A burner plate and a method of preventing burning resonance noise

Abstract: A burner plate having a plurality of fire holes (2) between its upper (22) and lower (21) surfaces. The fire holes allow high heat capacity primary burning on the upper surface of the plate. The plate is adapted to vary the time required, across the plate, for a air-fuel gas mixture to pass through the fire holes.

Description: This invention relates to a method of preventing burning resonance noise and a burner plate on which a primary burning is effected with a high heat capacity. In a burner apparatus, a burner plate is provided which has a multitude of fire holes each piercing through its thickness. Burner plates are, for example, shown in documents US-A-4,737,102 and JP-A-63/017,309. In both cases both surfaces of the plate are flat. In US-A-4,737,102 the fire holes are of constant length and are either of a first or a second constant axial cross-section. In the case of JP-A-63/017,309 the fire holes are similar, except that the larger cross-section fire holes have countersinks at one end of a larger bore again. The burner plate is placed between an upper end of an air-fuel passage in which a burner fan is disposed and a burner chamber in which a primary burning is effected with a high heat capacity. An acoustic system is formed which has a certain volume and configuration determined by the burner chamber, the air-fuel passage and an exhaust passage led from the air-fuel passage. The acoustic system has a characteristic frequency, and an acoustic resonance frequency appears to induce a burning resonance noise when a frequency response of a resonance burning heat frequency in the burner chamber has a certain relationship with the characteristic frequency of the acoustic system. The acoustic resonance frequency is induced when a phase of the frequency response of a resonance burning heat frequency is in a superposing relationship with a phase of the characteristic frequency of the acoustic system. Therefore, it is one of the objects of the invention to provide a device for preventing burning resonance noise by effectively altering the frequency characteristics of the burner flames so that the phase of the frequency response of a resonance burning heat frequency is not in a superposing relationship with a phase of the characteristic frequency of the acoustic system. It is also one of the objects of the invention to provide a burner plate which is capable of preventing the burning resonance noise when a primary burning is effected on the burner plate with a high heat capacity. According to one aspect of the present invention, there is provided a burner plate having first and second surfaces, the plate comprising: a plurality of primary burning fire holes passing through the burner plate between said first and second surfaces, said fire holes having, along their lengths, first portions and second, countersink portions; characterised in that the length of at least one of the first and second portions of each of the plurality of said fire holes vary across the width of the burner plate. According to another aspect of the present invention, there is provided a burner plate having first and second surfaces, the plate comprising: a plurality of primary burning fire holes passing through the burner plate between said first and second surfaces; wherein the shapes and/or lengths of said fire holes through the burner plate vary across the width of the burner plate; characterised in that one of said first and second surfaces is concave in shape. As a rule, the burner flame formed in the fire holes is repeatedly elongated and contracted to oscillate periodically due to the change of heating capacity when the volume of the burner flame greatly varies under the influence of combustion and pressure variation of the air-fuel mixture gas passing through the fire holes as shown in Figs. 1a, 1b. However, the arrangement of the fire holes according to either aspect is such that there arises consecutive time difference among the burner flame formed in the fire holes, and the burning heat frequency precedently occurs in the fire holes in which the air-fuel mixture gas passes more quickly, thus making it possible to alter the characteristics of the frequency response on the burner plate effectively. When there are countersinks, the burning heat frequency precedently occurs in the fire holes having shallow countersinks through which the air-fuel mixture gas passes more quickly, and thus making it possible to alter the characteristics of the frequency response on the burner plate effectively. The frequency response of the burning heat frequency provided by the resultant frequency of the burner flames on the entire burner plate repeatedly changes from α-state to β-state and vice versa as shown in Fig. 2a. As a result, a time lag occurs in the increment of the heat generation speed on the entire burner plate as opposed against the case in which the same time period is required for the air-fuel mixture gas to pass through the fire holes irrespective of where the fire holes are located on the burner plate. This makes it possible to lag the phase of the frequency response of the burner heat frequency behind the characteristic frequency wave of the acoustic system, and thus enabling to avoid the resonance with the characteristic frequency wave of the acoustic system. Further, it is possible to cancel the frequency response of the burner heat frequency of the burner flame in α-state with that of the burner flame in β-state so as to decrease the amplitude of the entire frequency response of the burner heat frequency. However, in the burner plate in which the passage time needed for the air-fuel mixture to pass the fire holes is altered only by randomly changing the diameter of the fire holes, the time lag of the oscillating wave based on different passage time is cancelled between the neighbouring flames. This makes it impossible to effect the state change in the frequency response of the burner heat frequency of the burner flame on the entire burner plate, thus negating an effective prevention of the resonance as shown in Fig. 2b. These and other objects, aspect and embodiments of the invention will be described in more detail with reference to the following drawing figures, of which: Fig. 1a is an explanatory view how burner flames is repeatedly elongated and contracted on a burner plate; Fig. 1b is an explanatory view how the oscillating wave occurs on the burner plate by the repeated elongation and contraction of the burner flames in the prior art; Fig. 2a is an explanatory view how oscillating wave occurs by the burner flames on the burner plate; Fig. 2b is an explanatory view how oscillating wave occurs by the burner flames on the burner plate in the prior art; Fig. 3a is a plan view of a burner plate which is not in accordance with the invention; Fig. 3b is a longitudinal cross sectional view taken along the line A1-A1 of Fig. 3a; Fig. 4a is a plan view of another burner plant which is not in accordance with the invention; Fig. 4b is a longitudinal cross sectional view taken along the line B1-B1 of Fig. 4a; Fig. 5a is a plan view of a burner plate according to a first embodiment of the invention; Fig. 5b is a longitudinal cross sectional view taken along the line C1-C1 of Fig. 5a; Fig. 6a is a plan view of a burner plate according to a second embodiment of the invention; Fig. 6b is a longitudinal cross sectional view taken along the line D1-D1 of Fig. 6a; Fig. 7a is a plan view of a burner plate according to a third embodiment of the invention; Fig. 7b is a longitudinal cross sectional view taken along the line E1-E1 of Fig. 7a; Fig. 8a is a plan view of a burner plate according to afourthembodiment of the invention; Fig. 8b is a longitudinal cross sectional view taken along the line F1-F1 of Fig. 8a; Fig. 9a is a plan view of a burner plate according to a fifth embodiment of the invention; Fig. 9b is a longitudinal cross sectional view taken along the line G1-G1 of Fig. 9a; Fig. 10a is a plan view of a burner plate according to a sixth embodiment of the invention; Fig. 10b is a longitudinal cross sectional view taken along the line H1-H1 of Fig. 10a; Fig. 11a is a plan view of a burner plate according to a seventh embodiment of the invention; Fig. 11b is a longitudinal cross sectional view taken along the line I1-I1 of Fig. 11a; Fig. 12a is a plan view of a burner plate according to an eighth embodiment of the invention; Fig. 12b is a longitudinal cross sectional view taken along the line J1-J1 of Fig. 12a; Fig. 13 is a longitudinal cross sectional view of a water heating apparatus into which the burner plate is incorporated; Fig. 14a is a plan view of a burner plate according to a ninth embodiment of the invention; Fig. 14b is a longitudinal cross sectional view taken along the line K1-K1 of Fig. 14a; Fig. 15a is a region in which a resonance occurs in a graph showing a relationship between a calorific input and revolution of a blower fan when the burner is incorporated into the water heating apparatus; Fig. 15b is a region in which a resonance occurs in a graph showing a relationship between a calorific input and revolution of a blower fan when the prior art burner is incorporated into the water heating apparatus; Fig. 16a is a plan view of a burner plate according to a tenth embodiment of the invention; Fig. 16b is a longitudinal cross sectional view taken along the line L1-L1 of Fig. 16a when a concave envelope curve is formed by connecting bottoms of countersinks provided in fire holes; and Fig. 16c is a view similar to Fig. 16b according to a modified form of the tenth embodiment of the invention when a V-shaped envelope is formed by connecting the bottoms of the countersinks provided in the fire holes. The Figures show a number of different burner plates. Each of the burner plates is made of heat-resistant ceramic material, and incorporated into a water heating apparatus U to effect an entire primary burning with a high calorific capacity as shown in Fig. 13. The water heating apparatus U has a burner chamber 102 in which a heat exchanger 101 is placed to produce a compact structure as a whole. The water heating apparatus U is such space-saving that it is usually installed under the kichen bay window, the eaves, the veranda or the like. In the water heating apparatus U, a blower 103 forces an air-fuel mixture gas into a mixing room 104 located upstream of the burner plate A (B∼J). The air-fuel mixture gas burns in the burner chamber 102 located downstream of the burner plate A (B∼J) on which burner flames are built to heat water flowing through the heat exchanger 101 so as to substantially always supply about 60 °C hot water irrespective of an amount of flowing water (2.9 ∼ 10.9 l/min). In this instance, an amount of calorific input changes within the range from 6000 kcal to 30000 kcal, and a burner control device 105 controls an proportional valve 106 and the blower 103 so that an amount of gas and air is appropriate to the calorific input. It is noted that in addition artificially synthesized fuel, the gas may categorically include all the fossil fuel such as liquefied natural gas, kerosine, heavy and light oil. Burner plate A measures 92 mm × 140 mm and 13 ∼ 23 mm in thickness as shown in Figs. 3a, 3b. The burner plate A has a convex-shaped configuration at its upper surface 22, and having a multitude of lattice-like fire holes 2 each piercing through its thichness. Each of the fire holes 2 measures 1.9 mm in diameter and 4 mm in center-to-center distance. In an outer periphery of the burner plate A, the upper surface 22 is in parallel with a lower surface 21 to be readily installed in the burner chamber 102. Figs. 4a, 4b show another burner plate B which has convex configuration at its lower surface 21 which is diametrically opposed to the burner plate of Figs. 3a, 3b. Figs. 5a, 5b show the first embodiment of the invention in which the burner plate C has a countersink 20 provided on the upper surface 22 of the fire holes 2 of the burner plate A. It is noted that the countersink 20 measures 4.5 mm in diameter and 1.5 mm in depth. The provision of the countersink 20 makes it possible to slow the air-fuel mixture gas flowing through the fire holes 2 so as to stabilize the flames on the burner plate. Figs. 6a, 6b show the second embodiment of the invention in which the burner plate D measures 92 mm × 140 mm and 13 ∼ 23 mm in thickness in the same manner as described in Figs. 3a, 3b. The burner plate D has a flat upper surface 22 and the concave lower surface 21, a thickness of which progressively increases from a central portion 21p toward an outer periphery 21q. The burner plate D has the lattice-like fire holes 2, each of which measures 1.7 mm in diameter and 3 mm in center-to-center distance. In an outer periphery of the burner plate D, the upper surface 22 is in parallel with a lower surface 21 to be readily installed in the burner chamber 102. Figs. 7a, 7b show the third embodiment of the invention in which the burner plate E has concave configuration at its upper surface 22 as diametrically opposed to the fourth embodiment of the invention. At least some of the embodiments of the invention have advantages as described below. The thickness of the burner plate progressively increases or reduces from a central portion toward an outer periphery of the burner plate. This makes it possible to change the time period needed for the air-fuel mixture gas to pass through the fire holes depending on what part of the burner plate the fire holes are placed. In this instance, the burning heat frequency precedently occurs in the fire holes provided on a thinner portion of the burner plate through which the air-fuel mixture gas passes more quickly, and thus making it possible to effectively alter the characteristics of the frequency response on the burner plate. The frequency response of the burning heat frequency provided by the resultant frequency of the burner flames on the entire burner plate repeatedly changes from α-state to β-state and vice versa as shown in Fig. 2a. As a result, a time lag occures in the increment of the heat generation speed on the entire burner plate as opposed against the case in which the same time period is required for the air-fuel mixture gas to pass through the fire holes irrespective of where the fire holes are located on the burner plate. This makes it possible to lag the phase of the frequency response of the burner heat frequency behind the characteristic frequency wave of the acoustic system, and thus enabling to avoid the resonance with the characteristic frequency wave of the acoustic system. Further, it is possible to cancel the frequency response of the burner heat frequency of the burner flame in α-state with that of the burner flame in β-state so as to decrease the amplitude of the entire frequency response of the burner heat frequency. The reduced amplitude of frequency response makes it possible to decrease the burning resonance noise to effect a low noise operation of the water heating apparatus U which does not disturbe people in home or next door. Figs. 8a, 8b show the fourth embodiment of the invention in which the flat type burner plate F is provided which measures 92 mm × 140 mm and 13 mm in thickness. The burner plate F has a multitude of lattice-like fire holes 2 each piercing through its thichness. Each of the fire holes 2 measures 1.9 mm in diameter and 4 mm in center-to-center distance. The burner plate F has the countersink 20 provided on the upper surface 22 of the fire holes 2 of the burner plate F. The countersink 20 measures 4.5 mm in diameter and 1.5 ∼ 3.5 mm in depth. The depth of the countersink 20 progressively decreases from the central portion 21p to the outer periphery 21q so as to form a concave envelope curve provided by connecting each bottom end of the countersinks. It is noted that the bottom ends of countersinks may be made so that they form a V-shaped envelope. Figs. 9a, 9b show the fifth embodiment of the invention in which the arcuate burner plate G is provided with the upper and lower surfaces 22, 21 upwardly curved respectively. The burner plate G measures 92 mm × 140 mm and 13 mm in thickness. The burner plate G has a multitude of lattice-like fire holes 2 each piercing through its thichness. Each of the fire holes 2 measures 1.9 mm in diameter and 4 mm in center-to-center distance. The burner plate G has the countersink 20 provided on the upper surface 22 of the fire holes 2 of the burner plate G. The countersink 20 measures 4.5 mm in diameter and 1.5 ∼ 3.5 mm in depth. The depth of the countersink 20 progressively decreases from the central portion 21p to the outer periphery 21q. In an outer periphery of the burner plate G, a periphery 221 of the upper surface 22 is in horizontal relationship with a periphery 211 of the lower surface 21 to be readily installed in the burner chamber 102. Figs. 10a, 10b show the sixth embodiment of the invention in which the arcuate burner plate H is provided with the upper and lower surfaces 22, 21 downwadly curved respectively The burner plate G measures 92 mm × 140 mm and 13 mm in thickness. The burner plate H has a multitude of lattice-like fire holes 2 each piercing through its thichness. Each of the fire holes 2 measures 1.9 mm in diameter and 4 mm in center-to-center distance. The burner plate G has the countersink 20 provided on the upper surface 22 of the fire holes 2 of the burner plate G. The countersink 20 measures 4.5 mm in diameter and 1.5 ∼ 3.5 mm in depth. The depth of the countersink 20 progressively decreases from the central portion 21p to the outer periphery 21q so as to form a concave envelope curve provided by connecting each bottom end of the countersinks. In an outer periphery of the burner plate H, the periphery 221 of the upper surface 22 is in horizontal relationship with the periphery 211 of the lower surface 21 to be readily installed in the burner chamber 102. It is noted that the bottom ends of countersinks may be made so that they form a V-shaped envelope. Incidentally, the time period (t) required for the air-fuel mixture gas to pass through the fire holes 2 is determined as follows: t = (L1/V1)+(L2/V2) Where L1 = a dimensional difference between the thickness of the burner plate (F∼H) and the depth of the countersink 20 in the fire holes 2, L2 = the depth of the countersink 20, V1 = velocity of the air-fuel mixture gas passing through a portion of the fire hole except for the countersink 20, V2 = velocity of the air-fuel mixture gas passing through the coutersink 20. Since the former velocity is greater than the latter velocity (V1 > V2), the air-fuel mixture gas pass through the fire holes more quickly as the depth L1 increases with the decrease of the depth L2. In the burner plate (F∼H), the countersink 20 is provided in the fire holes 2, and the depth of the countersink 20 is progressively decreases toward the outer periphery 21q of the burner plate. This makes it possible to change the time period needed for the air-fuel mixture gas to pass through the fire holes depending on what part of the burner plate the fire holes are placed. In this instance, the burning heat frequency precedently occurs in the fire holes having shorter countersink through which the air-fuel mixture gas passes more quickly, and thus making it possible to effectively alter the characteristics of the frequency response on the burner plate. For this reason, the frequency response of the burning heat frequency provided by the resultant frequency of the burner flames on the entire burner plate repeatedly changes from α-state to β-state and vice versa as shown in Fig. 2a. As a result, a time lag occures in the increment of the heat generation speed on the entire burner plate as opposed against the case in which the same time period is required for the air-fuel mixture gas to pass through the fire holes irrespective of where the fire holes are located on the burner plate. This makes it possible to lag the phase of the frequency response of the burner heat frequency behind the characteristic frequency wave of the acoustic system, and thus enabling to avoid the resonance with the characteristic frequency wave of the acoustic system. Further, it is possible to cancel the frequency response of the burner heat frequency of the burner flame in α-state with that of the burner flame in β-state so as to decrease the amplitude of the entire frequency response of the burner heat frequency. The reduced amplitude of frequency response makes it possible to decrease the burning resonance noise to effect a low noise operation of the water heating apparatus U which does not disturbe people in home or next door. It is observed that the depth of the countersink of the fire holes may progressively increase from the central portion toward the outer periphery of the burner plate. Figs. 11a, 11b show the seventh embodiment of the invention in which the burner plate I is generally identical to the plate burner A except for the provision of the countersink 20. The countersink 20 is provided in the fire holes 2 in the upper side 22 of the burner plate I. The depth of the countersink 20 ranges from 1.5 mm to 3.5 mm, and progressively decreases from the central portion 21p toward the outer periphery 21q of the burner plate I. It is noted that the depth of the countersink may be arranged so that a V-shaped envelope is formed by connecting the bottom ends of the countersink respectively. Figs. 12a, 12b show the eighth embodiment of the invention in which the burner plate J is generally identical to the plate burner A except for the provision of the countersink 20. The countersink 20 is provided in the fire holes 2 in the upper side 22 of the burner plate I. The depth of the countersink 20 ranges from 1.5 mm to 3.5 mm, and progressively decreases from the central portion 21p toward the outer periphery 21q of the burner plate J. According to the seventh and eighth embodiments of the invention, the thickness of the burner plates I, J is progressively decreases from the central portion toward the outer periphery of the burner plates, and the depth of the countersink progressively decreases from the central portion toward the outer periphery. This makes it possible to change the time period needed for the air-fuel mixture gas to pass through the fire holes depending on what part of the burner plate the fire holes are located. In this instance, the burning heat frequency precedently occurs in the fire holes which are placed in the thickness-reduced portion of the burner plate, and having shorter countersink through which the air-fuel mixture gas passes more quickly, and thus making it possible to effectively alter the characteristics of the frequency response on the burner plate. It is observed that the thickness of the burner plate and the depth of the fire holes are simultaneously arranged such that the time lag is readily provided among the flames built on the fire holes of burner plate. It is also observed that the thickness of the burner plate may progressively increase from the central portion toward the periphery, while the depth of the countersink may progressively increase from the central portion toward the periphery. Figs. 14a, 14b show a ninth embodiment of the invention in which a burner plate L is provided. Figs. 16a, 16b show a tenth embodiment of the invention in which a burner plate K is provided. The burner plates L, K are in turn incorporated into the water heating appratus U as shown in Fig. 13. The burner plate K measures 92 mm × 140 mm and 16 ∼ 25 mm in thickness as shown in Figs. 3a, 3b. The burner plate K has a convex-shaped configuration at its upper surface 22, and alternately having two rows (x), (y) of primary and secondary fire holes 2, 3 with regular intervals (8mm). The primary fire holes 2 have 1.9 mm in diameter, and the secondary fire holes 2 have 1.7 mm in diameter. Countersinks 23, 31 are in turn provided in the row of the primary and secondary fire holes 2, 3. The countersink 23 is 4.5 mm in diamter and 1.5 mm in depth, while the countersink 31 is 4.5 mm in diameter and 3.5 mm in depth. On the burner plate K, a multitude of tiny fire holes 4, 5 (1.3 mm, 0.9 mm in dia.) are provided, part of which are located to surround the countersinks 23, 31. With the fire holes 2, 3, 4 and 5 of different diameter provided on the burner plate, they play a role of stabilizing the flames built on the burner plate in the range from a low heating capacity region to a high heating capacity region. The countersinks 23, 31 contributes to reducing the velocity of the air-fuel gas passing through the fire holes so as to stabilize the flames on the burner plate. With two rows (x), (y) of primary and secondary fire holes 2, 3 alternately provided on the burner plate, the frequency response of the burning heat oscillation in α-state flame and the frequency response of the burning heat oscillation in β-state flame in turn occur. However, the two responses are cancelled each other so as to be advantageous in preventing the resonance noise. Figs. 15a, 15b show graphs each depicting a relationship between an amount of calorific input and revolution of the blower fan. The resonance noise occurs in the region as depicted by the hatched lines in Fig. 15a when the prior burner plate is incorporated into the water heating apparatus U. On the contrary, the water heating apparatus U remains substantially immune to the resonance noise in a good burning region 63 surrounded by an unburnable-limit line 61 and flame lift-limit line 62 as shown in Fig. 15b when the burner plate (A∼K) is incorporated into the water heating apparatus U. Returning back to the flat type burner plate L of the tenth embodiment of the invention, the flat type burner plate L measures 92 mm × 140 mm, and 16 mm in depth. Many a row of the secondary fire holes 3 (1.7 mm in dia.) are provided in the flat burner plate L with regular intervals (8mm). In each row of the secondary fire holes 3, countersink 32 is provided such that its depth progressively decreases from the central portion 21p toward the outer periphery 21q of the burner plate L. Such is the depth of the countersink 32 that a convex envelope curve is formed by in trun connecting the bottom end of the countersink 32 in the fire holes 3 as shown in Fig. 16b. It is noted that the depth of the countersink 32 may be arranged so that the envelope forms a V-shaped configuration as shown at M in Fig. 16c as a modification of the tenth embodiment of the invention. It is found that the water heating apparatus U remains substantially immune to the resonance noise as the case with the burner plate K when the burner plate L is incorporated into the water heating apparatus U. It is noted that the invention is applied to not only the water heating apparatus but also an air conditioner, gas grill, clothes dryer and the like. It is also noted that the diameter and interval of the fire holes, the depth and diameter of the countersink and the thickness of the burner plate are appropriately arranged as required upon putting it into practical use. It is appreciated that the countersink may be provided in all the fire holes, or otherwise it may be partly provided in the fire holes. It is further appreciated that the thickness of the burner plate and the depth of the countersink may be longitudinally and latitudinally changed from the central portion toward the outer periphery of the burner plate.

Claims: A burner plate (C,F-L) having first and second surfaces (21,22), the plate comprising: a plurality of primary burning fire holes (2-3) passing through the burner plate (C,F-L) between said first and second surfaces (21,22), said fire holes (2,3) having, along their lengths, first portions and second, countersink portions (20,23,31,32); characterised in that the lengths of at least one of the first and second portions (20,23,31,32) of each of the plurality of said fire holes (2,3) vary across the width of the burner plate (C,F-L). A plate according to claim 1, wherein the lengths of the first portions are the same across the width of the burner plate (C,F-L) and the lengths of the second portions (20,23,31,32) vary progressively across the width of the burner plate. A plate according to claim 1, wherein the lengths of the second sections (20,23,31,32) are the same across the width of the burner plate (C,F-L) and the lengths of the first portions vary progressively across the width of the burner plate. A plate according to claim 3, wherein said lengths of said second portions (20,23,31,32) progressively increase or decrease according to their spacing from a central portion of the plate. A plate according to any one of the preceding claims, wherein the axial cross-sections of the first and/or second portions are constant. A plate according to claim 5, wherein any first portions having constant axial cross-sections have the same first constant axial cross-sections and any second portions having constant axial cross-sections have the same second constant axial cross-sections. A plate according to any one of the preceding claims, wherein at least one of said first and second surfaces (21,22) is non-planar. A plate according to claim 7, wherein at least one of said first and second surfaces (21,22) is curved in at least one plane. A plate according to claim 7 or 8 when dependent on claim 3 or claim 4, wherein the lengths of said second portions (20,23,31,32) vary in accordance with the shaping of said at least one non-planar surface. A burner plate (D,E,G,H) having first and second surfaces (21,22), the plate comprising: a plurality of primary burning fire holes (2,3) passing through the burner plate (D,E,G,H) between said first and second surfaces (21,22); wherein the shapes and/or lengths of said fire holes (2,3) through the burner plate vary across the width of the burner plate; characterised in that one of said first and second surfaces (21,22) is concave in shape. A plate according to any one of claims 7 to 10, wherein the thickness of the plate in the elongate direction of the holes (2,3) progressively increases or decreases towards the edges of the plate from a central portion of the plate. A plate according to any one of the preceding claims, wherein the cross-sectional shapes and/or lengths of said fire holes (2,3) are the same for fire holes (2,3) equidistant from a certain point on said plate. A plate according to any one of the preceding claims, further comprising a plurality of secondary burning fire holes (4,5) of constant axial cross-section along their lengths, passing through the burner plate between said first and second surfaces (21,22). A burner having a burner plate according to any one of the preceding claims.

Inventors: ISHIKAWA HIDEAKI, JINNO HIDEYUKI, ISHIKAWA, HIDEAKI, JINNO, HIDEYUKI
Applicants: RINNAI KK, RINNAI KABUSHIKI KAISHA
Application year: 1993
Main classification: F23D14
IPC codes: F23J13, F23D14, F23L1