JP2013120014A - Combustion device - Google Patents

Combustion device Download PDF

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JP2013120014A
JP2013120014A JP2011268243A JP2011268243A JP2013120014A JP 2013120014 A JP2013120014 A JP 2013120014A JP 2011268243 A JP2011268243 A JP 2011268243A JP 2011268243 A JP2011268243 A JP 2011268243A JP 2013120014 A JP2013120014 A JP 2013120014A
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exhaust
combustion
hood
heat exchanger
exhaust port
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JP5421981B2 (en
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Takuji Koshiro
卓史 小代
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Rinnai Corp
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Rinnai Corp
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Priority to JP2011268243A priority Critical patent/JP5421981B2/en
Priority to CN201210517551.6A priority patent/CN103148492B/en
Priority to KR1020120141250A priority patent/KR101373451B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J13/00—Fittings for chimneys or flues 
    • F23J13/02—Linings; Jackets; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L17/00—Inducing draught; Tops for chimneys or ventilating shafts; Terminals for flues
    • F23L17/02—Tops for chimneys or ventilating shafts; Terminals for flues
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
    • F23M9/003—Baffles or deflectors for air or combustion products; Flame shields in flue gas ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2213/00—Chimneys or flues
    • F23J2213/10—Linings

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Fluid Heaters (AREA)
  • Housings, Intake/Discharge, And Installation Of Fluid Heaters (AREA)
  • Chimneys And Flues (AREA)

Abstract

PROBLEM TO BE SOLVED: To reduce Helmholtz resonance noise in addition to fan noise in a combustion device which includes a combustion chassis with a built-in burner, a fan supplying combustion air into the combustion chassis, a heat exchanger disposed above the combustion chassis, and an exhaust hood disposed above the heat exchanger to discharge combustion exhaust air through a cylindrical exhaust port extending upward from an upper wall portion of the exhaust hood, and further includes an exhaust limiting cylinder inserted to the exhaust port from under.SOLUTION: A cylindrical portion 65 raised upward is formed on the outer periphery of an annular flange 64 extended radially outside from the lower end of the exhaust limiting cylinder 63, and the upper end of the cylindrical portion 65 is fixed to the opening edge of the exhaust port 61 in the upper wall portion of the exhaust hood 6. The cylindrical portion 65 includes a plurality of ventilation holes 66 for passing the combustion exhaust air which are formed therein at circumferential intervals.

Description

本発明は、バーナを内蔵する燃焼筐と、燃焼筐内に燃焼用空気を供給するファンと、燃焼筐の上方に配置され、バーナの燃焼排気で加熱される熱交換器とを備える給湯用熱源機等の燃焼装置に関する。   The present invention relates to a heat source for hot water supply comprising a combustion housing incorporating a burner, a fan for supplying combustion air into the combustion housing, and a heat exchanger disposed above the combustion housing and heated by the combustion exhaust of the burner. The present invention relates to a combustion apparatus such as a machine.

従来、この種の燃焼装置は、熱交換器の上方に配置され、熱交換器を通過した燃焼排気が流入する排気フードを備え、排気フードの上壁部から上方にのびる筒状の排気口とこれに接続する排気筒とを介して燃焼排気が外部に排出されるようにしている。   Conventionally, this type of combustion apparatus includes an exhaust hood that is disposed above a heat exchanger, into which combustion exhaust gas that has passed through the heat exchanger flows, and has a cylindrical exhaust port extending upward from the upper wall portion of the exhaust hood. Combustion exhaust is discharged to the outside through an exhaust pipe connected to the exhaust pipe.

ところで、上記の如き燃焼筐、熱交換器及び排気フードを備える燃焼装置では、ヘルムホルツ型の共鳴を生ずる。その共鳴周波数ｆは、燃焼筐から排気フードまでの内容積をＶ、排気通路の断面積をＳ、排気通路の通路長をＬ、音速をＣとして、
ｆ＝(Ｃ／２π){Ｓ／(Ｖ・Ｌ)}１／２…(１)
になる。そして、共鳴周波数がバーナの燃焼振動の周波数に近いと、共鳴による騒音を生ずる。従って、騒音を低減するには、共鳴周波数を燃焼振動周波数からずらすことが必要になる。 By the way, in the combustion apparatus provided with the combustion casing, the heat exchanger, and the exhaust hood as described above, Helmholtz-type resonance occurs. The resonance frequency f is as follows: V is the internal volume from the combustion housing to the exhaust hood, S is the cross-sectional area of the exhaust passage, L is the passage length of the exhaust passage, and C is the speed of sound.
f = (C / 2π) {S / (V · L)} 1/2 (1)
become. When the resonance frequency is close to the combustion vibration frequency of the burner, noise due to resonance is generated. Therefore, to reduce noise, it is necessary to shift the resonance frequency from the combustion vibration frequency.

この場合、排気口の断面積を小さくして、共鳴周波数を燃焼振動周波数より小さくすることが考えられる。然し、これでは、排気口に接続する排気筒が小径のものになってしまう。そのため、排気筒における燃焼排気の通過抵抗が過大になって、所要量の燃焼用空気を供給するのに必要なファンの回転数が高くなり、ファン騒音が大きくなってしまう。   In this case, it is conceivable to reduce the cross-sectional area of the exhaust port so that the resonance frequency is lower than the combustion vibration frequency. However, in this case, the exhaust pipe connected to the exhaust port has a small diameter. As a result, the passage resistance of the combustion exhaust in the exhaust stack becomes excessive, the number of fan rotations required to supply the required amount of combustion air increases, and fan noise increases.

そこで、従来、特許文献１により、排気フード内に、排気口の下方に位置させて、排気口の断面積よりも広面積の邪魔板を設け、邪魔板と排気フードの上壁部下面との間に、燃焼排気を排気口に導く通気間隙を形成した燃焼装置が知られている。このものでは、熱交換器を通過した燃焼排気の排気口への直接的な流れが邪魔板によって阻止され、燃焼排気は上記通気間隙を経由して排気口に流れることになる。そして、通気間隙が音響的な抵抗になって、上記（１）式の排気通路長Ｌを長くしたのと同等の効果が得られ、排気口の断面積を小さくしなくても、共鳴周波数を燃焼振動周波数より小さくして、ヘルムホルツ型の共鳴騒音を低減することができる。   Therefore, conventionally, according to Patent Document 1, a baffle plate having a larger area than the cross-sectional area of the exhaust port is provided in the exhaust hood below the exhaust port, and the baffle plate and the lower surface of the upper wall portion of the exhaust hood There is known a combustion apparatus in which a ventilation gap for guiding combustion exhaust gas to an exhaust port is formed therebetween. In this case, the direct flow of the combustion exhaust gas that has passed through the heat exchanger to the exhaust port is blocked by the baffle plate, and the combustion exhaust gas flows to the exhaust port through the ventilation gap. Then, the ventilation gap becomes an acoustic resistance, and the same effect as that obtained by increasing the exhaust passage length L in the above formula (1) can be obtained. The resonance frequency can be reduced without reducing the cross-sectional area of the exhaust port. The Helmholtz type resonance noise can be reduced by making the frequency lower than the combustion vibration frequency.

然し、このものでは、全ての燃焼排気が通気間隙を流れることから、燃焼排気の通過抵抗が十分に小さくならず、ファン回転数を比較的高くせざるを得なくなる。従って、このものでも、ファン騒音を低減することは困難である。   However, in this case, since all the combustion exhaust gas flows through the ventilation gap, the passage resistance of the combustion exhaust gas is not sufficiently reduced, and the rotational speed of the fan has to be made relatively high. Therefore, even with this, it is difficult to reduce fan noise.

また、従来、排気口に下方から挿入される、排気口よりも小径の排気制限筒を備える燃焼装置も市販されている。排気制限筒は、その下端から径方向外方にのびる環状のフランジ部を有しており、このフランジ部を排気フードの上壁部の排気口の開口縁部に固定して、燃焼排気が排気制限筒を介して排気口に流れるようにしている。このものでは、排気制限筒により上記（１）式の排気通路断面積Ｓを小さくしたのと同等の効果が得られ、排気口の断面積を小さくしなくても、共鳴周波数を燃焼振動周波数より小さくして、ヘルムホルツ型の共鳴騒音を低減することができる。   Conventionally, a combustion apparatus including an exhaust restriction cylinder having a smaller diameter than the exhaust port, which is inserted into the exhaust port from below, is also commercially available. The exhaust restriction cylinder has an annular flange portion extending radially outward from the lower end thereof, and the flange portion is fixed to the opening edge of the exhaust port of the upper wall portion of the exhaust hood so that the combustion exhaust gas is exhausted. It is made to flow to an exhaust port through a restriction cylinder. In this case, the same effect as that obtained by reducing the exhaust passage cross-sectional area S of the above equation (1) by the exhaust restriction cylinder can be obtained, and the resonance frequency can be made higher than the combustion vibration frequency without reducing the cross-sectional area of the exhaust port. It is possible to reduce the Helmholtz type resonance noise.

然し、排気制限筒の断面積をかなり小さくしないと、上述した効果が得られない。そのため、このものでも、燃焼排気の通過抵抗を十分に小さくすることはできず、ファン騒音を低減することは困難である。   However, the above-described effects cannot be obtained unless the cross-sectional area of the exhaust restriction cylinder is significantly reduced. Therefore, even with this, the passage resistance of combustion exhaust gas cannot be made sufficiently small, and it is difficult to reduce fan noise.

特開２００７−３１７５号公報JP 2007-3175 A

本発明は、以上の点に鑑み、排気制限筒を備える燃焼装置を改良し、ファン騒音を低減して、且つ、ヘルムホルツ型の共鳴騒音も低減できるようにした燃焼装置を提供することをその課題としている。   SUMMARY OF THE INVENTION In view of the above, the present invention provides a combustion apparatus that is improved in a combustion apparatus including an exhaust restriction cylinder, reduces fan noise, and can also reduce Helmholtz resonance noise. It is said.

上記課題を解決するために、本発明は、バーナを内蔵する燃焼筐と、燃焼筐内に燃焼用空気を供給するファンと、燃焼筐の上方に配置され、バーナの燃焼排気で加熱される熱交換器と、熱交換器の上方に配置され、熱交換器を通過した燃焼排気が流入する排気フードとを備え、排気フードの上壁部から上方にのびる筒状の排気口を介して燃焼排気が排出されるようにした燃焼装置であって、排気口に下方から挿入される、排気口よりも小径の排気制限筒を備え、排気制限筒は、その下端から径方向外方にのびる環状のフランジ部を有し、このフランジ部を排気フードの上壁部の排気口の開口縁部に固定するものにおいて、フランジ部の外周に、上方に立ち上る筒部が形成され、フランジ部が筒部の上端で排気フードの上壁部の排気口の開口縁部に固定されると共に、筒部に、燃焼排気が通過する通気孔が周方向の間隔を存して複数開設されることを特徴とする。   In order to solve the above-mentioned problems, the present invention provides a combustion housing that contains a burner, a fan that supplies combustion air into the combustion housing, and heat that is disposed above the combustion housing and is heated by the combustion exhaust of the burner. Combustion exhaust through a tubular exhaust port that extends upward from the upper wall of the exhaust hood, and includes an exchanger and an exhaust hood that is disposed above the heat exchanger and into which combustion exhaust that has passed through the heat exchanger flows. Is a combustion apparatus that is inserted into the exhaust port from below, and includes an exhaust restriction cylinder having a smaller diameter than the exhaust port, and the exhaust restriction cylinder has an annular shape extending radially outward from its lower end. In the one having a flange portion and fixing the flange portion to the opening edge of the exhaust port of the upper wall portion of the exhaust hood, a cylindrical portion rising upward is formed on the outer periphery of the flange portion, and the flange portion is Opening edge of the exhaust port on the upper wall of the exhaust hood at the upper end A is fixed, the cylindrical portion, the combustion exhaust vent, characterized in that it is more open to exist a circumferential interval passes.

本発明によれば、熱交換器を通過した燃焼排気が、排気制限筒を介して排気口に流れるだけでなく、筒部に開設した通気孔を経由して排気口に流れるため、排気制限筒の断面積をヘルムホルツ型の共鳴騒音の低減効果が得られるように小さくしても、燃焼排気の通過抵抗は小さくなる。従って、ファン回転数を然程高くせずに済み、ファン騒音を低減できる。また、各通気孔から流入した燃焼排気は、一旦径方向内方に流れた後、排気口に向けて上方に屈曲して流れるため、燃焼排気の流線が長くなり、更に、各通気孔から流入する燃焼排気が周方向に隣接する通気孔から流入する燃焼排気とぶつかり合い、音響的な抵抗となる。そのため、通気孔から流入する燃焼排気の流れは、上記（１）式の排気通路長Ｌを長くするのと同等の効果を発揮する。従って、通気孔を形成しても、ヘルムホルツ型の共鳴騒音を低減できる。   According to the present invention, the exhaust gas that has passed through the heat exchanger not only flows to the exhaust port via the exhaust restriction tube, but also flows to the exhaust port via the vent hole formed in the tubular portion. Even if the cross-sectional area is made small so that the effect of reducing Helmholtz resonance noise can be obtained, the passage resistance of the combustion exhaust gas becomes small. Therefore, it is not necessary to increase the fan rotation speed so much, and fan noise can be reduced. In addition, the combustion exhaust gas flowing in from the respective vent holes once flows inward in the radial direction, and then bends upward and flows toward the exhaust port. The inflowing combustion exhaust gas collides with the combustion exhaust gas flowing in from the circumferentially adjacent vent holes, and becomes acoustic resistance. Therefore, the flow of the combustion exhaust gas flowing from the vent hole exhibits the same effect as increasing the exhaust passage length L in the above formula (1). Therefore, Helmholtz-type resonance noise can be reduced even if the vent hole is formed.

尚、筒部に形成する全通気孔の合計面積が排気制限筒の断面積の２５％より小さいと、燃焼排気の通過抵抗を十分に小さくできず、また、全通気孔の合計面積が排気制限筒の断面積の５０％より大きいと、通気孔が持つ音響的な抵抗としての効果が薄れて、ヘルムホルツ型の共鳴騒音を十分に低減できなくなる。従って、全通気孔の合計面積は、排気制限筒の断面積の２５〜５０％であることが望ましい。   If the total area of all the vent holes formed in the cylinder portion is smaller than 25% of the cross-sectional area of the exhaust restriction cylinder, the passage resistance of the combustion exhaust gas cannot be sufficiently reduced, and the total area of all the vent holes is limited to the exhaust restriction. When it is larger than 50% of the cross-sectional area of the cylinder, the effect of the acoustic resistance of the vent hole is reduced, and the Helmholtz resonance noise cannot be sufficiently reduced. Therefore, it is desirable that the total area of all the vent holes is 25 to 50% of the cross-sectional area of the exhaust restriction cylinder.

本発明の実施形態の燃焼装置の正面図。The front view of the combustion apparatus of embodiment of this invention. 図１のＩＩ−ＩＩ線で切断した排気フード及び給気フードの切断側面図。FIG. 2 is a cut side view of the exhaust hood and the supply hood cut along the line II-II in FIG. 1. 図２のＩＩＩ−ＩＩＩ線で切断した排気フード及び給気フードの切断正面図。FIG. 3 is a cut front view of an exhaust hood and an air supply hood cut along line III-III in FIG. 2.

図１は屋内に設置する給湯用熱源機から成る燃焼装置を示している。この燃焼装置は、外装ケース１を備えている。外装ケース１内には、濃淡燃焼式のバーナ２を複数本内蔵する燃焼筐３と、燃焼筐３の下方のファン４と、燃焼筐３の上方の給湯用熱交換器５と、熱交換器５の上方の排気フード６と、排気フード６を覆う給気フード７とが配置されている。そして、図示省略した屋外にのびる給気筒からの外気をファン４により給気フード７とこれに接続する給気ダクト７２（図２参照）とを介して吸引し、この外気を燃焼筐３内に燃焼用空気として供給するようにしている。バーナ２の燃焼排気は燃焼筐３から熱交換器５に流れてこれを加熱する。そして、熱交換器５を通過した燃焼排気は排気フード６に流入して、排気フード６から給気筒の内側の図示省略した排気筒を介して屋外に排出される。   FIG. 1 shows a combustion apparatus comprising a hot water supply heat source installed indoors. This combustion apparatus includes an outer case 1. In the outer case 1, a combustion housing 3 containing a plurality of burners 2 of light and dark combustion, a fan 4 below the combustion housing 3, a hot water supply heat exchanger 5 above the combustion housing 3, and a heat exchanger An exhaust hood 6 above 5 and an air supply hood 7 covering the exhaust hood 6 are arranged. Then, outside air from a supply cylinder that extends outside the drawing is sucked by the fan 4 through the supply hood 7 and the supply duct 72 (see FIG. 2) connected to the supply hood 7, and this outside air is put into the combustion housing 3. The air is supplied as combustion air. The combustion exhaust from the burner 2 flows from the combustion housing 3 to the heat exchanger 5 to heat it. The combustion exhaust gas that has passed through the heat exchanger 5 flows into the exhaust hood 6 and is discharged from the exhaust hood 6 to the outside through an exhaust cylinder (not shown) inside the supply cylinder.

図２、図３を参照して、給気フード７は、その上壁部から上方にのびる筒状の給気口７１を有しており、この給気口７１に給気筒が接続される。また、給気フード７の後面（図２で右方の面）は開放されており、この後面に給気ダクト７２が接続される。そして、給気筒からの外気が、給気口７１と、給気フード７内に画成される排気フード６との間の空間とを介して給気ダクト７２に導かれるようにしている。   With reference to FIGS. 2 and 3, the air supply hood 7 has a cylindrical air supply port 71 extending upward from the upper wall portion, and a supply cylinder is connected to the air supply port 71. Further, the rear surface of the air supply hood 7 (the surface on the right side in FIG. 2) is opened, and the air supply duct 72 is connected to this rear surface. The outside air from the supply cylinder is guided to the supply air duct 72 through the space between the supply air port 71 and the exhaust hood 6 defined in the supply air hood 7.

排気フード６は、その上壁部から上方にのびる筒状の排気口６１を有しており、この排気口６１に排気筒が接続される。排気口６１の上部内周には、排気筒内での燃焼排気中の水分の凝縮で生ずるドレン水を受け止める筒状のドレン受け６２が装着されている。また、排気口６１に、ドレン受け６２の底部に連通する排水管６２ａを連結している。排水管６２ａは、給気口７１を通して外方に突出しており、その外端部にキャップ６２ｂを装着している。そして、キャップ６２ｂを取り外すことにより、ドレン受け６２に溜ったドレン水を排水管６２ａを介して抜くことができるようにしている。   The exhaust hood 6 has a cylindrical exhaust port 61 extending upward from the upper wall portion, and the exhaust tube is connected to the exhaust port 61. A cylindrical drain receiver 62 that receives drain water generated by condensation of moisture in the combustion exhaust gas in the exhaust cylinder is attached to the upper inner periphery of the exhaust port 61. A drain pipe 62 a communicating with the bottom of the drain receiver 62 is connected to the exhaust port 61. The drain pipe 62a protrudes outward through the air supply port 71, and a cap 62b is attached to the outer end thereof. Then, by removing the cap 62b, the drain water accumulated in the drain receiver 62 can be removed through the drain pipe 62a.

排気フード６には、更に、排気口６１に下方から挿入される、排気口６１よりも小径の排気制限筒６３が設けられている。排気制限筒６３は、その下端から径方向外方にのびるフランジ部６４を有している。フランジ部６４の外周には、上方に立ち上がる筒部６５が形成されている。そして、フランジ部６４を、筒部６５の上端の曲げ縁部６５ａにおいて、排気フード６の上壁部の排気口６１の開口縁部下面に固定している。   The exhaust hood 6 is further provided with an exhaust restriction cylinder 63 having a smaller diameter than the exhaust port 61 and inserted into the exhaust port 61 from below. The exhaust restriction cylinder 63 has a flange portion 64 extending radially outward from its lower end. A cylindrical portion 65 that rises upward is formed on the outer periphery of the flange portion 64. The flange portion 64 is fixed to the lower surface of the opening edge portion of the exhaust port 61 of the upper wall portion of the exhaust hood 6 at the bent edge portion 65 a at the upper end of the cylindrical portion 65.

ここで、排気制限筒６３の断面積を小さくすれば、上記（１）式の排気通路断面積Ｓを小さくしたと同様の効果が得られ、共鳴周波数を燃焼振動周波数よりも小さくして、ヘルムホルツ型の共鳴騒音を低減することができる。然し、このままでは、排気制限筒６３における燃焼排気の通過抵抗が大きくなって、所要量の燃焼用空気を供給するのに必要なファン４の回転数が高くなり、ファン騒音が大きくなってしまう。   Here, if the cross-sectional area of the exhaust restriction cylinder 63 is reduced, the same effect as that obtained by reducing the exhaust passage cross-sectional area S in the above equation (1) can be obtained, and the resonance frequency is made lower than the combustion vibration frequency to reduce the Helmholtz. The resonance noise of the mold can be reduced. However, in this state, the passage resistance of the combustion exhaust in the exhaust restriction cylinder 63 increases, and the rotational speed of the fan 4 necessary to supply a required amount of combustion air increases, and the fan noise increases.

そこで、本実施形態では、筒部６５に、燃焼排気が通過する通気孔６６を周方向の間隔を存して複数形成している。これによれば、燃焼排気が、排気制限筒６３を介して排気口６１に流れるだけでなく、通気孔６６を経由して排気口６１に流れるため、排気制限筒６３の断面積をヘルムホルツ型の共鳴騒音の低減効果が得られるように小さくしても、燃焼排気の通過抵抗は小さくなる。従って、ファン４の回転数を然程高くせずに済み、ファン騒音を低減できる。   Therefore, in the present embodiment, a plurality of vent holes 66 through which the combustion exhaust gas passes are formed in the cylindrical portion 65 at intervals in the circumferential direction. According to this, since the combustion exhaust gas flows not only to the exhaust port 61 via the exhaust restriction cylinder 63 but also to the exhaust port 61 via the vent hole 66, the sectional area of the exhaust restriction cylinder 63 is reduced to a Helmholtz type. Even if it is made small so that the effect of reducing the resonance noise is obtained, the passage resistance of the combustion exhaust gas becomes small. Therefore, it is not necessary to increase the rotational speed of the fan 4 so much, and the fan noise can be reduced.

また、各通気孔６６から流入した燃焼排気は、図２に矢印で示す如く、一旦径方向内方に流れた後、排気口６１に向けて上方に屈曲して流れ、燃焼排気の流線が長くなる。更に、各通気孔６６から流入する燃焼排気が周方向に隣接する通気孔６６から流入する燃焼排気とぶつかり合い、音響的な抵抗となる。そのため、通気孔６６から流入する燃焼排気の流れは、上記（１）式の排気通路長Ｌを長くするのと同等の効果を発揮する。従って、通気孔６６を形成しても、ヘルムホルツ型の共鳴騒音を低減できる。   Further, as shown by arrows in FIG. 2, the combustion exhaust gas flowing in from the respective vent holes 66 once flows inward in the radial direction, then flows upwardly bent toward the exhaust port 61, and the combustion exhaust streamlines become longer. Further, the combustion exhaust gas flowing in from the respective vent holes 66 collides with the combustion exhaust gas flowing in from the circumferentially adjacent vent holes 66, and becomes acoustic resistance. Therefore, the flow of the combustion exhaust gas flowing in from the vent hole 66 exhibits the same effect as increasing the exhaust passage length L in the above formula (1). Therefore, even if the vent hole 66 is formed, Helmholtz resonance noise can be reduced.

尚、筒部６５に形成する全通気孔６６の合計面積が排気制限筒６３の断面積の２５％より小さいと、燃焼排気の通過抵抗を十分に小さくできず、また、全通気孔６６の合計面積が排気制限筒６３の断面積の５０％より大きいと、通気孔６６が持つ音響的な抵抗としての効果が薄れて、ヘルムホルツ型の共鳴騒音を十分に低減できなくなることが実験結果から確認できた。従って、全通気孔６６の合計面積は、排気制限筒６３の断面積の２５〜５０％であることが望ましい。   If the total area of all the ventilation holes 66 formed in the cylinder portion 65 is smaller than 25% of the cross-sectional area of the exhaust restriction cylinder 63, the passage resistance of the combustion exhaust gas cannot be made sufficiently small, and the total of all the ventilation holes 66 It can be confirmed from the experimental results that if the area is larger than 50% of the cross-sectional area of the exhaust restriction cylinder 63, the effect of the acoustic resistance of the air vent 66 is reduced, and the Helmholtz resonance noise cannot be sufficiently reduced. It was. Therefore, the total area of all the vent holes 66 is preferably 25 to 50% of the cross-sectional area of the exhaust restriction cylinder 63.

本実施形態では、排気制限筒６３の直径（内径）を４２ｍｍ、筒部６５の直径（内径）を８６ｍｍ、筒部６５の高さを８ｍｍとし、筒部６５に、幅３ｍｍ、高さ５ｍｍの角孔状の通気孔６６を周方向に等間隔で３２個形成している。この場合、全通気孔６６の合計面積（＝４８０ｍｍ２）は、排気制限筒６３の断面積（≒１３８５ｍｍ２）の約３５％になる。 In the present embodiment, the diameter (inner diameter) of the exhaust restriction cylinder 63 is 42 mm, the diameter (inner diameter) of the cylinder part 65 is 86 mm, the height of the cylinder part 65 is 8 mm, and the cylinder part 65 has a width of 3 mm and a height of 5 mm. Thirty-two square hole-like air holes 66 are formed at equal intervals in the circumferential direction. In this case, the total area of Zentsu pores 66 (= 480mm 2) becomes about 35% of the cross-sectional area of the exhaust restriction cylinder 63 (≒ 1385mm 2).

以上、本発明の実施形態について図面を参照して説明したが、本発明はこれに限定されない。例えば、フランジ部６４に、燃焼排気が通過する小さな孔を複数形成し、燃焼排気の通過抵抗を更に小さくすることも可能である。但し、この孔では、筒部６５に形成した通気孔６６と異なり、音響的な抵抗としての効果が得られない。そのため、ヘルムホルツ型の共鳴騒音を低減するには、フランジ部６４に形成する全孔の合計面積を全通気孔６６の合計面積の１５％以下にすることが必要である。   As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to this. For example, a plurality of small holes through which the combustion exhaust passes can be formed in the flange portion 64 to further reduce the passage resistance of the combustion exhaust. However, in this hole, unlike the air hole 66 formed in the cylindrical portion 65, an effect as an acoustic resistance cannot be obtained. Therefore, in order to reduce Helmholtz-type resonance noise, the total area of all the holes formed in the flange portion 64 needs to be 15% or less of the total area of all the vent holes 66.

また、上記実施形態は、給湯用の熱交換器５を有する給湯用熱源機から成る燃焼装置に本発明を適用したものであるが、暖房用といった給湯以外の用途の熱交換器を有する燃焼装置にも同様に本発明を適用できる。   Moreover, although the said embodiment applies this invention to the combustion apparatus which consists of the hot water supply heat source machine which has the heat exchanger 5 for hot water supply, the combustion apparatus which has a heat exchanger for uses other than hot water supply, such as for heating Similarly, the present invention can be applied.

２…バーナ、３…燃焼筐、４…ファン、５…熱交換器、６…排気フード、６１…排気口、６３…排気制限筒、６４…フランジ部、６５…筒部、６６…通気孔。   DESCRIPTION OF SYMBOLS 2 ... Burner, 3 ... Combustion housing, 4 ... Fan, 5 ... Heat exchanger, 6 ... Exhaust hood, 61 ... Exhaust port, 63 ... Exhaust restriction cylinder, 64 ... Flange part, 65 ... Tube part, 66 ... Vent hole.

Claims (2)

バーナを内蔵する燃焼筐と、燃焼筐内に燃焼用空気を供給するファンと、燃焼筐の上方に配置され、バーナの燃焼排気で加熱される熱交換器と、熱交換器の上方に配置され、熱交換器を通過した燃焼排気が流入する排気フードとを備え、排気フードの上壁部から上方にのびる筒状の排気口を介して燃焼排気が排出されるようにした燃焼装置であって、
排気口に下方から挿入される、排気口よりも小径の排気制限筒を備え、排気制限筒は、その下端から径方向外方にのびる環状のフランジ部を有し、このフランジ部を排気フードの上壁部の排気口の開口縁部に固定するものにおいて、
フランジ部の外周に、上方に立ち上る筒部が形成され、フランジ部が筒部の上端で排気フードの上壁部の排気口の開口縁部に固定されると共に、筒部に、燃焼排気が通過する通気孔が周方向の間隔を存して複数開設されることを特徴とする燃焼装置。 A combustion housing with a built-in burner, a fan for supplying combustion air into the combustion housing, a heat exchanger disposed above the combustion housing and heated by the combustion exhaust of the burner, and disposed above the heat exchanger An exhaust hood into which the combustion exhaust gas that has passed through the heat exchanger flows, and the combustion exhaust gas is exhausted through a cylindrical exhaust port extending upward from the upper wall portion of the exhaust hood. ,
The exhaust restriction cylinder is inserted into the exhaust outlet from below and has a smaller diameter than the exhaust outlet. The exhaust restriction cylinder has an annular flange portion extending radially outward from the lower end thereof, and this flange portion is connected to the exhaust hood. In what is fixed to the opening edge of the exhaust port of the upper wall,
A cylindrical portion that rises upward is formed on the outer periphery of the flange portion, and the flange portion is fixed to the opening edge of the exhaust port of the upper wall portion of the exhaust hood at the upper end of the cylindrical portion, and combustion exhaust gas passes through the cylindrical portion. A combustion apparatus characterized in that a plurality of vent holes are formed at intervals in the circumferential direction. 前記筒部に形成する全通気孔の合計面積は、前記排気制限筒の断面積の２５〜５０％であることを特徴とする請求項１記載の燃焼装置。   The combustion apparatus according to claim 1, wherein a total area of all the vent holes formed in the cylinder portion is 25 to 50% of a cross-sectional area of the exhaust restriction cylinder.
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