system 3' is also cut off, the flames of the four burner portions 1a and 1b corresponding to the system 3' are extinguished. In any case of the above combustion states, since each of the flames 8b of the second burner portions 1b has flames 8a of the first burner portions 1a on its both sides, the flames 8b of the second burner portions 1b are stabilized by the flames 8a of the first burner portions 1a as described before. To ensure such stabilization action, in this example, when the burner portions 1a and 1b fed by the fuel gas supply system 3" are engaged in combustion, the flames of the burners 1a and 1b fed by the fuel gas supply system 3' must remain burning. In this way, the active flame port area engaged can be changed stepwise without inhibiting the action of stabilizing the flames 8b of the second burner portions 1b by the flames 8a of the first burner portions 1a. Therefore, the heat input can be adjusted in a wide range using any known combustion quantity control method such as proportional control. In the example described above, the flame port area can be changed in four steps. It is, of course, possible to provide more or less than four steps of change in the flame port area. In the above example, the fuel gas supply systems 2 and 3 and the corresponding burner portions 1a and 1b only, or the fuel gas supply systems 2 and 3' and the corresponding burner portions 1a and 1b only may be used. In addition to the step-wise control discussed above, proportional control of all active flame ports can be achieved. A proportional control valve 16 and master valves 17, feeding all fuel gas control systems, permit simultaneous proportional control of fuel gas. Such proportional control, combined with the stepwise control described above, provides a complete range of control for heat generation. Referring now to Figs. 3 and 4, a further embodiment of the present invention includes first burner portions 1a that narrow down at their tip portions 9 and that have slit-like flame ports at their tops. Side walls 10 extend above wider lower portions of these burner portions to provide spaces between the side walls 10 and tip portions 9. The second burner portions 1b have ribbons 11 installed at their tips, to form many flame ports b. As best shown in Fig. 4, the tip spout portions 9 of the first burner portions 1a can have flame retention port 12 formed on their sides as required. Referring now to Fig. 5 a burner according to a further embodiment of the invention includes first burner portions 1a have ribbons 13 installed at their tips to form many flame ports a as is done with the second burner portions 1b. Flame retention holes 12 a formed in the ribbons of flame ports a, and flame retention side walls 10 are disposed outside these ribbons spaced therefrom to provide spaces therebetween. In the above-described burner, the generation of noise can be further inhibited by the air-fuel mixture flow guide action at the flame ports a and b formed by the ribbons 11 and 13, in addition to the action as described for the embodiments of Figs. 1 and 2. Furthermore, when retained flames 14 are formed at the first burner portions 1a, not only the flames 8a of the first burner portions themselves but also the flames 8b of the second burner portions 1b can be further stabilized. Referring now to Fig. 6, a ceramic plate 15 having many flame ports a and b formed therein a ceramic plate 15. That is, the ceramic plate 15 has may flame ports formed in straight rows, to form the first and second flame port groups A and B alternately arranged. The flame ports b of the second flame port groups B are smaller in diameter and more in number than the flame ports a of the first flame port groups A. In the illustrated example, each of the second flame port groups B is formed by many small flame ports b arranged in two rows. In the above embodiment, the combustion in flame ports b of the second flame port groups B is of an air rich mixture as described before, and the combustion is divided into many small-diameter flame ports b. This division of the flames into many small flames further reduces the temperature of the flames 8b, thus further decreasing the generation of NO x . Furthermore, since the flames 8b are stabilized by the flames 8a of the fuel rich mixture from the flame ports a of the first flame port groups A, as in the other examples described before, lift and oscillating combustion are inhibited. Fig. 7 shows the NO x emission characteristics of the burner of the embodiment of the present invention shown in Fig. 1. The diagram shows the relation between the air ratio of the burner shown on the abscissa achieved by adjusting the air ratio of the fuel lean mixture, and the quantity of NO x generated by such burning while the air ratio of the fuel rich mixture is set at = 0.4 to 0.7. The indicated air ratio values include the cooling air which may be fed around the burner. The parenthesized air ratio values show the values not including the cooling air. The ratio of the heat input by the fuel lean mixture to the heat input by the fuel rich mixture is 7.5:2.5. From Fig. 7, it can be seen that the burner of the present invention is remarkably lower in the generation of NO x than a conventional general Bunsen burner. Fig. 8 shows the lift limit of the flames by the burner portions or flame port groups supplied with the fuel lean mixture in the present invention, as an example in comparison with others. Symbol A shows the lift limit of the second burner portions 1b achieved when the fuel lean mixture is supplied to the flame ports b of the second burner portions 1b or the flame port groups B without the flame retention by the flames 8a of the fuel rich mixture by the first burner portions 1a or the flame port groups A in the burner of the present invention, and the limit is about 0.7. On the contrary, symbol B shows the lift limit in the conventional general Bunsen burner with a flame retention mechanism. This limit is about 1.3. Symbol C shows the lift limit of the second burner portions 1b when both the first and second burner portions 1a and 1b of the flame port groups A and B are used for combustion in the burner of the present invention. This limit is about 3.0. From the above, it can be seen that the burner of the present invention allows stable combustion of a very air rich mixture compared to the conventional general Bunsen burner and decreases the NO x generated. As described above, in the present invention, since the combustion of a highly air rich mixture (fuel lean mixture), which is unstable in itself, is stabilized by the stable flames produced by the combustion of fuel rich mixture, the combustion of air rich mixture can be stabilized effectively and the generation of NO x can be decreased. Furthermore, since the combustion of an air rich mixture is stabilized, the NO x reduction is accomplished without the generation of noise. Thus, a small combustion apparatus can be made in which the generation of NO x is reduced without increasing noise. Moreover, the flame port area as a whole can be changed stepwise without disturbing the stabilized combustion of air rich mixture, and thus, the adjustable range of heat input can be expanded. Comprising respectively plural first and second flame port groups A and B, each with a row of flame ports a and b, being arranged alternately adjacently to one another, with one each of the first flame port groups A located at both the extreme ends of the arranged first and second flame port groups, to constitute a flame port section; plural fuel gas supply systems 2, 3, 3' and 3'', being provided to supply fuel gas to the flame port section; and each of the plural fuel gas supply systems 2, 3, 3' and 3'', being provided with fuel rich mixture producing means corresponding to the first flame port groups and fuel lean mixture producing means corresponding to the second flame port groups, and being controlled to locate one each of the first flame port groups at both the extreme ends in the range of the flame port section to be supplied with the fuel gas from each of the fuel gas supply systems.

Claims: A burner comprising a plurality of first flame port groups (A), wherein each group (A) includes a first row of flame ports (a), and a plurality of second flame port groups (B), wherein each group (B) includes a second row of flame ports (b), whereby the first and second flame port groups (A, B) are alternately arranged adjacent each other in such a way that at both outermost ends of a structure formed by the first and second flame port groups (A, B) there are located first flame port groups (A) whilst there has been provided at least a first fuel gas supply system (5a) supplying a rich fuel-air mixture to said first flame port groups (A) and at least a second fuel gas supply system (5b) supplying a lean fuel-air mixture to said second flame port groups (B), characterised in that a set of adjacent first and second flame port groups (A, B) of said plurality of flame port groups is feeded by a first set (2) of first and second fuel gas supply systems (5a, 5b) and an adjacent further set of adjacent first and second flame port groups (A, B) of said plurality of flame port groups is feeded by a second set (3) of first and second fuel gas sypply systems (5a, 5b) and means (4) are provided for cutting of one of said sets (3) of first and second fuel gas supply systems (5a, 5b) independently of the other set (2) of first and second fuel gas supply systems (5a, 5b), whereby the arrangement is such that during operation of both said sets of adjacent flame port groups (A, B) as well as during operation of one set of said sets of adjacent flame port groups (A, B) the outermost operative flame port groups are formed by first flame port groups (A). A burner according to claim 1, wherein at least three sets of first and second flame port groups (A, B) are arranged one besides the other, each of said sets of adjacent first and second flame port groups (A, B) is fed by its own set of first and second fuel gas supply systems (5a, 5b), the outermost flame port groups of the middlemost set of first and second flame port groups (A, B) are formed by first flame port groups, the outermost sets of first and second flame port groups (A, B) each include a second flame port group (B) at their end contiguous to said middlemost set of first and second flame port groups (A, B) and a first flame port group (A) at their end remote from said middlemost set of first and second flame port groups, whereby the arrangement is such that only the middlemost set of first and second flame port groups of said three sets can be turned on and further the middlemost set of first and second flame port groups of said three sets can be turned on with one or an other of the further sets of first and second flame port groups of said three sets or with said two further sets of first and second flame port groups of said three sets together. A burner according to claim 1, wherein at least three sets of first and second flame port groups (A, B) are arranged one besides the other, each of said sets of adjacent first and second flame port groups (A, B) is fed by its own set of first and second fuel gas supply systems (5a, 5b), the outermost flame port groups (A, B) of one of the outermost sets of first and second flame port groups (A,B) of said three sets are formed by first flame port groups, the middlemost set of first and second flame port groups (A, B) includes a second flame port group (B) at its end contiguous to said one of the outermost sets of first and second flame port groups (A, B) and a first flame port group (A) at its end remote from said one of the outermost sets of first and second flame port group (A, B), another outermost set of first and second flame port groups (A, B) includes a second flame port groups (A) at its end contiguous to said middlemost set of first and second flame port groups (A, B) and a first flame port group (A) at its end remote from said middlemost set of first and second flame port groups, whereby the arrangement is such that only the said one of the outermost set of first and second flame port groups of said three sets can be turned on and further the said one of the outermost set of first and second flame port groups of said three sets of first and second flame port groups of said three sets can be turned on with the middlemost set of first and second flame port groups of said three sets together and further the said one of the outermost sets of first and second flame port groups of said three sets can be turned on with middlemost set and another outermost set of first and second flame port groups of said three sets together. A burner according to any preceding claim, wherein in association with the sets of first and second gas supply systems (5a, 5b) there has been provided proportionating means (16) for controlling a fuel flow to said sets of first and second gas supply systems (5a, 5b). A burner according any preceding claim, wherein said flame ports (a, b) are associated with means for producing a rich fuel-air mixture and a lean fuel-air mixture respectively, said means comprising a plurality of mixer tubes (7), a plurality of nozzles (6) for injecting fuel into said mixer tubes and means admitting air into said mixer tubes.

Inventors: AKIYAMA SHIGETOSHI, MOCHIZUKI KIMIO, SUGAHARA TATSUYA, TAKAGI TAKAO, AKIYAMA, SHIGETOSHI, MOCHIZUKI, KIMIO, SUGAHARA, TATSUYA, TAKAGI, TAKAO
Applicants: TAKAGI KOGYO KK, TOKYO GAS CO LTD, TAKAGI INDUSTRIES CO., LTD., TOKYO GAS CO., LTD.
Application year: 1992
Main classification: F23D14
IPC codes: F23D14