EP0949453A2 - Plaque de brûleur - Google Patents

Plaque de brûleur Download PDF

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Publication number
EP0949453A2
EP0949453A2 EP99302724A EP99302724A EP0949453A2 EP 0949453 A2 EP0949453 A2 EP 0949453A2 EP 99302724 A EP99302724 A EP 99302724A EP 99302724 A EP99302724 A EP 99302724A EP 0949453 A2 EP0949453 A2 EP 0949453A2
Authority
EP
European Patent Office
Prior art keywords
burner
burner port
ports
excess air
closed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99302724A
Other languages
German (de)
English (en)
Other versions
EP0949453B1 (fr
EP0949453A3 (fr
Inventor
Tsutomu c/o Rinnai Kabushiki Kaisha Sobue
Akio c/o Rinnai Kabushiki Kaisha Tanaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rinnai Corp
Original Assignee
Rinnai Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Rinnai Corp filed Critical Rinnai Corp
Publication of EP0949453A2 publication Critical patent/EP0949453A2/fr
Publication of EP0949453A3 publication Critical patent/EP0949453A3/fr
Application granted granted Critical
Publication of EP0949453B1 publication Critical patent/EP0949453B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/102—Flame diffusing means using perforated plates
    • F23D2203/1023—Flame diffusing means using perforated plates with specific free passage areas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2210/00—Noise abatement

Definitions

  • the present invention relates to a burner plate for use in a gas burner, which has a heat exchanger, for burning a fuel gas in total primary combustion.
  • a mixture of the fuel gas and air added at a predetermined excess air ratio is supplied to a burner plate mounted on a gas burner unit and burned in total primary combustion.
  • the burner plate comprises a heat-resistant plate of ceramics or the like which has a number of burner ports defined therein and extending from a surface of the plate to the opposite surface thereof.
  • a burner plate 3b has a plurality of burner ports 7 divided into a plurality of lozenge-shaped patterns each having burner ports 7 arranged in six rows and six columns as a burner port group 8. Adjacent lozenged burner port groups 8 are spaced from each other by spaces or gaps 9. With the burner plate 3b shown in FIG.
  • the burner plate 3b is effective in limiting flames to an appropriate size and stabilizing them without the danger of being lifted off the burner plate 3b and extinguished.
  • JIS S 2109 provides that the produced amount of carbon monoxide should not exceed a certain reference level, e.g., 0.28 %. Those gas burners should not produce an amount of carbon monoxide in excess of the prescribed reference level during operation.
  • An excess air ratio allowance for a gas burner is determined when the gas burner is designed. If an excess air ratio allowance is too small, then depending on the supplied mixture, an actual excess air ratio may fall out of the excess air ratio allowance due to individual gas burner fabrication errors. When an actual excess air ratio falls out of the excess air ratio allowance, the gas burner may be liable to produce an undue amount of carbon monoxide. For this reason, the excess air ratio allowance should preferably be as large as possible, and may be set to 0.5 or more, for example.
  • the inventors have conducted research activities and found a couple of reasons why carbon monoxide is produced in the total primary combustion even if the excess air ratio is set to a value greater than 1.
  • the first reason is that since the mixture is a dynamic mixture, the excess air ratio may become smaller than 1 in local areas, and incomplete combustion may occur in those local areas. However, the phenomenon in which the excess air ratio becomes smaller than 1 in local areas is less intensive as the excess air ratio becomes greater than 1. Therefore, the produced amount of carbon monoxide becomes smaller as the excess air ratio becomes greater than a value near 1.
  • the second reason is that if the excess air ratio becomes sufficiently greater than 1, the mixture ejected from the burner ports flows at an increased speed and flames tend to contact fins of the heat exchanger. When the flames contact fins of the heat exchanger, the flames are quickly cooled, interrupting the combustive reaction in the flames. As a result, the amount of carbon monoxide which is an intermediate product of the combustive reaction increases.
  • the excess air ratio becomes greater than 1, the produced amount of carbon monoxide becomes smaller for the first reason described above.
  • the excess air ratio reaches a certain value, the reduction in the produced amount of carbon monoxide for the first reason and the increase in the produced amount of carbon monoxide for the second reason are brought into equilibrium, whereupon the produced amount of carbon monoxide is minimized.
  • the excess air ratio exceeds the certain value, the produced amount of carbon monoxide increases for the second reason.
  • FIG. 7 of the accompanying drawings shows a dot-and-dash-line curve representing how the produced amount of carbon monoxide varies with the excess air ratio when the mixture is supplied to the burner plate and burned in the total primary combustion.
  • a range of excess air ratios capable of limiting the produced amount of carbon monoxide to or below a certain reference level, e.g., 0.28 %, is indicated by W 1 .
  • the range W 1 is represented by the difference between an upper limit for excess air ratios for keeping the produced amount of carbon monoxide to or below the reference level and a lower limit for measurable excess air ratios for keeping the produced amount of carbon monoxide to or below the reference level.
  • the compact gas burner described above since flames contact the fins of the heat exchanger upon full-capacity combustion, the produced amount of carbon monoxide with respect to each excess air ratio increases. Specifically, the dot-and-dash-line curve is translated upwardly into a two-dot-and-dash-line curve, reducing the range W 1 of excess air ratios to a range W 2 of excess air ratios. If the range of excess air ratios or the excess air ratio allowance is reduced, then depending on the supplied mixture, an actual excess air ratio may fall out of the excess air ratio allowance due to individual gas burner fabrication errors, tending to produce a large amount of carbon monoxide, as described above.
  • some of the burner ports 7 of the burner port groups 8 may be closed to reduce flames generated by the burner port groups 8. However, if the number of closed burner ports 7 is increased, then the vibrations of flames caused by the combustive reaction in the flames produced from the open burner ports 7 generate combustion resonant sounds in coaction with the natural frequency of the gas burner.
  • a burner plate for use in a gas burner for burning a mixture of a fuel gas and air added at a predetermined excess air ratio in total primary combustion to heat a heat exchanger, comprising a heat-resistant plate having a plurality of burner ports defined therein and extending from a surface of the plate to an opposite surface thereof, the burner ports divided into a plurality of burner port groups which are spaced from each other by gaps, the burner port groups including burner port groups each having in a central area thereof as many burner ports closed as effective to limit an extension of flames produced from the burner port groups and suppress combustion resonant sounds generated by vibrations of the flames in coaction with a natural frequency of the gas burner.
  • the burner ports are divided into a plurality of burner port groups which are spaced from each other by gaps. Flames ejected from the burner ports are combined together in each of the burner port groups, but are prevented from being spread out of each of the burner port groups by the gaps.
  • the burner plate is effective in limiting flames to an appropriate size for combustion.
  • the burner port groups include burner port groups each having burner ports closed in a central area thereof.
  • the closed burner ports are located in the central areas of the certain selected burner port groups, the number of those closed burner ports is limited for thereby preventing combustion resonance sounds from being generated.
  • the closed burner ports are uniformly -distributed over the heat-resistant plate.
  • the closed burner ports preferably constitute 2 through 9 % of the total number of the burner ports on the heat-resistant plate. If the closed burner ports were less than 2 % of the total number of the burner ports, then the excess air ratio allowance capable of reducing the produced amount of carbon monoxide would be reduced. If the closed burner ports were in excess of 9 % of the total number of the burner ports, then the excess air ratio allowance capable of preventing combustion resonance sounds from being generated would be reduced.
  • the burner port groups are arranged in a plurality of burner port group clusters each comprising a plurality of burner port groups, the burner port group clusters being repeated in a predetermined pattern, each of the burner port group clusters including a predetermined number of burner port groups each having a predetermined number of burner ports closed in a central area thereof.
  • the closed burner ports can uniformly be distributed over the heat-resistant plate.
  • each of the burner port groups may comprise 36 burner ports arranged in six rows and six columns in a lozenge-shaped pattern.
  • Each of the burner port group clusters may comprise four lozenged burner port groups arranged in a similarly lozenge-shaped area larger than the lozenged burner port groups, the burner port group clusters being kept in a repeated arrangement.
  • FIG. 1 shows a gas-combusted water heater 1 which burns a mixture of a fuel gas and air added at a predetermined excess air ratio in total primary combustion.
  • the gas-combusted water heater 1 comprises a gas burner 3 housed in a casing 2 and a heat exchanger 5 also housed in the casing 2 for heating water supplied from a water supply pipe 4 with the gas burner 3 thereby to produce hot water.
  • the hot water produced by the heat exchanger 5 is supplied via a hot water supply pipe 6 to various places including a kitchen, a washroom, a bathroom, etc.
  • the gas burner 3 has a burner plate 3a comprising a heat-resistant plate of ceramics such as cordierite or the like which has a number of burner ports 7 defined therein and extending from a surface of the plate to the opposite surface thereof.
  • the gas burner 3 is ignited by an igniting unit (not shown) when a mixture of a fuel gas and air added at a predetermined excess air ratio is supplied to the burner ports 7.
  • FIGS. 2 through 4 show respective different patterns of burner ports 7 for the burner plate 3a.
  • FIG. 5 shows a conventional burner plate 3b
  • FIG. 6 shows a comparative burner plate 3c.
  • the burner plate 3a shown in FIG. 2 has a total of 1269 burner ports 7 each having a diameter of 1.25 mm, defined in a heat-resistance plate having a size of 60 mm x 128 mm. Of the total of 1269 burner ports 7, 2 through 9 % of the burner ports 7 are closed. Two such burner plates 3a are longitudinally juxtaposed to provide a combined burner plate having a size of 60 mm x 256 mm.
  • FIGS. 2 through 6 show portions of the burner plates 3a, 3b, 3c (corresponding to 483 burner ports 7) each having a total of 1269 burner ports 7, for illustrating different patterns of burner ports 7.
  • the burner ports 7 are divided into a plurality of lozenge-shaped patterns each having 36 burner ports 7 arranged in six rows and six columns as a burner port group 8.
  • the centers of adjacent burner ports 7 are spaced 1.8 mm from each other.
  • Adjacent lozenged burner port groups 8 are spaced from each other by spaces or gaps 9.
  • Four lozenged burner port groups 8 are arranged in a similarly lozenge-shaped area larger than the individual lozenged burner port groups 8, making up a burner port group cluster 10.
  • a burner port pattern of the burner plate 3a is formed by a repeated arrangement of burner port group clusters 10.
  • one of the four lozenged burner port groups 8 of each of the burner port group clusters 10 has four central burner ports 7 closed, providing a closed area 7a.
  • the closed burner port percentage of the burner port group clusters 10 on the burner plate 3a shown in FIG. 2 is calculated according to the equation (1) below.
  • the closed burner port percentage is defined as the proportion of closed burner ports 7 in the total number of burner ports 7 which would otherwise be present if no closed burner ports were present.
  • burner port groups 8a, 8b, 8c positioned in peripheral areas make up portions of the larger lozenge-shaped areas.
  • Each of the burner port groups 8a has 15 burner ports 7, each of the burner port groups 8b has 10 burner ports 7, and each of the burner port groups 8c has 4 burner ports 7. Therefore, the actual closed burner port percentage is different from the closed burner port percentage (designed value) calculated according to the equation (1).
  • the actual closed burner port percentage on the burner plate 3a shown in FIG. 2 is expressed by the following equation (2):
  • the burner plate 3a shown in FIG. 3 may be modified such that two of the four lozenged burner port groups 8, whose vertexes confront each other in the horizontal direction, of each of the burner port group clusters 10, or two of the four lozenged burner port groups 8, which are located adjacent to each other across the gap 9, of each of the burner port group clusters 10, may each have four central burner ports 7 closed.
  • three of the four lozenged burner port groups 8 of each of the burner port group clusters 10 each have four central burner ports 7 closed, providing a closed area 7a.
  • the closed burner port percentage of the burner port group clusters 10 on the burner plate 3a shown in FIG. 4 is calculated according to the equation (5) below.
  • the burner plate 3a shown in FIG. 4 may be modified such that any desired three of the four lozenged burner port groups 8 of each of the burner port group clusters 10 may each have four central burner ports 7 closed.
  • the four lozenged burner port groups 8 of each of the burner port group clusters 10 do not have any burner ports 7 closed, and hence do not provide any closed area 7a. Accordingly, the closed burner port percentage which is defined as the proportion of closed burner ports 7 in the total number of burner ports 7 which would otherwise be present if no closed burner ports were present is 0 % in terms of both designed and actual values.
  • burner port groups 8a, 8b, 8c positioned in peripheral areas make up portions of the larger lozenge-shaped areas. Therefore, the actual closed burner port percentage is different from the closed burner port percentage (designed value) calculated according to the equation (7). Specifically, the actual closed burner port percentage on the burner plate 3c shown in FIG. 6 is expressed by the following equation (8):
  • the actual values of the closed burner port percentages of the burner plates 3a, 3b, 3c are different from the designed values thereof.
  • Other types of burner plates also have actual values of the closed burner port percentages.
  • Table 1 indicates that there are no significant differences between the designed values and the actual values. Therefore, no problem occurs in carrying out the present invention no matter which of the designed values and the actual values may be employed.
  • the closed burner port percentages will hereinafter be described in terms of the designed values.
  • the burner plate 3a shown in FIG. 3 was installed in the gas-combusted water heater 1 shown in FIG. 1, and a mixture of a fuel gas and air was supplied to the burner plate 3a for achieving a maximum level of combustion (input: 29.3 kw).
  • the excess air ratio of the mixture was varied, the produced amount of carbon monoxide (%) with respect to the different excess air ratios was measured.
  • the burner plate 3b shown in FIG. 5 was installed in the gas-combusted water heater 1 shown in FIG. 1, and when the excess air ratio of the mixture was varied in the same manner as with the burner plate 3a shown in FIG. 3, the produced amount of carbon monoxide (%) with respect to the different excess air ratios was measured.
  • the burner plate 3c shown in FIG. 6 was installed in the gas-combusted water heater 1 shown in FIG. 1, and when the excess air ratio of the mixture was varied in the same manner as with the burner plate 3a shown in FIG. 3, the produced amount of carbon monoxide (%) with respect to the different excess air ratios was measured.
  • an upper limit for the excess air ratio was determined from Tables 2 through 4.
  • the upper limit was set to a value of the excess air ratio at the time the produced amount of carbon monoxide reached a predetermined reference level of 0.28 %, for example, after it had been increased from the minimum level.
  • the lower limit was subtracted from the upper limit to determine an excess air ratio allowance with which the produced amount of carbon monoxide was not greater than the reference level.
  • an excess air ratio allowance of 0.54 was determined with respect to the burner plate 3a shown in FIG. 3, whose closed burner port percentage was 5.56 %.
  • an excess air ratio allowance of 0.42 was determined with respect to the burner plate 3b shown in FIG. 5, whose closed burner port percentage was 0 %, and an excess air ratio allowance of 0.59 was determined with respect to the burner plate 3c shown in FIG. 6, whose closed burner port percentage was 11.11 %.
  • the excess air ratio allowance is 0.5 or greater when the closed burner port percentage is 2.78 % or greater. As the closed burner port percentage increases, the excess air ratio allowance becomes greater.
  • the excess air ratio allowance should preferably be 0.5 or greater so as to prevent a large amount of carbon monoxide from being generated when the excess air ratio allowance suffers large variations due to individual gas burner product variations.
  • the burner plates 3a, 3b, 3c shown respectively in FIGS. 3, 5, 6 were installed in the gas burner 3 of the gas-combusted water heater 1 shown in FIG. 1, and a mixture of a fuel gas and air was supplied so as to accomplish a maximum level of combustion (input: 29.3 kw).
  • the excess air ratio of the mixture was varied to check whether combustion resonant sounds were produced due to the combustion of mixtures having respective excess air ratios.
  • Upper and lower limits for the excess air ratio with which no combustion resonant sounds are produced were determined. The determined upper and lower limits are shown in Table 6 and FIG. 8. Closed burner port percentage (%) Excess air ratio
  • Upper limit Lower limit FIG. 5 0 1.620 1.050 FIG. 3 5.56 1.615 1.055 FIG. 6 11.11 1.400 1.100
  • the excess air ratio is reduced as the closed burner port percentage is increased.
  • the excess air ratio allowance is less than 0.5 when the closed burner port percentage is 11.11 %. For this reason, the excess air ratio allowance should preferably be set to 0.5 or more.
  • a study of FIG. 9 indicates that when the closed burner port percentage is less than 2 %, the excess air ratio allowance where the produced amount of carbon monoxide is kept to or below the reference level is less than 0.5, and that when the closed burner port percentage exceeds 9 %, the excess air ratio allowance where no combustion resonant sounds are generated is less than 0.5.
  • a plurality of burner ports 7 on each of the burner plates 3a are arranged into a lozenge burner port group 8.
  • a plurality of burner ports 7 may be grouped into any of various shapes including a square shape, an elongate rectangular shape, a circular shape, etc.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
EP19990302724 1998-04-08 1999-04-07 Plaque de brûleur Expired - Lifetime EP0949453B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP9586298 1998-04-08
JP9586298 1998-04-08
JP05256699A JP3695201B2 (ja) 1998-04-08 1999-03-01 燃焼用バーナプレート
JP5256699 1999-03-01

Publications (3)

Publication Number Publication Date
EP0949453A2 true EP0949453A2 (fr) 1999-10-13
EP0949453A3 EP0949453A3 (fr) 2000-02-23
EP0949453B1 EP0949453B1 (fr) 2003-12-10

Family

ID=26393190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19990302724 Expired - Lifetime EP0949453B1 (fr) 1998-04-08 1999-04-07 Plaque de brûleur

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Country Link
EP (1) EP0949453B1 (fr)
JP (1) JP3695201B2 (fr)
DE (1) DE69913414T2 (fr)
ES (1) ES2210978T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1418382A2 (fr) * 2002-11-05 2004-05-12 CRAMER SR s.r.o. Brûleur radiant
EP3514453A1 (fr) * 2018-01-17 2019-07-24 Atag Heating B.V. Plaque de bruleur pour une chaudiere a chauffage central

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5513425B2 (ja) * 2011-03-02 2014-06-04 リンナイ株式会社 燃焼プレート
JP5415497B2 (ja) * 2011-08-30 2014-02-12 リンナイ株式会社 燃焼装置
JP2016084955A (ja) * 2014-10-24 2016-05-19 リンナイ株式会社 燃焼プレート
JP6853075B2 (ja) * 2017-03-13 2021-03-31 リンナイ株式会社 全一次燃焼式バーナ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989001116A1 (fr) * 1987-08-03 1989-02-09 Worgas Bruciatori S.R.L. PROCEDE DE COMBUSTION ET BRULEUR A GAZ A FAIBLE EMISSION DE NOx ET DE CO
JPH01310217A (ja) * 1988-06-09 1989-12-14 Rinnai Corp 燃焼プレート
WO1992001196A1 (fr) * 1990-07-06 1992-01-23 Worgas Bruciatori S.R.L. Procedes et appareil pour la combustion des gaz
WO1993007420A1 (fr) * 1991-10-03 1993-04-15 Nefit Fasto B.V. Procede et installation de combustion d'un melange gazeux

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989001116A1 (fr) * 1987-08-03 1989-02-09 Worgas Bruciatori S.R.L. PROCEDE DE COMBUSTION ET BRULEUR A GAZ A FAIBLE EMISSION DE NOx ET DE CO
JPH01310217A (ja) * 1988-06-09 1989-12-14 Rinnai Corp 燃焼プレート
WO1992001196A1 (fr) * 1990-07-06 1992-01-23 Worgas Bruciatori S.R.L. Procedes et appareil pour la combustion des gaz
WO1993007420A1 (fr) * 1991-10-03 1993-04-15 Nefit Fasto B.V. Procede et installation de combustion d'un melange gazeux

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 014, no. 107 (M-0942), 27 February 1990 (1990-02-27) & JP 01 310217 A (RINNAI CORP), 14 December 1989 (1989-12-14) *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1418382A2 (fr) * 2002-11-05 2004-05-12 CRAMER SR s.r.o. Brûleur radiant
EP1418382A3 (fr) * 2002-11-05 2004-05-26 CRAMER SR s.r.o. Brûleur radiant
EP3514453A1 (fr) * 2018-01-17 2019-07-24 Atag Heating B.V. Plaque de bruleur pour une chaudiere a chauffage central
NL2020282B1 (nl) * 2018-01-17 2019-07-25 Atag Heating B V Branderplaat voor een cv-ketel

Also Published As

Publication number Publication date
DE69913414D1 (de) 2004-01-22
JP3695201B2 (ja) 2005-09-14
ES2210978T3 (es) 2004-07-01
EP0949453B1 (fr) 2003-12-10
EP0949453A3 (fr) 2000-02-23
DE69913414T2 (de) 2004-10-07
JPH11351522A (ja) 1999-12-24

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