JP2004205102A - Burner with inward port - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve lifting resistance and combustion performance by setting the size of each slit burner port and a distance between slit burner ports to be optimum values. <P>SOLUTION: The burner ports 41 are each formed into a vertically elongated slit of width 0.8 mm, whereby the blowing speed of mixed gas is increased to prevent backfire and extinguishing noises while securing a required port area. The slit burner ports 41 are lined two by two at distances of 2.0 mm between the burner ports to form burner port groups 47, whereby negative pressure arises between the burner ports 41 for pulling flames obliquely downward, improving lifting durability. The burner port groups 47 constituted by two burner ports 41 are arranged at distances of 5.0 mm between the burner ports and non burner port portions 48 are formed between the burner port groups 47, whereby secondary air is easily taken around the flames, improving the combustion performance. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

尚、理論ＣＯとは、不完全燃焼の程度を表す指数であり、燃焼排ガス中で検出されたＣＯとＣＯ_２の値から次式で計算される。理論ＣＯの値が小さい方が発生するＣＯが少なく燃焼性能が良好な状態であることを示す。
理論ＣＯ＝測定ＣＯ％×（ＣＯ_２ｍａｘ／測定ＣＯ_２％）
ＣＯ_２ｍａｘ：燃料ガスを理論空気比（λ＝１）で完全燃焼させた場合に発生する二酸化炭素の濃度
【００２８】
理論ＣＯが０．０８５％以下であれば燃焼が良好であるとすると（法規での排出基準は０．１４％以下であり、余裕度を加味して本実施形態では基準を０．０８５％以下とした）、グラフより、調理鍋Ｐと五徳リング４ｂとの距離Ｌがおよそ１０ｍｍ〜１６ｍｍの範囲でこの基準をクリアしている。また、熱効率ηは、距離Ｌが１２ｍｍよりも近づくと急激に悪化する。すなわち、Ｌ＝１２ｍｍが熱効率ηの変曲点となる。
従って、距離Ｌが１２ｍｍ〜１６ｍｍの範囲にあれば、燃焼性能を良好に維持できると共に、高い熱効率が達成できる。すなわち、距離Ｌの許容域は１２ｍｍ〜１６ｍｍとなる。
【００２９】
上述した構成のテーブルこんろ１では、調理鍋Ｐを五徳４の上に載置して、図示しない点火ボタンを押して内向きバーナ３に点火して加熱調理を行う。
内向きバーナ３の燃焼により生じた高温の燃焼ガスは、上方へ移動し鍋底に到達した後に、最初に中心付近に当たり、外周付近まで広がって良好に調理鍋Ｐを加熱する。鍋底を加熱した後の燃焼ガスは、五徳リング４ｂと調理鍋Ｐとの間の隙間Ｚから外側へと排出される。この移動に伴って発生するドラフト力によって、隙間Ｘ及び隙間Ｙから燃焼用二次空気Ａ及びＢが吸引される。
【００３０】
そして、従来のテーブルこんろに比べて、五徳リング４ｂを調理鍋Ｐに近づけて形成しているため、五徳リング４ｂと調理鍋Ｐとの間の隙間Ｚから燃焼用二次空気が吸引されてしまうことを防止できる。このため、内向きバーナ３の火炎が冷えた二次空気と直接接触して冷却されることはなく、燃焼性能が向上する。
従って、五徳爪４ａを低くして調理鍋Ｐの載置面を内向きバーナ３に近づけて熱効率の向上を図っても、燃焼性能を良好に維持することができる。
五徳リング４ｂと調理鍋Ｐの底面との最短距離Ｌは、実験によって燃焼性能及び熱効率が共に良好となる許容域に設定されている。言い換えれば、距離Ｌが実験的に設定された条件を満たすことによって、五徳リング４ｂと調理鍋Ｐとの間の隙間Ｚから二次空気が供給されないようにできると共に、排気抵抗を小さく抑えることができ、燃焼性能が向上する。つまり、調理鍋Ｐと五徳リング４ｂとの間の隙間Ｚは、燃焼排気のみをスムーズに通過させるので、給排気バランスがくずれることを防止でき燃焼性能が向上する。
また、距離Ｌがこの範囲よりも狭いと火炎が五徳リング４ｂに接触して、火炎の熱が五徳リング４ｂによって奪われるため、熱効率が低下してしまう。
【００３１】
また、帯状の金属板に複数の炎口４１をプレス打ち抜き加工によって開口し円筒状に丸めて炎口面部４０を形成しているため、炎口４１を形成する部材としては、帯状の金属板だけですみ内向きバーナ３製造のコストを低減できる。しかも、炎口４１はプレス打ち抜きによって形成されるため、炎口４１を好きな場所に自由な形状で容易に形成することが可能である。このため、炎口群４７の形状や位置関係を複雑なものとしても、容易に作製することができ、製造コストの上昇を抑制できる。
このように製造コストを低減できることは、一般的な外向き炎口バーナよりも大型になってしまう内向き炎口バーナ３においては特に有用である。
【００３２】
また、炎口４１を幅が０．８ｍｍの縦長のスリット状とすることによって、必要な炎口面積を確保しながら、混合ガスの噴出速度を速くして、バックや消火音の発生を防止できる。
本実施形態では、炎口４１の幅を０．８ｍｍとしているが、これに限ったものではなく、本出願人による各種実験によって０．６ｍｍ〜１．０ｍｍの範囲で良好な燃焼状態となることが確認された。炎口幅が１．０ｍｍよりも大きいと、混合ガスの噴出速度が急激に遅くなり、バックや消火音の問題が生じてくる。逆に、０．６ｍｍよりも小さいと、噴出速度が速くなりすぎ、リフトの問題が生じてくる。
【００３３】
更に、スリット状の炎口４１を炎口間距離２．０ｍｍで二個づつ列設して炎口群４７を形成することによって、炎口４１間が負圧になり炎口群４７に形成される連続した火炎の基部を斜め下方向に引っ張るので、リフトに対する耐久性を向上させることができる。
本実施形態では、炎口間距離を２．０ｍｍとしているが、これに限ったものではなく、本出願人による各種実験によってＴ（帯状の金属板の板厚）〜３．０ｍｍの範囲で良好な燃焼状態となることが確認された。炎口間距離が３．０ｍｍよりも大きいと、火炎が離れすぎてしまい保炎性能が十分ではなく火力を絞った時にリフトしてしまう。逆に、板厚Ｔｍｍよりも小さいと、炎口４１間の肉厚が十分にとれずプレス打ち抜きによって良好に炎口４１を形成することができない。
【００３４】
また、炎口４１二つから構成される炎口群４７を炎口群距離５．０ｍｍで配置して、炎口群４７間に無炎口部４８を形成して火炎を分割することによって、火炎の周囲から二次空気を取り込みやすくしているため、燃焼性能が向上する。
本実施形態では、炎口群４７間の距離を５．０ｍｍとしているが、これに限ったものではなく、本出願人による各種実験によって４．０ｍｍ〜６．０ｍｍの範囲で良好な燃焼状態となることが確認された。炎口群間距離が６．０ｍｍよりも大きいと、最低火力時に炎口群４７間で火移りできなくなってしまう。逆に、４．０ｍｍよりも小さいと、最大火力時に二次空気が取り込みにくくなり燃焼状態が急激に悪化する。
【００３５】
また、炎口面部４０のリング径が上方ほど大きいため、バーナ上部の燃焼空間が大きくとれ燃焼性能が向上する。更に、炎口４１の噴出方向が上方に傾くため、火炎を鍋底に勢い良く衝突させることができ、熱効率が向上する。
【００３６】
また、炎口４１の下方に形成された張り出し部２６によって、隙間Ｙから取り込まれる二次空気Ｂは、炎口４１の下部付近に形成される火炎に直接あたらないようにその流れが変化する。このため、炎口４１下端においても火炎はリフトせず良好に燃焼するので、燃焼性能が一層向上する。一般的な外向きバーナとは違い、炎口４１の下端に当たる二次空気Ｂが狭い隙間Ｙを通ってくるためにその流速が速い内向きバーナ３では、このようにして炎口４１下端にあたる二次空気の流れを変化させることは特に燃焼性能向上に効果的である。
本実施形態では、炎口４１下端からの張り出し部２６の先端までの距離Ｋを５．５ｍｍとしているが、これに限ったものではなく、本出願人による各種実験によってこの距離Ｋが、炎口４１下端からの張り出し部２６の下面までの距離Ｊの０．５〜２倍の範囲で良好な燃焼状態となることが確認された。距離Ｋが距離Ｊの２倍よりも大きいと、火炎への二次空気の供給がスムーズに行えず燃焼不良となってしまう。逆に、０．５倍よりも小さいと、炎口４１の下端付近に形成された火炎の基部に二次空気が直接あたってしまい、火炎が冷却されて燃焼速度が遅くなり炎口４１下端でリフトが生じる。
【００３７】
以上本発明の実施形態について説明したが、本発明はこうした実施形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々なる態様で実施し得ることは勿論である。
例えば、図１０に示すように、炎口群４７の間に形成された無炎口部４８に、保炎用の小炎口５１を設けても良い。この小炎口５１によって炎口面が暖められ保炎性能が向上し一層リフトしにくくなる。小炎口５１は、スリット状の炎口４１の面積の１／３以下であることが望ましい。１／３よりも大きいと、最大火力時に二次空気が取り込みにくくなり燃焼不良となってしまう。
また、本実施形態では、スリット状の炎口４１を二つ列設することによって炎口群４７を形成しているが、これに限ったものではなく、炎口群４７は三つでも四つでも複数個の炎口４１で形成すればよい。
【００３８】
また、本実施形態では、炎口４１は、一つの縦長の穴から形成されているがこれに限ったものではなく、図１１に示すように、小丸状の小丸炎口５２を縦一列に連続して接近させて並べて一つのスリット炎口を形成してもよい。このように、炎口を更にこまかく分割することによって、バックや消火音が一層生じにくくなる。
また、本実施形態では、縦長のスリット炎口４１を横方向に列設して炎口群４７を形成しているが、図１２に示すように、横長のスリット状の炎口５３を縦方向に列設して炎口群５４を形成しても構わない。また、図１３に示すように、横長の炎口を小丸状の小孔炎口５５を横一列に並べて擬スリット状に形成してもよい。
【００３９】
また、本実施形態では、分布板２４に形成する分布孔２５を、真円状に形成しているが、これに限ったものではなく、図１４に示すように、分布孔５６を長穴状に開口して分布板５７を形成しても構わない。
また、本実施形態では、五徳４を五徳爪４ａと五徳リング４ｂとで一体的に構成しているが、これに限ったものではなく、リング状の五徳リングの上に別部材の五徳爪を載置するようにしても構わない。
【００４０】
【発明の効果】
以上詳述したように、本発明の請求項１記載の内向き炎口バーナによれば、炎口幅を狭くして細長いスリット炎口とすることによって、必要な炎口面積を確保しながら、バックや消火音の発生を防止できる。しかも、スリット炎口を複数個近づけて列設して炎口群を形成することによって、保炎性能を向上させてリフトを防止することができる。加えて、炎口群同士の間には二次空気供給用の隙間が形成されるため燃焼性能も向上する。
【００４１】
更に、本発明の請求項２記載の内向き炎口バーナによれば、炎口群間の距離を適切に設定することによって、二次空気の取り込み性能と火移り性能とを両立させることができる。
【００４２】
更に、本発明の請求項３記載の内向き炎口バーナによれば、炎口群間に保炎用の小炎口を設けることによって、一層リフトを防止できる。
【図面の簡単な説明】
【図１】本実施形態としてのテーブルこんろの断面図である。
【図２】本実施形態としての内向きバーナの断面図である。
【図３】本実施形態としての分布板の上面図である。
【図４】本実施形態としての炎口部の拡大図である。
【図５】本実施形態としての張り出し部の拡大図である。
【図６】本実施形態としての本体側フランジ部の上面図である。
【図７】本実施形態としての混合管側フランジ部の上面図である。
【図８】本実施形態として内向きバーナをビルトインこんろに適用する場合の断面図である。
【図９】実験データの一例を表１に対応して示した特性グラフである。
【図１０】別の実施形態としての炎口部の拡大図である。
【図１１】別の実施形態としての炎口部の拡大図である。
【図１２】別の実施形態としての炎口部の拡大図である。
【図１３】別の実施形態としての炎口部の拡大図である。
【図１４】別の実施形態としての分布板の上面図である。
【図１５】従来例としての内向きバーナの断面図である。
【符号の説明】
３…内向きバーナ、３ｂ…バーナ本体、３ｃ…バーナヘッド、２１…混合気室、４０…炎口面部、４１…炎口、４７…炎口群、４８…無炎口部、５１…小炎口。[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an inward burner burner in which a number of vertically elongated slit burners are arranged in a circumferential direction of an inner peripheral surface.
[0002]
[Prior art]
Conventionally, in order to prevent the flame from overflowing from the bottom of the cooking pot in a table stove or the like, an inward direction in which an air-fuel mixture chamber is formed in an annular shape and a number of flame ports are arranged on an inner peripheral surface thereof. One using a flame burner is known.
Further, some of these inward-facing burner burners are provided with an elongated so-called slit burner 141 having a narrower burner width as shown in FIG. (For example, see Patent Document 1).
[0003]
[Patent Document 1]
JP-A-11-141882
[0004]
[Problems to be solved by the invention]
However, since the slit flame 141 has an elongated rectangular shape, the perimeter of the flame is longer than the amount of combustion, and the base of the flame is cooled. there were. In particular, in the inward burner burner, since the secondary air is sucked from below the inner peripheral surface where the slit burner 141 is formed, the cold secondary air directly hits the base of the flame, and such a lift is generated. Was a big problem.
Therefore, when a plurality of slit flame ports are arranged close to each other, the pressure between the flame ports becomes negative pressure and the base of the continuous flame is pulled obliquely downward, so that the durability against lift (lift resistance) can be improved. it can. However, if the slit flame ports are too dense, secondary air is difficult to be supplied to the inner slit flame port, and there is a problem that the combustion performance deteriorates.
The inward burner burner of the present invention solves the above-mentioned problems, and aims to improve both the lift resistance and the combustion performance by setting the size of the slit burner and the distance between the slit burners to optimal values. And
[0005]
[Means for Solving the Problems]
The inward-facing burner burner according to claim 1 of the present invention which solves the above-mentioned problems,
While forming an air-fuel mixture chamber in an annular shape, in the inward-facing burner burner in which a number of vertically elongated slit flames are arranged on the inner peripheral surface,
Each of the slit flame ports has a flame port width of 0.6 mm to 1.0 mm, and a plurality of slit flame ports having a distance between the flame ports in a range of the thickness (T) of the inner peripheral surface to 3.0 mm. The gist is to form a plurality of flame port groups by arranging the flame port groups, and to form a plurality of the flame port groups separated by a predetermined distance between the flame port groups larger than the distance between the flame ports.
[0006]
The inward burner burner according to claim 2 of the present invention is the inward burner burner according to claim 1,
The gist is that the distance between the flame outlet groups is 4.0 mm to 6.0 mm.
[0007]
The inward burner burner according to claim 3 of the present invention is the inward burner burner according to claim 2,
The gist of the invention is that a small flame port for flame holding of 1/3 or less of the area of the slit flame port is formed between the flame port groups.
[0008]
The inward-facing burner burner according to claim 1 of the present invention having the above-described configuration has a required burner area by narrowing the burner width to 0.6 mm to 1.0 mm and forming the slit burner to be elongated. While ensuring, the jetting speed of the mixed gas can be increased to prevent the occurrence of back noise and fire extinguishing noise.
Further, a plurality of slit flame ports are arranged in a row such that the distance between the flame ports is T (thickness of the inner peripheral surface of the annular air-fuel mixture chamber) to 3.0 mm to form a flame port group. Since the mouth becomes negative pressure and the base of the continuous flame is pulled obliquely downward, the durability against lift can be improved.
Further, since the flame becomes one lump of flame for each group of flame outlets and is divided, the secondary air is easily taken in from between them, and the combustion performance is improved.
[0009]
In addition, in the inward-facing burner burner according to claim 2 of the present invention, since the distance between the burner groups is set to 4.0 mm to 6.0 mm, the secondary air is supplied to the flame from the non-flame opening between the burner groups. Good intake and improved combustion performance. In addition, the fire transfer between the flame outlet groups is also performed favorably.
[0010]
Further, in the inward burner burner according to claim 3 of the present invention, the burner face is warmed by the flame holding small flame provided between the burner groups, so that the flame holding property is further improved.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
In order to further clarify the configuration and operation of the present invention described above, a preferred embodiment of an inward flame port burner of the present invention will be described below.
[0012]
A table stove for home use as one embodiment of the present invention will be described with reference to FIGS.
In the table stove 1 of the present embodiment, as shown in FIG. 1, an opening 2a is provided in a top plate 2, and an inward burner burner 3 (hereinafter simply referred to as an inward burner 3) is provided at a center position of the opening 2a. ) Is placed. The head of the inward burner 3 has a ring shape, and an opening formed in the center of the head is referred to as a center opening 3a. The gotoku 4 on which the cooking pot P is placed is placed on the top plate 2 so as to cover the periphery of the head of the inward burner 3 from above. As will be described later, a juice receiving tray 5 is provided below the central opening 3a of the inward burner 3.
[0013]
As shown in FIGS. 1 and 2, the inward burner 3 includes a burner main body 3b to which fuel gas and primary air are supplied, and a ring-shaped burner head 3c mounted on the burner main body 3b.
[0014]
The burner main body 3b serves as a mixing pipe section 10 for mixing the fuel gas ejected from the nozzle 6 and the primary air sucked from the primary air suction port 3d with the ejection, and a mounting section for the burner head 3c. And a main body 20 forming an annular air-fuel mixture chamber 21. On the upstream side of the gas flow path to the nozzle 6, a gas control unit 7 that opens and closes the gas flow path and adjusts the gas amount in conjunction with the operation of the operation switch is provided.
[0015]
The mixing tube section 10 is formed in a tubular shape by facing both the upper plate 11 and the lower plate 12 made of metal formed in a concave shape by press molding and by caulking the ends thereof, and is formed on the opposite side of the nozzle 6 mounting side. A mixing tube side flange portion 13 serving as a connection portion with the main body portion 20 is caulked to the end portion.
The main body 20 has a ring-shaped upper plate 22 whose upper part is bent inward by press molding, and a distribution plate 24 in which a number of distribution holes 25 are formed in a ring-shaped flat plate and opened over the entire circumference (FIG. 3). And a lower plate 23 having a ring shape and a concave cross section. Then, the upper plate 22 and the lower plate 23 face each other, and the distribution plate 24 is sandwiched between the upper plate 22 and the lower plate 23 to form a donut shape having an open upper surface and an inner peripheral side. The distribution plate 24 makes the distribution of the mixed gas supplied from the mixing pipe section 10 uniform. Further, on the inner peripheral side, a protruding portion 26 that protrudes inward from the inner peripheral surface due to caulking between the distribution plate 24 and the lower plate 23 is formed over the entire circumference. Further, a communication hole 27 is opened in the lower plate 23, and a main body side flange portion 28 serving as a connection portion with the mixing pipe portion 10 is caulked.
[0016]
A plurality of connection holes 30 are respectively opened in the main body side flange portion 28 and the mixing pipe side flange portion 13, and the main body portion 20 and the mixing pipe are connected by connecting the respective connection holes 30 using the connection screws 8. The unit 10 is connected. At this time, gas sealing is performed by the flange portions 13 and 28 abutting on each other.
[0017]
The burner head 3c is formed by rolling a band-shaped metal plate (for example, a plate thickness: 0.6 mm to 1.0 mm) having a large number of slit-shaped flame openings 41 into a cylindrical shape by press punching. 40 and a weight member 42 of a forged product, which is a weight when the burner head 3c is placed on the burner main body 3b. The weight member 42 has a ring shape. Further, when the weight member 42 is placed on the burner main body 3b, the weight member 42 comes into contact with the upper surface opening of the burner main body 3b to ensure airtightness therein, and also positions the burner head 3c and the burner main body 3b. A cylindrical support member 44 is vertically provided over the entire circumference.
[0018]
Here, the flame port surface portion 40 in which a large number of flame ports 41 are opened will be described in detail. The flame port surface portion 40 is formed by rolling a band-shaped flat plate having a large number of slit-shaped flame ports 41 opened in a ring shape by press punching, and welding both ends. The upper end of the flame port surface portion 40 is bent outward to form an upper contact surface 45 with the weight member 42, and the lower end is bent inward to form a lower contact surface with the overhang portion 26 of the burner body 3b. 46 are formed. Further, the flame port surface portion 40 is formed such that the ring diameter increases as it goes upward.
[0019]
As shown in FIG. 4, the flame outlet 41 has a vertically long slit shape having a width of 0.8 mm and a length (height) of 7 mm. Further, the flame outlets 41 are arranged in pairs at a predetermined flame distance (2 mm) to form a flame hole group 47, and the flame hole groups 47 are separated from each other by a predetermined flame hole distance (5 mm). They are spaced apart and are arranged at equal intervals over the entire circumference of the ring-shaped flame face 40. Between the groups of flame ports 47, there is a non-flame port portion 48 in which no flame is formed. The width of the non-flame port portion 48 (that is, the distance between the flame port groups) depends on the gas at the time of the minimum capacity of the inward burner 3. It is set within the allowable range of the amount of fire. The flame formed on the flame surface portion 40 is interrupted at the non-flame port portion 48, so that each flame group 47 forms one continuous flame. The distance between the flame ports 41 in the flame port group 47 is set to an appropriate distance to improve the lift resistance.
The distance J from the lower end of the flame port 41 to the lower surface of the overhang portion 26 is 7.5 mm, and the distance K from the lower end of the flame port 41 to the tip of the overhang portion 26 is 5.5 mm. (See Fig. 5)
[0020]
Next, the connection between the mixing pipe section 10 and the main body section 20 will be described in detail.
6 shows a top view of the main body side flange portion 28, and FIG. 7 shows a top view of the mixing tube side flange portion 13. In FIG. 7, the mixing tube section 10 is also shown.
The body-side flange portion 28 and the mixing tube-side flange portion 13 are respectively provided with a body-side passage hole 29 and a mixing tube-side passage hole 14 near the center, which serve as passages for mixed gas. The first connection hole 31 and the second connection hole 32 are opened in the main body side flange portion 28 point-symmetrically with respect to the center F of the main body side passage hole 29 with the main body side passage hole 29 interposed therebetween. A third connection hole 33 and a fourth connection hole 34, and a fifth connection hole 35 and a sixth connection hole 36 are provided on the mixing pipe side flange portion 13 with the mixing pipe side passage hole 14 interposed therebetween. The openings are opened point-symmetrically with respect to the center G of the passage hole 14. The distance between the center F of the main body side passage hole 29, the first connection hole 31, and the second connection hole 32 is the distance between the center G of the mixing tube side passage hole 14, the third connection hole 33, and the fourth connection hole 34. The distance is equal to the distance between the center G, the fifth connection hole 35, and the sixth connection hole 36.
[0021]
Therefore, when connecting the main body part 20 and the mixing pipe part 10, a first connection form that connects the first connection hole 31, the third connection hole 33, and the second connection hole 32 and the fourth connection hole 34, A second connection mode for connecting the first connection hole 31, the fifth connection hole 35, the second connection hole 32, and the sixth connection hole 36, the first connection hole 31, the fourth connection hole 34, and the second connection A third connection mode for connecting the holes 32 and the third connection holes 33, a fourth connection mode for connecting the first connection holes 31, the sixth connection holes 36, and the second connection holes 32 and the fifth connection holes 35. Can be connected in four forms.
[0022]
As described above, by switching the connection holes 30 to be connected, the positional relationship between the main body 20 and the mixing tube 10 can be changed. For example, in the first connection mode and the second connection mode, as shown in FIG. 1, the mixing tube section 10 is arranged inward (toward the main body section 20) and is arranged for a table stove. In the connection mode and the fourth connection mode, as shown in FIG. 8, the mixing tube section 10 is disposed facing outward and is a configuration for a built-in stove. FIG. 1 shows a second connection mode, and FIG. 8 shows a fourth connection mode.
[0023]
Therefore, since the inward burner 3 can be applied to both the table stove and the built-in stove, it is not necessary to separately manufacture the burner according to the stove, and the parts can be shared, and the cost can be reduced. Can be reduced.
In addition, even for the same table stove or built-in stove, since there are two connection states each, it can be used properly according to the arrangement state of the gas control unit 7 and the gas pipe, etc. The degree of freedom in layout is improved, and the flexibility in instrument design is increased.
Further, by opening the connection holes 30 at locations other than those shown in the present embodiment, the mixing tube section 10 and the main body section 20 can be laid out as desired.
[0024]
The outer edge of the soup tray 5 is bent outward to form a mounting edge 5a. Three mounting pieces 5b are welded at equal intervals to the bottom surface of the main body 20 of the burner main body 3b, and the juice receiving tray 5 is mounted on the mounting piece 5b by the mounting edge 5a. . When the juice tray 5 is disposed in this manner, the central opening 3a of the inward burner 3 is not completely closed, and a gap for supplying secondary air B is provided between the juice tray 5 and the inner peripheral surface of the burner body 3b. Y is formed.
[0025]
As shown in FIG. 1, the gotoku 4 covers a plurality of L-shaped gotoku claws 4 a on which the cooking pot P is placed and the inner peripheral edge of the opening 2 a of the top plate 2, and the gotoku claws 4 a are erected on the upper surface thereof. It is integrally formed with the virtues ring 4b which becomes the base which does. That is, the virtues claw 4a is configured to be supported by the virtues ring 4b. The virtuosity ring 4b is disk-shaped with a ring opening 4c formed in the center.
The inner peripheral side of the gotoku ring 4b is inclined downward toward the center of the ring to form an inclined flange 4d. The inclined flange 4d extends until it covers the entire circumference of the head of the inward burner 3, ie, covers the burner head 3c and the main body 20 of the burner main body 3b.
Gotoku 4 is placed on the top plate 2 by the outer peripheral end of the Gotoku ring 4b.
Further, a gap X for supplying the secondary air A is formed between the inward burner 3, the top plate 2 and the ring 4b.
[0026]
The height of the gotoku nail 4a is a distance from the top of the gotoku ring 4b to the top end of the gotoku nail 4a, that is, the shortest distance L between the cooking pot P and the gotoku ring 4b when the cooking pot P is placed is 12 mm or more. It is provided so as to be in a range of 16 mm (that is, L = 12 mm to 16 mm is an allowable range).
The gap Z between the cooking pot P and the virtuosity ring 4b serves as a discharge passage for the combustion exhaust of the inward burner 3. Therefore, if the gap Z is too small, the exhaust resistance increases and the combustion performance deteriorates. Conversely, if the gap Z is too large, excess secondary air for combustion flows from below the combustion exhaust in the gap Y. However, the combustion performance deteriorates because the flame is cooled. Further, when the height of the gotoku claws 4a is reduced and the gap Z is reduced, the flame comes into contact with the gotoku ring 4b and heat is taken by the gotoku ring 4b, so that the thermal efficiency decreases. .
[0027]
The above-mentioned shape of the virtues ring 4b and the distance L between the cooking pot P and the virtues ring 4b are the optimal set values experimentally obtained so that both the combustion performance and the thermal efficiency are within a good range. An example of the experimental data is as shown in Table 1 and the characteristic graph of FIG.
[Table 1]

The theoretical CO is an index indicating the degree of incomplete combustion. ₂ Is calculated from the following equation. A smaller value of the theoretical CO indicates that the amount of generated CO is smaller and the combustion performance is better.
Theoretical CO = measured CO% x (CO _2max / Measurement CO ₂ %)
CO _2max ： Concentration of carbon dioxide generated when fuel gas is completely burned at the theoretical air ratio (λ = 1)
[0028]
If the theoretical CO is 0.085% or less, it is assumed that the combustion is good (the emission standard in the regulation is 0.14% or less, and in consideration of the margin, the standard is 0.085% or less in this embodiment. According to the graph, this criterion is satisfied when the distance L between the cooking pot P and the goto ring 4b is in the range of about 10 mm to 16 mm. Further, the thermal efficiency η rapidly deteriorates when the distance L is shorter than 12 mm. That is, L = 12 mm is the inflection point of the thermal efficiency η.
Therefore, if the distance L is in the range of 12 mm to 16 mm, good combustion performance can be maintained and high thermal efficiency can be achieved. That is, the allowable range of the distance L is 12 mm to 16 mm.
[0029]
In the table stove 1 having the above-described configuration, the cooking pot P is placed on the goto 4 and the ignition button (not shown) is pressed to ignite the inward burner 3 to perform heating cooking.
The high-temperature combustion gas generated by the combustion of the inward burner 3 moves upward and reaches the bottom of the pot, first strikes the vicinity of the center, spreads to the vicinity of the outer periphery, and heats the cooking pot P well. The combustion gas after heating the bottom of the pot is discharged outward from the gap Z between the goto ring 4b and the cooking pot P. The secondary air for combustion A and B is sucked from the gap X and the gap Y by the draft force generated by this movement.
[0030]
And, since the virtue ring 4b is formed closer to the cooking pot P than the conventional table stove, the secondary air for combustion is sucked from the gap Z between the gotoku ring 4b and the cooking pot P. Can be prevented. Therefore, the flame of the inward burner 3 does not come into direct contact with the cooled secondary air to be cooled, and the combustion performance is improved.
Therefore, even if the gotoku claws 4a are lowered and the mounting surface of the cooking pot P is brought closer to the inward burner 3 to improve the thermal efficiency, it is possible to maintain good combustion performance.
The shortest distance L between the gotoku ring 4b and the bottom surface of the cooking pot P is set to an allowable range in which both combustion performance and heat efficiency are good by experiments. In other words, when the distance L satisfies the condition set experimentally, it is possible to prevent the secondary air from being supplied from the gap Z between the virtue ring 4b and the cooking pot P, and to reduce the exhaust resistance. Combustion performance is improved. In other words, since the gap Z between the cooking pot P and the virtuosity ring 4b allows only the combustion exhaust gas to pass smoothly, the supply / exhaust balance can be prevented from being lost, and the combustion performance is improved.
If the distance L is smaller than this range, the flame comes into contact with the virtue ring 4b, and the heat of the flame is taken away by the virtue ring 4b, so that the thermal efficiency is reduced.
[0031]
In addition, since a plurality of flame holes 41 are opened by press punching in a band-shaped metal plate and are rounded into a cylindrical shape to form the flame hole surface portion 40, only the band-shaped metal plate is used as a member for forming the flame holes 41. Thus, the cost of manufacturing the inward burner 3 can be reduced. In addition, since the flame port 41 is formed by press punching, the flame port 41 can be easily formed at a desired place in a free shape. For this reason, even if the shape and positional relationship of the flame port group 47 are complicated, they can be easily manufactured, and an increase in manufacturing cost can be suppressed.
This reduction in manufacturing cost is particularly useful for the inward burner burner 3 which is larger than a general outward burner burner.
[0032]
In addition, by making the flame port 41 into a vertically long slit shape having a width of 0.8 mm, it is possible to increase the ejection speed of the mixed gas while securing a necessary flame port area, and to prevent generation of a back noise or a fire extinguishing sound. .
In the present embodiment, the width of the flame port 41 is set to 0.8 mm. However, the present invention is not limited to this, and a good combustion state can be obtained in a range of 0.6 mm to 1.0 mm by various experiments by the present applicant. Was confirmed. If the flame opening width is larger than 1.0 mm, the jetting speed of the mixed gas is sharply reduced, and problems such as back noise and fire extinguishing noise occur. Conversely, if it is smaller than 0.6 mm, the ejection speed becomes too fast, and the problem of lift arises.
[0033]
Further, by forming two slit-shaped flame ports 41 in a row at a distance of 2.0 mm between the flame ports to form the flame port group 47, the pressure between the flame ports 41 becomes negative and the flame port group 47 is formed. Since the base of the continuous flame is pulled obliquely downward, the durability against lift can be improved.
In the present embodiment, the distance between the flame outlets is set to 2.0 mm. However, the present invention is not limited to this. Various experiments performed by the present applicant have a good result in the range of T (thickness of the strip-shaped metal plate) to 3.0 mm. It was confirmed that the combustion state was as follows. If the distance between the flame openings is larger than 3.0 mm, the flame will be too far apart, the flame holding performance will not be sufficient, and the flame will lift when the thermal power is reduced. On the other hand, when the thickness is smaller than the plate thickness Tmm, the thickness between the flame ports 41 cannot be sufficiently obtained, and the flame ports 41 cannot be formed well by press punching.
[0034]
In addition, by arranging a flame group 47 consisting of two flame ports 41 at a flame group distance of 5.0 mm and forming a non-flame port portion 48 between the flame groups 47 and dividing the flame, Since the secondary air is easily taken in from around the flame, the combustion performance is improved.
In the present embodiment, the distance between the flame group 47 is set to 5.0 mm. However, the distance is not limited to 5.0 mm. According to various experiments by the present applicant, a good combustion state is obtained in the range of 4.0 mm to 6.0 mm. It was confirmed that it became. If the distance between the flame groups is greater than 6.0 mm, it will not be possible to make a fire between the flame groups 47 at the time of the minimum thermal power. Conversely, if it is smaller than 4.0 mm, it is difficult to take in the secondary air at the time of the maximum thermal power, and the combustion state rapidly deteriorates.
[0035]
In addition, since the ring diameter of the flame opening face portion 40 is larger as it goes upward, the combustion space above the burner is large and the combustion performance is improved. Further, since the ejection direction of the flame port 41 is inclined upward, the flame can be vigorously collided with the bottom of the pot, and the thermal efficiency is improved.
[0036]
Further, the flow of the secondary air B taken in from the gap Y is changed by the overhanging portion 26 formed below the flame port 41 so that the secondary air B does not directly hit the flame formed near the lower portion of the flame port 41. For this reason, even at the lower end of the flame port 41, the flame is satisfactorily burned without being lifted, so that the combustion performance is further improved. Unlike a general outward burner, in the inward burner 3 whose flow velocity is high because the secondary air B impinging on the lower end of the flame port 41 comes through the narrow gap Y, the secondary air B hits the lower end of the flame port 41 in this way. Changing the flow of the secondary air is particularly effective for improving the combustion performance.
In the present embodiment, the distance K from the lower end of the flame 41 to the tip of the overhang portion 26 is set to 5.5 mm. However, the distance K is not limited to this. It has been confirmed that a favorable combustion state is achieved in a range of 0.5 to 2 times the distance J from the lower end of 41 to the lower surface of the overhang portion 26. If the distance K is larger than twice the distance J, the supply of the secondary air to the flame cannot be performed smoothly, resulting in poor combustion. Conversely, if it is smaller than 0.5 times, the secondary air directly hits the base of the flame formed near the lower end of the flame port 41, the flame is cooled and the combustion speed becomes slower, and A lift occurs.
[0037]
Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments at all, and it is needless to say that the present invention can be implemented in various modes without departing from the gist of the present invention.
For example, as shown in FIG. 10, a small flame port 51 for flame holding may be provided in a non-flame port portion 48 formed between the flame port groups 47. The small flame port 51 warms the flame port surface, improves the flame holding performance, and makes it more difficult to lift. It is desirable that the small flame port 51 is not more than ３ of the area of the slit-shaped flame port 41. If it is larger than 1/3, it is difficult to take in the secondary air at the time of the maximum thermal power, resulting in poor combustion.
Further, in this embodiment, the flame port group 47 is formed by arranging two slit-shaped flame ports 41 in a row. However, the present invention is not limited to this. However, it may be formed by a plurality of flame ports 41.
[0038]
Further, in the present embodiment, the flame outlet 41 is formed from a single vertically long hole, but is not limited to this, and as shown in FIG. One slit flame port may be formed side by side. In this way, by further finely dividing the flame outlet, the back noise and the fire extinguishing sound are more unlikely to occur.
Further, in the present embodiment, the vertically elongated slit flame ports 41 are arranged in the horizontal direction to form the flame port group 47. However, as shown in FIG. And the flame port group 54 may be formed. In addition, as shown in FIG. 13, the horizontally long flame holes may be formed in a pseudo slit shape by arranging small circular hole holes 55 in a horizontal line.
[0039]
Further, in the present embodiment, the distribution holes 25 formed in the distribution plate 24 are formed in a perfect circular shape. However, the present invention is not limited to this, and the distribution holes 56 are formed as shown in FIG. And the distribution plate 57 may be formed.
Further, in the present embodiment, the virtues 4 are integrally formed with the virtues 4a and the virtues ring 4b, but the invention is not limited to this. It may be mounted.
[0040]
【The invention's effect】
As described in detail above, according to the inward-facing burner burner according to claim 1 of the present invention, by reducing the width of the burner and forming an elongated slit burner, the required burner area can be secured. It is possible to prevent the occurrence of back noise and fire extinguishing noise. In addition, by forming a plurality of slit flame ports close to each other to form a flame port group, the flame holding performance can be improved and a lift can be prevented. In addition, since a gap for supplying secondary air is formed between the groups of flame ports, combustion performance is also improved.
[0041]
Furthermore, according to the inward-facing burner burner according to the second aspect of the present invention, by appropriately setting the distance between the burner groups, it is possible to achieve both secondary air intake performance and fire transfer performance. .
[0042]
Further, according to the inward burner burner according to the third aspect of the present invention, the lift can be further prevented by providing a small flame burner for flame holding between the burner burners.
[Brief description of the drawings]
FIG. 1 is a sectional view of a table stove as an embodiment.
FIG. 2 is a sectional view of an inward burner according to the embodiment.
FIG. 3 is a top view of a distribution plate according to the embodiment.
FIG. 4 is an enlarged view of a flame outlet as the present embodiment.
FIG. 5 is an enlarged view of an overhang as the present embodiment.
FIG. 6 is a top view of a main body side flange portion as the present embodiment.
FIG. 7 is a top view of a mixing tube side flange portion as the present embodiment.
FIG. 8 is a cross-sectional view of a case where an inward burner is applied to a built-in stove as the present embodiment.
FIG. 9 is a characteristic graph showing an example of experimental data corresponding to Table 1.
FIG. 10 is an enlarged view of a flame outlet as another embodiment.
FIG. 11 is an enlarged view of a flame outlet as another embodiment.
FIG. 12 is an enlarged view of a flame outlet as another embodiment.
FIG. 13 is an enlarged view of a flame outlet as another embodiment.
FIG. 14 is a top view of a distribution plate as another embodiment.
FIG. 15 is a sectional view of an inward burner as a conventional example.
[Explanation of symbols]
3 Inward burner, 3b Burner main body, 3c Burner head, 21 Mixture chamber, 40 Flame face, 41 Flame, 47 Flame group, 48 No flame, 51 Flame mouth.

Claims (3)

While forming an air-fuel mixture chamber in an annular shape, in the inward-facing burner burner in which a number of vertically elongated slit flames are arranged on the inner peripheral surface,
Each of the slit flame ports has a flame port width of 0.6 mm to 1.0 mm, and a plurality of slit flame ports having a distance between the flame ports in a range of the thickness (T) of the inner peripheral surface to 3.0 mm. An inward-facing burner burner, wherein a plurality of burner groups are arranged in a row and the plurality of burner groups are formed at a predetermined distance between the burner groups larger than the distance between the burner ports. 2. The inward burner burner according to claim 1, wherein the distance between the burner groups is 4.0 mm to 6.0 mm. 3. The inward-facing burner burner according to claim 2, wherein a small flame burner for flame holding having a size of 1/3 or less of the area of the slit flame burner is formed between the flame burners.

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