JP3511585B2 - Exhaust gas circulation type indirect heating heating device - Google Patents
Exhaust gas circulation type indirect heating heating deviceInfo
- Publication number
- JP3511585B2 JP3511585B2 JP35848099A JP35848099A JP3511585B2 JP 3511585 B2 JP3511585 B2 JP 3511585B2 JP 35848099 A JP35848099 A JP 35848099A JP 35848099 A JP35848099 A JP 35848099A JP 3511585 B2 JP3511585 B2 JP 3511585B2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust gas
- burner
- exhaust
- tip outer
- tube
- 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.)
- Expired - Lifetime
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
Landscapes
- Gas Burners (AREA)
- Air Supply (AREA)
- Combustion Of Fluid Fuel (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、排ガス循環式の間
接加熱発熱体に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust gas circulation type indirectly heated heating element.
【０００２】[0002]
【従来の技術】特開平８−１１４３０９号公報に開示さ
れているように、ラジアントチューブバーナと呼ばれる
間接加熱発熱体が知られている。これを用いると燃焼ガ
ス、排ガスが直接加熱炉内に排出されないので、加熱雰
囲気を調整する必要のある加熱炉（たとえば浸炭炉な
ど）に用いられている。その加熱媒体としてバーナを用
いることが多いが、シングルエンドチューブ型とダブル
エンドチューブ型とに大きく分けられる。シングルエン
ドチューブ型は一端が閉じられた１つのチューブ内を二
重管にして他端にバーナーを設置し、燃焼した排ガスを
内管と外管との間を通して排出するものである。ダブル
エンドチューブ型はＵ字状などのチューブの一端から燃
焼ガスを導入し、他端から排出するものである。蓄熱燃
焼バーナを用いる場合は両端に蓄熱燃焼バーナを取り付
け、交互に燃焼させる。2. Description of the Related Art As disclosed in Japanese Patent Laid-Open No. 8-114309, an indirect heating element called a radiant tube burner is known. When this is used, combustion gas and exhaust gas are not directly discharged into the heating furnace, so it is used in a heating furnace (for example, carburizing furnace) in which the heating atmosphere needs to be adjusted. Although a burner is often used as the heating medium, it is roughly classified into a single end tube type and a double end tube type. In the single-ended tube type, one tube whose one end is closed is made into a double tube and a burner is installed at the other end, and burned exhaust gas is discharged through between the inner tube and the outer tube. The double end tube type is one in which combustion gas is introduced from one end of a U-shaped tube and discharged from the other end. When a heat storage combustion burner is used, heat storage combustion burners are installed at both ends and burned alternately.
【０００３】[0003]
【発明が解決しようとする課題】従来の間接加熱発熱体
には、つぎの問題がある。シングルエンドチューブ型で
は、チューブ径が細い場合、たとえばバーナ径より細い
場合、チューブ内で排ガスを循環させることが難しくな
る。その結果、チューブのうちバーナ近傍だけで燃焼し
火炎が延びず、炉内を均一に加熱することができなくな
る。また、バーナ近傍で燃焼するので、バーナ先端が熱
損傷を受けやすい。そのため、従来のシングルエンドチ
ューブ型では、径を太くせざるを得なかった。ダブルエ
ンドチューブ型は排ガス循環による燃焼の緩慢化ができ
ないので、ＮＯｘ発生が抑制できない。また、配管系統
が多くなって複雑化し、装置が高価である。本発明の目
的は、チューブ径の太さによらず良好な排ガス循環がで
きる排ガス循環式間接加熱発熱体を提供することにあ
る。本発明のもう一つの目的は、チューブ径の太さによ
らず良好な排ガス循環ができるとともに、バーナ先端の
熱損傷を抑制できる排ガス循環式間接加熱発熱体を提供
することにある。The conventional indirect heating element has the following problems. In the single-ended tube type, if the tube diameter is small, for example, smaller than the burner diameter, it becomes difficult to circulate the exhaust gas in the tube. As a result, only in the vicinity of the burner in the tube, the flame does not spread and the flame does not spread, so that the inside of the furnace cannot be heated uniformly. Moreover, since the burner burns in the vicinity of the burner, the burner tip is easily damaged by heat. Therefore, in the conventional single-ended tube type, the diameter has to be increased. The double-end tube type cannot suppress combustion due to exhaust gas circulation, and therefore cannot suppress NOx generation. In addition, the number of piping systems is large and complicated, and the device is expensive. An object of the present invention is to provide an exhaust gas circulation type indirect heating element capable of excellent exhaust gas circulation regardless of the tube diameter. Another object of the present invention is to provide an exhaust gas circulation type indirect heating element that can satisfactorily circulate exhaust gas regardless of the tube diameter and can suppress heat damage to the burner tip.
【０００４】[0004]
【課題を解決するための手段】上記目的を達成する本発
明の排ガス循環式間接加熱発熱装置はつぎの通りであ
る。
（１） 加熱媒体がシングル型蓄熱燃焼バーナであり、
前記シングル型蓄熱燃焼バーナと発熱体とからなり、前
記シングル型蓄熱燃焼バーナが、給排気面と、該給排気
面より給気流れ方向下流に位置する燃料開放部と、前記
給排気面とそれより下流側部位を囲み壁に排気循環穴が
あけられたバーナ先端外管と、を有し、前記発熱体が、
一端が前記バーナ先端外管に接続され、他端が前記排気
循環穴に連通され、内部に燃焼ガスを流し排気をバーナ
先端外管内に循環させる通路が形成された、チューブま
たはパネルからなり、前記バーナ先端外管が前記排気循
環穴より下流側に絞り部を有し、前記燃料開放部が給気
流れ方向に前記絞り部と同じ位置かまたはそれより下流
側に位置する排ガス循環式間接加熱発熱装置。
（２） 前記バーナ先端外管の外側に排ガスヘッダーを
有し、前記発熱体が該排ガスヘッダーに接続されてお
り、排ガスヘッダー内部は前記バーナ先端外管内部と前
記排気循環穴で連通している（１）記載の排ガス循環式
間接加熱発熱装置。
（３） 前記排ガスヘッダー内に穴付き仕切板が設けら
れている（２）記載の排ガス循環式間接加熱発熱装置。
（４） 前記排ガスヘッダーに外部空間に開閉自在な排
気エスケイプ孔が設けられている（２）または（３）記
載の排ガス循環式間接加熱発熱装置。Means for Solving the Problems The exhaust gas circulation type indirect heating and heating device of the present invention which achieves the above object is as follows. (1) The heating medium is a single type regenerative combustion burner,
The single-type regenerative combustion burner and a heating element,
The single type heat storage combustion burner has a supply / exhaust surface and the supply / exhaust
A fuel opening portion located downstream from the surface in the supply air flow direction,
Exhaust circulation holes are provided on the wall that surrounds the air supply / exhaust surface and the downstream area.
A burner tip outer tube that is opened, and the heating element,
One end is connected to the burner tip outer pipe, and the other end is the exhaust gas.
It communicates with the circulation hole, flows combustion gas inside, and burns exhaust gas.
A tube or a tube with a passage for circulation in the outer tip tube is formed.
Or a panel, the burner tip outer tube has a throttle portion downstream of the exhaust circulation hole, and the fuel opening portion is located at the same position as the throttle portion in the supply air flow direction or downstream thereof. Exhaust gas circulation type indirect heating heat generating device. ( 2 ) An exhaust gas header is provided outside the burner tip outer pipe, the heating element is connected to the exhaust gas header, and the interior of the exhaust gas header communicates with the burner tip outer pipe through the exhaust circulation hole. ( 1 ) The exhaust gas circulation type indirect heating / heating device as described above. ( 3 ) The exhaust gas circulation type indirect heating / heating device according to ( 2 ), wherein a partition plate with a hole is provided in the exhaust gas header. ( 4 ) The exhaust gas circulation type indirect heating device according to ( 2 ) or ( 3 ), wherein the exhaust gas header has an exhaust escape hole that can be opened and closed in an external space.
【０００５】ここで、「シングル型蓄熱燃焼バーナ」と
は、「一本のバーナ内で、蓄熱体の排気ガスによる蓄熱
部と給気を加熱する部位とを使い分け、各部位を連続的
または間欠的に切り替えて用いるタイプの蓄熱バーナ」
を指す。蓄熱部は一体のものを複数の部位に分けて使い
分けてもよく、また、複数の蓄熱体と集合させ、全体と
して一体にしてもよい。なお、特開平９−７９５２４号
公報に記載のようなバーナは、一見すると一本のバーナ
のように構成されているが、燃料供給系統が複数あるこ
とから、一対の蓄熱燃焼バーナを単に隣合わせて構成し
ただけであり、本発明における「シングル型蓄熱燃焼バ
ーナ」には該当しない。また、「排ガス循環式」とは、
給気と排気とが分離され、局部的なものを除き、全体と
して対向流が起こらないことをいう。特開平８−１１４
３０９号公報記載のようなラジアントチューブバーナは
シングルエンドチューブ内で給気と排気の流路が分離さ
れておらず、チューブ内で対向流が生じているので、本
発明における「排ガス循環式」に該当しない。上記
（１）の排ガス循環式間接加熱発熱装置では、排ガスを
燃焼用エアと対向流とならずに給排気面に循環できるの
で、発熱体チューブの太さに関係なく、円滑に排ガスを
循環でき、燃焼を緩慢化して、火炎を伸ばし、発熱体を
ほぼ均一に加熱することができる。上記（１）の排ガス
循環式間接加熱発熱装置では、バーナ先端外管が下流側
部に絞り部を有するので、絞り部での流れ抵抗が大きく
なって燃焼用エアの一部が給排気面の排気ポートにショ
ートパスし、バーナ先端部およびバーナ内部の過熱を防
止することができる。上記（２）、（３）の排ガス循環
式間接加熱発熱装置では、排ガスヘッダーを介して排ガ
スをバーナ先端外管内に戻すようにしたので、バーナ先
端外管周りから均一に排ガスをバーナ先端外管内に循環
させることができる。上記（４）の排ガス循環式間接加
熱発熱装置では、排ガスヘッダーに外部空間に開閉自在
な排気エスケイプ孔が設けられているので、チューブ内
を冷却したいとき、チューブ内をバーナを介さずに直接
外部に連通させることができる。したがって、発熱装置
の冷却性能が上がる。The term "single-type regenerative combustion burner" as used herein means that "in a single burner, a heat storage portion by exhaust gas of a regenerator and a portion for heating supply air are selectively used, and each portion is continuous or intermittent. Type thermal storage burner
Refers to. The heat storage section may be divided into a plurality of parts and used separately, or may be integrated with a plurality of heat storage bodies to be integrated as a whole. The burner described in Japanese Patent Laid-Open No. 9-79524 is configured like a single burner at first glance, but since there are a plurality of fuel supply systems, a pair of heat storage combustion burners are simply arranged next to each other. It is configured only and does not correspond to the "single-type heat storage combustion burner" in the present invention. In addition, “exhaust gas circulation type” means
It means that the supply air and the exhaust air are separated, and the counterflow does not occur as a whole except for local ones. JP-A-8-114
In the radiant tube burner as described in Japanese Patent No. 309 publication, the flow paths of the air supply and the exhaust are not separated in the single end tube, and the counterflow is generated in the tube. Not applicable. the above
In the exhaust gas circulation type indirect heating device of (1), the exhaust gas can be circulated to the air supply / exhaust surface without forming a counterflow with the combustion air, so that the exhaust gas can be smoothly circulated regardless of the thickness of the heating element tube, Combustion can be slowed to extend the flame and heat the heating element almost uniformly. In the above-mentioned (1) exhaust gas circulation type indirect heating / heating device, since the burner tip outer tube has the throttle portion on the downstream side, the flow resistance in the throttle portion becomes large, and a part of the combustion air is supplied to the supply / exhaust surface. Short-pass to the exhaust port to prevent overheating of the burner tip and inside the burner. In the above-described ( 2 ) and ( 3 ) exhaust gas circulation type indirect heating / heating devices, since the exhaust gas is returned to the inside of the burner tip outer tube through the exhaust gas header, the exhaust gas is uniformly distributed from around the burner tip outer tube. Can be circulated. In the exhaust gas circulation type indirect heating device described in ( 4 ) above, the exhaust gas header is provided with an exhaust escape hole that can be opened and closed in the external space. Therefore, when cooling the inside of the tube, the inside of the tube can be directly exposed to the outside without a burner. Can be connected to. Therefore, the cooling performance of the heat generating device is improved.
【０００６】[0006]
【発明の実施の形態】本発明実施例の排ガス循環式間接
加熱発熱装置を、図１〜図１０を参照して説明する。図
１、図２は本発明の第１実施例を示し、図３、図４は本
発明の第２実施例を示し、図５は本発明の第３実施例を
示し、図６は本発明の第４実施例を示し、図７は本発明
の第５実施例を示し、図８は本発明の第６実施例を示
し、図９は本発明の第７実施例を示し、図１０は何れの
本発明実施例にも適用可能な蓄熱燃焼バーナを示す。何
れの実施例にも共通する部分には全実施例にわたって同
じ符号を付してある。まず、本発明の全実施例に共通す
る構造、作用を、たとえば図１、図２、図１０を参照し
て説明する。BEST MODE FOR CARRYING OUT THE INVENTION An exhaust gas circulation type indirect heating / heating device according to an embodiment of the present invention will be described with reference to FIGS. 1 and 2 show a first embodiment of the present invention, FIGS. 3 and 4 show a second embodiment of the present invention, FIG. 5 shows a third embodiment of the present invention, and FIG. 6 shows the present invention. 7 shows a fifth embodiment of the present invention, FIG. 8 shows a sixth embodiment of the present invention, FIG. 9 shows a seventh embodiment of the present invention, and FIG. 1 shows a heat storage combustion burner applicable to any of the embodiments of the present invention. The parts common to any of the embodiments are given the same reference numerals throughout the embodiments. First, the structure and operation common to all the embodiments of the present invention will be described with reference to, for example, FIGS. 1, 2, and 10.
【０００７】図１、図２、図１０に示すように、本発明
実施例の排ガス循環式間接加熱発熱装置１は、加熱媒体
がシングル型蓄熱燃焼バーナ１０であり、排ガスが燃焼
用エアと非対向流でシングル型蓄熱燃焼バーナ１０の給
排気面１４の給気流れ方向すぐ下流の部分に循環され
る、排ガス循環式間接加熱発熱装置からなる。As shown in FIGS. 1, 2 and 10, in the exhaust gas circulation type indirect heating device 1 of the embodiment of the present invention, the heating medium is the single type regenerative combustion burner 10, and the exhaust gas is not the combustion air. It is composed of an exhaust gas circulation type indirect heating device which is circulated in a counter flow in a portion immediately downstream of the supply / exhaust surface 14 of the single-type regenerative combustion burner 10 in the supply air flow direction.
【０００８】さらに詳しくは、本発明実施例の排ガス循
環式間接加熱発熱装置は、シングル型蓄熱燃焼バーナ１
０と発熱体２０とからなる。シングル型蓄熱燃焼バーナ
１０は、給気流れ方向に上流側から下流側に向かって順
に設けられた、給排気切替機構１１と、蓄熱体１２と、
バーナ先端部１３とからなる。給排気切替機構１１は、
軸芯まわりに回転することにより給排気を切り換える。
蓄熱体１２はハニカム体からなり排気が通過する時に排
気熱を奪って蓄熱し給気が通過する時に放熱して給気を
予熱する。蓄熱体１２の中心部を燃料ガスが通り、その
周囲をパイロットエアが通り、その外側を給排気が通
る。１９はスパーク部である。More specifically, the exhaust gas circulation type indirect heating heat generating apparatus of the embodiment of the present invention is a single type regenerative combustion burner 1.
0 and heating element 20. The single type heat storage combustion burner 10 is provided with an air supply / exhaust gas switching mechanism 11, a heat storage body 12, and a heat storage body 12, which are sequentially provided from the upstream side to the downstream side in the supply air flow direction.
And the burner tip 13. The supply / exhaust switching mechanism 11
The air supply / exhaust is switched by rotating around the axis.
The heat storage body 12 is made of a honeycomb body, and absorbs exhaust heat when the exhaust gas passes therethrough and stores the heat, and radiates heat when the supply air passes to preheat the supply air. Fuel gas passes through the center of the heat storage body 12, pilot air passes through the periphery thereof, and supply and exhaust air passes outside thereof. Reference numeral 19 is a spark section.
【０００９】バーナ先端部１３は、給排気ポート１８が
開口する給排気面１４と、給排気面１４より給気流れ方
向に下流に位置し燃料ガスを開放する燃料開放部１５
と、給排気面１４とそれより下流側部位を囲む壁を有し
該壁に排気循環穴１７があけられたバーナ先端外管１６
（図１０にはバーナ先端外管１６は図示していない）
と、を有する。給排気ポートは、給気または排気を通
す。排気は排気循環穴１７を通してバーナ先端外管１６
内に戻る。排気循環穴１７は、バーナ先端外管１６に周
方向に等間隔に複数個穿設されている。バーナ先端外管
１６はバーナ１０と一体でなくてもよい。The burner tip portion 13 has an air supply / exhaust surface 14 on which an air supply / exhaust port 18 opens, and a fuel opening portion 15 located downstream of the air supply / exhaust surface 14 in the air supply flow direction for releasing fuel gas.
And a burner tip outer pipe 16 having a wall surrounding the air supply / exhaust surface 14 and a portion downstream thereof and having an exhaust circulation hole 17 formed in the wall.
(The burner tip outer tube 16 is not shown in FIG. 10)
And. The air supply / exhaust port allows air supply or exhaust to pass. Exhaust gas passes through the exhaust circulation hole 17 and the burner tip outer pipe 16
Return to inside. A plurality of exhaust circulation holes 17 are formed in the burner tip outer pipe 16 at equal intervals in the circumferential direction. The outer burner tip tube 16 may not be integral with the burner 10.
【００１０】発熱体２０が、一端がバーナ先端外管１６
に接続され、他端が排気循環穴１７に連通され、内部に
燃焼ガスおよび循環排ガスを流し排ガスを排気循環穴１
７を通してバーナ先端外管１６内に循環させる通路が形
成された、チューブまたはパネル（二重管の場合も含
む。以下、単にチューブという）からなる。発熱体２０
は、内部を通る燃焼ガスおよび循環排ガスの高温ガスに
よって加熱されて熱を放射するラジアントチューブとな
り、炉内を加熱する。発熱体２０はバーナ側チューブ２
１と反バーナ側チューブ２２とを有し、バーナ側チュー
ブ２１と反バーナ側チューブ２２はつながっている。The heating element 20 has a burner tip outer tube 16 at one end.
Is connected to the exhaust gas circulation hole 17, and the other end is communicated with the exhaust gas circulation hole 17, and the combustion gas and the circulating exhaust gas are flown inside to discharge the exhaust gas to the exhaust gas circulation hole 1.
It is composed of a tube or a panel (including a case of a double tube; hereinafter simply referred to as a tube) in which a passage for circulating the burner tip outer tube 16 through 7 is formed. Heating element 20
Is a radiant tube that radiates heat by being heated by the combustion gas passing therethrough and the hot gas of the circulating exhaust gas, and heats the inside of the furnace. The heating element 20 is the burner side tube 2
1 and the anti-burner side tube 22. The burner side tube 21 and the anti-burner side tube 22 are connected.
【００１１】バーナ先端外管１６は、排気循環穴１７よ
り給気流れ方向下流側に絞り部１６ａを有し、たとえば
レデューサ（バーナ先端外管１６と同じ部材のため、レ
デューサにも１６の番号を付す）からなる。燃料開放部
１５は、給気流れ方向に絞り部１６ａと同じ位置かまた
はそれより下流側に位置する。The burner tip outer pipe 16 has a throttle portion 16a downstream of the exhaust circulation hole 17 in the supply air flow direction. For example, a reducer (because it is the same member as the burner tip outer pipe 16, the reducer is also numbered 16). Attached). The fuel release section 15 is located at the same position as the throttle section 16a or in the downstream side in the supply air flow direction.
【００１２】排ガス循環式間接加熱発熱装置１は、バー
ナ先端外管１６の外側に排ガスヘッダー３０を有してい
てもよい。排ガスヘッダー３０が設けられる場合、発熱
体２０のバーナ先端外管１６に接続される側と反対側の
端部は、排ガスヘッダー３０に接続され、排ガスヘッダ
ー３０の内部はバーナ先端外管１６の内部と排気循環穴
１７で連通している。排ガスヘッダー３０が設けられる
場合、排ガスヘッダー３０内に穴３２付き仕切板３１が
設けられていてもよい。穴３２付き仕切板３１は、他の
圧損生成手段で置き換えられてもよい。The exhaust gas circulation type indirect heating device 1 may have an exhaust gas header 30 outside the burner tip outer pipe 16. When the exhaust gas header 30 is provided, the end of the heating element 20 opposite to the side connected to the burner tip outer pipe 16 is connected to the exhaust gas header 30, and the inside of the exhaust gas header 30 is the inside of the burner tip outer pipe 16. And the exhaust circulation hole 17 communicate with each other. When the exhaust gas header 30 is provided, the partition plate 31 with the holes 32 may be provided in the exhaust gas header 30. The partition plate 31 with the holes 32 may be replaced by another pressure loss generating means.
【００１３】つぎに、本発明の全実施例に共通する作用
を説明する。シングル型蓄熱燃焼バーナ１０は、燃焼用
メインエア（給気）を蓄熱体１２で予熱し、給排気面１
４から吹き出す。一方、燃料ガスはパイロットエアと共
に燃料開放部１５から吹き出す。燃料ガスは、スパーク
部１９で着火され、燃料開放部１５の下流で、燃焼用メ
インエアと混合して火炎を形成し、燃焼する。燃焼ガス
は発熱体チューブをバーナ側チューブ２１から反バーナ
側チューブ２２へと流れ、蓄熱燃焼バーナ１０に向かっ
て戻り、バーナ先端外管１６の外側から排気循環穴１７
を通って給排気面１４近傍に、給気の流れ方向に対して
横方向から、戻る。排ガスの一部は、給気とともに給気
流れ方向下流に流れて発熱体２０内を循環し、残りは排
気ポートとして働いている給排気ポート１８を通して蓄
熱体１２に流れ、蓄熱体１２で熱を奪われて温度が下が
り、給排気切替機構１１を通って大気に放出される。The operation common to all the embodiments of the present invention will be described below. The single-type regenerative combustion burner 10 preheats main combustion air (supply air) with the regenerator 12 to supply / exhaust surface 1
Blow out from 4. On the other hand, the fuel gas is blown out from the fuel opening portion 15 together with the pilot air. The fuel gas is ignited in the spark unit 19, and is mixed with the main combustion air downstream of the fuel opening unit 15 to form a flame and burn. The combustion gas flows from the burner side tube 21 to the anti-burner side tube 22 through the heating element tube, returns toward the heat storage combustion burner 10, and from the outside of the burner tip outer pipe 16 to the exhaust circulation hole 17
And returns to the vicinity of the air supply / exhaust surface 14 from a direction lateral to the flow direction of the air supply. A part of the exhaust gas flows downstream of the supply air flow direction together with the supply air, circulates in the heating element 20, and the rest flows to the heat storage body 12 through the supply / exhaust port 18 that functions as an exhaust port, and heat is stored in the heat storage body 12. The temperature is deprived and the temperature is lowered, and the air is released to the atmosphere through the supply / exhaust gas switching mechanism 11.
【００１４】排気がシングル型蓄熱燃焼バーナ１０に戻
されるので、燃焼用メインエアが排気で希釈され、燃焼
が緩慢になって、ＮＯｘ生成量が低下するとともに、火
炎が長く延びる。これによって、バーナ側チューブ２１
から反バーナ側チューブ２２との温度差が少なくなり、
発熱体温度が全長にわたってほぼ均一化し、炉内を均一
加熱することができる。Since the exhaust gas is returned to the single type regenerative combustion burner 10, the main combustion air is diluted with the exhaust gas, the combustion becomes slow, the NOx production amount decreases, and the flame extends for a long time. As a result, the burner side tube 21
Therefore, the temperature difference with the tube 22 on the side opposite to the burner decreases,
The temperature of the heating element becomes almost uniform over the entire length, and the inside of the furnace can be heated uniformly.
【００１５】また、排気をバーナ側チューブ２１から反
バーナ側チューブ２２に流し、反バーナ側チューブ２２
からバーナ先端外管１６の排気循環穴１７を通してシン
グル型蓄熱燃焼バーナ１０の給排気面１４近傍に戻すの
で、排気の戻りが燃焼用メインエアと対向流とならず、
円滑に給排気面１４近傍に戻すことができ、排気を循環
させることができる。従来のような単一チューブ内での
排気循環の場合は、チューブ径が細くなってくると排気
の戻りが悪くなり、排気循環が円滑に行われなくなっ
て、バーナ出口で局部的に燃焼し、バーナ近傍だけが発
熱体が赤熱するが、本発明では排気の横側戻しによって
チューブ径の大小によらずに円滑に排気を循環させるこ
とができ、炉内均一加熱に寄与できる。Exhaust gas flows from the burner-side tube 21 to the anti-burner-side tube 22 and the anti-burner-side tube 22.
Since it returns to the vicinity of the air supply / exhaust surface 14 of the single type regenerative combustion burner 10 through the exhaust circulation hole 17 of the burner tip outer pipe 16, the return of the exhaust does not become a counterflow with the main combustion air.
The air can be smoothly returned to the vicinity of the air supply / exhaust surface 14, and the exhaust gas can be circulated. In the case of exhaust gas circulation in a single tube as in the past, when the tube diameter becomes thin, the exhaust gas returns poorly, exhaust gas circulation is not performed smoothly, and local combustion occurs at the burner outlet. Although the heating element becomes red only in the vicinity of the burner, in the present invention, the exhaust gas can be smoothly circulated by returning the exhaust gas to the lateral side regardless of the size of the tube diameter, which contributes to uniform heating in the furnace.
【００１６】バーナ先端外管１６に、排気循環穴１７よ
り下流側に、絞り部１６ａを設け、燃料開放部１５を絞
り部１６ａかそれより下流側に位置させると、燃焼用エ
アの通路断面積は燃料開放部１５の外径とバーナ先端外
管１６の絞り部１６ａの内径との間の環状通路の面積と
なり、通路断面積が絞られる。これによって、燃焼用エ
アの流れ抵抗が大きくなり、燃焼用エアの一部がショー
トパスして排ガスとともに給排気ポートから排出され、
残りが循環排ガスとともに燃焼用エアとして下流に流れ
燃料ガスと混合して燃焼する。ショートパスする燃焼用
エアの一部は、蓄熱体１２を通過する時に予熱されてい
るとはいえ、排ガスよりは温度が低く（たとえば、排ガ
スが８００℃、予熱された燃焼用エアは７００℃）、燃
料開放部１５、給排気面１４を含むバーナ先端部および
バーナ内部（蓄熱体等）を自動的に効果的に冷却する。
これによって、従来熱損傷を受けやすかったバーナ先端
部およびバーナ内部を熱的に保護でき、装置の耐久性を
向上させる。When the throttle section 16a is provided on the burner tip outer pipe 16 downstream of the exhaust circulation hole 17 and the fuel release section 15 is located at the throttle section 16a or on the downstream side thereof, the cross-sectional area of the combustion air passage is reduced. Is the area of the annular passage between the outer diameter of the fuel opening portion 15 and the inner diameter of the narrowed portion 16a of the burner tip outer pipe 16, and the passage cross-sectional area is narrowed. As a result, the flow resistance of the combustion air increases, a part of the combustion air short-passes and is discharged from the supply / exhaust port together with the exhaust gas.
The rest flows downstream as combustion air together with the circulating exhaust gas, mixes with the fuel gas, and burns. Although a part of the combustion air that short-passes is preheated when passing through the heat storage body 12, it has a lower temperature than the exhaust gas (for example, the exhaust gas is 800 ° C, the preheated combustion air is 700 ° C). , The fuel opening portion 15, the burner tip including the air supply / exhaust surface 14, and the inside of the burner (heat storage body etc.) are automatically and effectively cooled.
As a result, the tip of the burner and the inside of the burner, which have been hitherto susceptible to thermal damage, can be thermally protected and the durability of the device is improved.
【００１７】バーナ先端外管１６の周りに排ガスヘッダ
ー３０を設けた場合には、排ガス流れに淀みが生じてバ
ーナ先端外管１６の周方向に静圧が均等化し、バーナ先
端外管１６の複数の排気循環穴１７を通しての排ガスの
戻しが、バーナ先端外管１６の周方向に均一化する。反
バーナ側チューブ２２に近い方の排気循環穴１７と、そ
れと反対側の排気循環穴１７とで、排ガス流量に偏りが
生じると、均一加熱、ＮＯｘ生成量低減にとって望まし
くないが、排ガスヘッダー３０を設けることによって、
偏りを抑制することができる。排ガスヘッダー３０内に
穴３２付き仕切板３１を配置すると、穴３２をバーナ先
端外管１６の周方向に等間隔に配置することによって、
さらにバーナ先端外管１６の周方向に静圧が均等化し、
バーナ先端外管１６の複数の排気循環穴１７を通しての
排ガスの戻しが、バーナ先端外管１６の周方向にさらに
均一化する。When the exhaust gas header 30 is provided around the burner tip outer pipe 16, the stagnation occurs in the exhaust gas flow and the static pressure is equalized in the circumferential direction of the burner tip outer pipe 16, so that a plurality of burner tip outer pipes 16 are provided. The return of the exhaust gas through the exhaust circulation hole 17 is uniformized in the circumferential direction of the burner tip outer pipe 16. When the exhaust gas flow rate is uneven between the exhaust gas circulation hole 17 nearer to the anti-burner side tube 22 and the exhaust gas flow hole 17 on the opposite side, it is not desirable for uniform heating and reduction of NOx production amount. By providing
Bias can be suppressed. When the partition plate 31 with the holes 32 is arranged in the exhaust gas header 30, by arranging the holes 32 at equal intervals in the circumferential direction of the burner tip outer pipe 16,
Furthermore, the static pressure is equalized in the circumferential direction of the burner tip outer tube 16,
The return of the exhaust gas through the plurality of exhaust circulation holes 17 of the burner tip outer pipe 16 is further uniformized in the circumferential direction of the burner tip outer pipe 16.
【００１８】つぎに、本発明の各実施例に特有な構成、
作用を説明する。本発明の第１実施例では、図１、図２
に示すように、発熱体２０のチューブの径（外径で約１
００ｍｍ）は蓄熱燃焼バーナ１０の外径（約１６４ｍ
ｍ）より小さく、発熱体２０を細径としてある。発熱体
２０はＵ字状チューブからなる。バーナ先端外管１６は
下流側に向かって絞られたレデューサからなり、燃料開
放部１５位置は絞り部１６ａ位置にほぼ一致させてあ
る。バーナ先端外管１６の排気循環穴１７はレデューサ
の大径部かまたは大径部から絞り部への移行途中に（図
示例では大径部に）、複数個（図示例ではバーナ先端外
管１６の周方向に等間隔に６個）設けられている。箱型
の排ガスヘッダー３０が設けられており、発熱体２０は
排ガスを排ガスヘッダー３０に戻す。排ガスヘッダー３
０内にはバーナ先端外管１６の軸芯と直交する方向に延
びる仕切板３１が設けられており、仕切板３１にはバー
ナ先端外管１６の周りに等間隔に複数（たとえば、４
個）の穴３２が設けられている。排ガスヘッダー３０内
は仕切板３１によって２つの室に区画されている。排ガ
スは、発熱体２０から第１の室に流れ、第１の室から穴
３２を通して第２の室に流れ、第２の室から排気循環穴
１７を通してバーナ先端外管１６内に流れる。Next, the structure peculiar to each embodiment of the present invention,
The operation will be described. In the first embodiment of the present invention, FIG.
As shown in, the diameter of the tube of the heating element 20 (outer diameter is about 1
00 mm is the outer diameter of the heat storage combustion burner 10 (about 164 m)
m) and the heating element 20 has a small diameter. The heating element 20 is a U-shaped tube. The burner tip outer pipe 16 is composed of a reducer that is throttled toward the downstream side, and the position of the fuel opening portion 15 is substantially aligned with the position of the throttle portion 16a. Exhaust circulation holes 17 of the burner tip outer tube 16 are provided in a plurality of (in the illustrated example, burner tip outer tube 16 in the illustrated example) during the transition from the large diameter portion of the reducer or in the transition from the large diameter portion to the throttle portion (in the illustrated example). 6) are provided at equal intervals in the circumferential direction. A box-shaped exhaust gas header 30 is provided, and the heating element 20 returns the exhaust gas to the exhaust gas header 30. Exhaust gas header 3
A partition plate 31 extending in a direction orthogonal to the axial center of the burner tip outer tube 16 is provided in 0, and a plurality of partition plates 31 are provided around the burner tip outer tube 16 at equal intervals (for example, 4
Individual holes 32 are provided. The interior of the exhaust gas header 30 is divided into two chambers by a partition plate 31. The exhaust gas flows from the heating element 20 to the first chamber, flows from the first chamber to the second chamber through the hole 32, and flows from the second chamber through the exhaust circulation hole 17 into the burner tip outer pipe 16.
【００１９】レデューサ１６による接続により、蓄熱燃
焼バーナ１０に細径の発熱体２０を接続することができ
る。細い発熱体２０のため、炉が小型の場合でも適用で
きる。レデューサの大径部に排ガスを戻すことにより、
円滑に排ガスを戻すことができる。また、レデューサ１
６を用いることにより、給気を自動的にショートパスさ
せることができ、蓄熱燃焼バーナ１０の先端部を冷却で
きる。また、排ガスヘッダー３０および穴３２付き仕切
板３１を用いることによって、レデューサ１６の周りか
ら均一に排ガスをレデューサ１６内に循環させることが
できる。By connecting with the reducer 16, a heat generating element 20 having a small diameter can be connected to the regenerative combustion burner 10. Since the heating element 20 is thin, it can be applied even when the furnace is small. By returning the exhaust gas to the large diameter part of the reducer,
The exhaust gas can be returned smoothly. Also, reducer 1
By using 6, the supply air can be automatically short-passed and the tip portion of the heat storage combustion burner 10 can be cooled. Further, by using the exhaust gas header 30 and the partition plate 31 with the holes 32, the exhaust gas can be circulated uniformly in the reducer 16 from around the reducer 16.
【００２０】本発明の第２実施例は、図３、図４に示す
ように、本発明の第１実施例で、排ガスヘッダー３０内
の穴３２付き仕切板３１を除去したものに対応し、その
他の構成は本発明の第１実施例の構成に準じる。作用
は、レデューサ１６の周りから均一に排ガスをレデュー
サ１６内に循環させる性能が本発明の第１実施例に比べ
て若干低下する他は、本発明の第１実施例に準じる。As shown in FIGS. 3 and 4, the second embodiment of the present invention corresponds to the first embodiment of the present invention in which the partition plate 31 with the holes 32 in the exhaust gas header 30 is removed. Other configurations are similar to those of the first embodiment of the present invention. The operation is the same as that of the first embodiment of the present invention, except that the performance of uniformly circulating the exhaust gas from around the reducer 16 in the reducer 16 is slightly lower than that of the first embodiment of the present invention.
【００２１】本発明の第３実施例では、図５に示すよう
に、発熱体２０は１本のバーナ側チューブ２１とそれに
接続する２本の反バーナ側チューブ２２とからなる。反
バーナ側チューブ２２は、その排ガス戻り端が排ガスヘ
ッダーを介することなく直接バーナ先端外管１６の排気
循環穴１７に接続しており、排ガスを直接バーナ先端外
管１６内に戻す。バーナ先端外管１６は下流側に向かっ
て絞られたレデューサからなり、燃料開放部１５位置は
絞り部１６ａ位置にほぼ一致させてある。バーナ先端外
管１６の排気循環穴１７はレデューサの大径部かまたは
大径部から絞り部への移行途中に（図示例では大径部
に）、２個設けられている。In the third embodiment of the present invention, as shown in FIG. 5, the heating element 20 comprises one burner side tube 21 and two anti-burner side tubes 22 connected to it. The anti-burner side tube 22 has its exhaust gas return end directly connected to the exhaust circulation hole 17 of the burner tip outer pipe 16 without passing through the exhaust gas header, and returns the exhaust gas directly into the burner tip outer pipe 16. The burner tip outer pipe 16 is composed of a reducer that is throttled toward the downstream side, and the position of the fuel opening portion 15 is substantially aligned with the position of the throttle portion 16a. Two exhaust circulation holes 17 of the burner tip outer pipe 16 are provided in the large diameter portion of the reducer or in the transition from the large diameter portion to the throttle portion (in the large diameter portion in the illustrated example).
【００２２】レデューサの大径部に排ガスを戻すことに
より、円滑に排ガスを戻すことができる。また、レデュ
ーサ１６を用いることにより、給気を自動的にショート
パスさせることができ、蓄熱燃焼バーナ１０の先端部を
冷却できる。By returning the exhaust gas to the large diameter portion of the reducer, the exhaust gas can be smoothly returned. Further, by using the reducer 16, the supply air can be automatically short-passed, and the tip portion of the regenerative combustion burner 10 can be cooled.
【００２３】本発明の第４実施例では、図６に示すよう
に、発熱体２０は１本のバーナ側チューブ２１とそれに
接続する２本の反バーナ側チューブ２２とからなる。反
バーナ側チューブ２２は、その排ガス戻り端が排ガスヘ
ッダー３０に接続しており、排ガスヘッダー３０を介し
て排ガスをバーナ先端外管１６内に戻す。バーナ先端外
管１６は下流側に向かって絞られたレデューサからな
り、燃料開放部１５位置は絞り部１６ａ位置にほぼ一致
させてある。バーナ先端外管１６の排気循環穴１７はレ
デューサの大径部かまたは大径部から絞り部への移行途
中に、複数設けられている。In the fourth embodiment of the present invention, as shown in FIG. 6, the heating element 20 comprises one burner side tube 21 and two anti-burner side tubes 22 connected to it. The anti-burner side tube 22 has its exhaust gas return end connected to the exhaust gas header 30, and returns the exhaust gas into the burner tip outer pipe 16 via the exhaust gas header 30. The burner tip outer pipe 16 is composed of a reducer that is throttled toward the downstream side, and the position of the fuel opening portion 15 is substantially aligned with the position of the throttle portion 16a. A plurality of exhaust circulation holes 17 of the burner tip outer pipe 16 are provided at the large diameter portion of the reducer or during the transition from the large diameter portion to the throttle portion.
【００２４】レデューサの大径部に排ガスを戻すことに
より、円滑に排ガスを戻すことができる。また、レデュ
ーサ１６を用いることにより、給気を自動的にショート
パスさせることができ、蓄熱燃焼バーナ１０の先端部を
冷却できる。By returning the exhaust gas to the large diameter portion of the reducer, the exhaust gas can be smoothly returned. Further, by using the reducer 16, the supply air can be automatically short-passed, and the tip portion of the regenerative combustion burner 10 can be cooled.
【００２５】本発明の第５実施例では、図７に示すよう
に、発熱体２０は、パネル２３によって囲まれた偏平な
空間を仕切板２４によって区切って形成した、１本のバ
ーナ側通路２１（他の実施例のバーナ側チューブ２１に
相当するもの）とそれに接続する２本の反バーナ側通路
２２（他の実施例の反バーナ側チューブ２２に相当する
もの）とからなる。反バーナ側通路２２は、その排ガス
戻り端が排ガスヘッダーを介することなく直接バーナ先
端外管１６（パネル２３と仕切板２４によって囲まれた
空間）の排気循環穴１７（仕切板２４に形成された穴）
に接続しており、排ガスを直接バーナ先端外管１６内に
戻す。バーナ先端外管１６は下流側に向かって絞られた
レデューサからなり、燃料開放部１５位置は絞り部１６
ａ位置にほぼ一致させてある。バーナ先端外管１６の排
気循環穴１７はレデューサの大径部かまたは大径部から
絞り部への移行途中に（図示例では大径部に）、２個設
けられている。In the fifth embodiment of the present invention, as shown in FIG. 7, the heating element 20 has one burner side passage 21 formed by partitioning a flat space surrounded by a panel 23 by a partition plate 24. (Corresponding to the burner side tube 21 of another embodiment) and two anti-burner side passages 22 (corresponding to the anti-burner side tube 22 of another embodiment) connected thereto. The anti-burner side passage 22 has the exhaust gas return end formed in the exhaust circulation hole 17 (partition plate 24) of the burner tip outer pipe 16 (the space surrounded by the panel 23 and the partition plate 24) directly without passing through the exhaust gas header. hole)
The exhaust gas is directly returned to the burner tip outer pipe 16. The outer pipe 16 at the tip of the burner is a reducer that is throttled toward the downstream side.
It is almost aligned with the position a. Two exhaust circulation holes 17 of the burner tip outer pipe 16 are provided in the large diameter portion of the reducer or in the transition from the large diameter portion to the throttle portion (in the large diameter portion in the illustrated example).
【００２６】レデューサの大径部に排ガスを戻すことに
より、円滑に排ガスを戻すことができる。また、レデュ
ーサ１６を設けることにより、給気を自動的にショート
パスさせることができ、蓄熱燃焼バーナ１０の先端部を
冷却できる。By returning the exhaust gas to the large diameter portion of the reducer, the exhaust gas can be smoothly returned. Further, by providing the reducer 16, the supply air can be automatically short-passed and the tip portion of the regenerative combustion burner 10 can be cooled.
【００２７】本発明の第６実施例では、図８に示すよう
に、発熱体２０は二重管で構成されており、内筒２５
と、その外部の外筒２６からなる。内筒内部が他の実施
例のバーナ側通路２１に相当し、内筒２５と外筒２６と
の間が他の実施例の反バーナ側通路２２に相当する。内
筒先端の開放部から吹き出した排ガスは、先端が閉じら
れた外筒２６の中を通ってバーナ先端外管の排気循環穴
１７からバーナ先端外管内に戻す。このように構成する
と給排気の住み分けができるので、外筒２６の径をバー
ナ径近くまで小型化することができる。そして、内筒２
５を長く伸ばすことにより長尺化もできる。なお、本実
施例でもバーナ先端外管を絞っているので、給気のショ
ートパスによるバーナ冷却効果が得られる。そのため、
発熱体部分をセラミック等の耐熱性のある材料で構成す
れば、バーナ耐熱温度（たとえば、１０００℃）以上の
炉内温度となるような高温負荷浸炭炉などへの適用がで
きる。In the sixth embodiment of the present invention, as shown in FIG. 8, the heating element 20 is composed of a double tube, and the inner cylinder 25
And an outer cylinder 26 outside thereof. The inside of the inner cylinder corresponds to the burner side passage 21 of the other embodiment, and the portion between the inner cylinder 25 and the outer cylinder 26 corresponds to the non-burner side passage 22 of the other embodiment. The exhaust gas blown from the open end of the inner cylinder tip passes through the outer cylinder 26 whose tip is closed and returns from the exhaust circulation hole 17 of the burner tip outer tube into the burner tip outer tube. With such a configuration, it is possible to separate supply and exhaust of the air, so that the diameter of the outer cylinder 26 can be reduced to near the burner diameter. And the inner cylinder 2
The length can be increased by extending 5 for a long time. Since the outer tube of the burner tip is also narrowed in this embodiment, the burner cooling effect by the short path of the air supply can be obtained. for that reason,
If the heating element portion is made of a heat-resistant material such as ceramics, it can be applied to a high temperature load carburizing furnace or the like in which the furnace temperature becomes equal to or higher than the burner heat resistant temperature (for example, 1000 ° C.).
【００２８】本発明の第７実施例では、図９に示すよう
に、ヘッダー３０から外部に通ずるエスケイプ孔３３が
設けられ、その端部に開閉自在な弁３４が設けられてい
る。バーナを加熱しているときは弁３４を閉じて排ガス
を循環させるが、加熱終了後冷却したいときには、弁３
４を開けて発熱体内部の高温排ガスを直接外部に逃がす
ことができる。そのため、冷却が速くなる。このエスケ
イプ孔３３を設けないときには、チューブ内の排ガス
は、バーナの蓄熱体を通して外部に排出させるため、本
実施例のように外部に直接排出する場合に比べ、冷却が
遅い。In the seventh embodiment of the present invention, as shown in FIG. 9, an escape hole 33 communicating from the header 30 to the outside is provided, and an openable valve 34 is provided at the end thereof. When heating the burner, the valve 34 is closed to circulate the exhaust gas, but when cooling is desired after heating is completed, the valve 3
4 can be opened to allow the high-temperature exhaust gas inside the heating element to escape directly to the outside. Therefore, cooling becomes faster. When the escape hole 33 is not provided, the exhaust gas in the tube is discharged to the outside through the heat storage body of the burner, so that cooling is slower than in the case of directly discharging to the outside as in the present embodiment.
【００２９】[0029]
【発明の効果】請求項１の排ガス循環式間接加熱発熱装
置によれば、排ガスを燃焼用エアと対向流とならずに給
排気面に循環できるので、発熱体チューブの太さに関係
なく、円滑に排ガスを循環でき、燃焼を緩慢化して、火
炎を伸ばし、発熱体をほぼ均一に加熱することができ
る。請求項１の排ガス循環式間接加熱発熱装置によれ
ば、給排気面を囲み壁に排気循環穴があけられたバーナ
先端外管を設けたので、排ガスを燃焼用エアと対向流と
ならずに給排気面に循環でき、発熱体チューブの太さに
関係なく、円滑に排ガスを循環でき、燃焼を緩慢化し
て、火炎を伸ばし、発熱体をほぼ均一に加熱することが
できる。請求項１の排ガス循環式間接加熱発熱装置によ
れば、バーナ先端外管が下流側部に絞り部を有するの
で、絞り部での流れ抵抗が大きくなって燃焼用エアの一
部を給排気面の排気ポートにショートパスさせることが
でき、バーナ先端部およびバーナ内部の過熱を防止する
ことができる。請求項２の排ガス循環式間接加熱発熱装
置によれば、排ガスヘッダーを介して排ガスをバーナ先
端外管内に戻すようにしたので、バーナ先端外管周りか
ら均一に排ガスをバーナ先端外管内に循環させることが
できる。請求項３の排ガス循環式間接加熱発熱装置によ
れば、排ガスヘッダーを介して排ガスをバーナ先端外管
内に戻すようにし、排ガスヘッダー内に穴付き仕切板を
設けたので、バーナ先端外管周りから均一に排ガスをバ
ーナ先端外管内に循環させることができる。請求項４の
排ガス循環式間接加熱発熱装置によれば、排ガスヘッダ
ーに外部空間に開閉自在な排気エスケイプ孔が設けられ
ており、発熱体内の排ガスを直接外部へ排出することが
できるので、発熱装置の冷却を速くすることができる。According to the exhaust gas circulation type indirect heating heat generating device of claim 1, since the exhaust gas can be circulated on the air supply / exhaust surface without forming a counterflow with the combustion air, regardless of the thickness of the heating element tube, Exhaust gas can be circulated smoothly, combustion can be slowed, flames can be extended, and heating elements can be heated almost uniformly. According to the exhaust gas circulation type indirect heating device of claim 1 , since the burner tip outer pipe having the exhaust gas circulation hole in the wall surrounding the supply / exhaust surface is provided, the exhaust gas does not flow in the counter flow with the combustion air. It can be circulated on the air supply / exhaust surface, the exhaust gas can be smoothly circulated regardless of the thickness of the heating element tube, the combustion can be slowed, the flame can be extended, and the heating element can be heated almost uniformly. According to the exhaust gas circulation type indirect heating device of claim 1 , since the burner tip outer tube has the throttle portion on the downstream side, the flow resistance in the throttle portion becomes large and a part of the combustion air is supplied to the exhaust surface. The exhaust port can be short-passed, and overheating of the burner tip and the inside of the burner can be prevented. According to the exhaust gas circulation type indirect heating device of claim 2 , since the exhaust gas is returned to the inside of the burner tip outer tube through the exhaust gas header, the exhaust gas is uniformly circulated from around the burner tip outer tube into the burner tip outer tube. be able to. According to the exhaust gas circulation type indirect heating device of claim 3 , the exhaust gas is returned to the inside of the burner tip outer tube through the exhaust gas header, and the partition plate with holes is provided in the exhaust gas header. Exhaust gas can be uniformly circulated in the burner tip outer tube. According to the exhaust gas circulation type indirect heating device of claim 4 , the exhaust gas header is provided with the exhaust escape hole which can be opened and closed in the external space, and the exhaust gas in the heating element can be directly discharged to the outside. Can be cooled faster.
【図１】本発明の第１実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、断面図である。FIG. 1 is a cross-sectional view of a tip portion of a regenerative combustion burner and a heating element of an exhaust gas circulation type indirect heating heat generating device according to a first embodiment of the present invention.
【図２】図１の装置部分の側面図である。2 is a side view of the device portion of FIG. 1. FIG.
【図３】本発明の第２実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、断面図である。FIG. 3 is a cross-sectional view of a heat storage combustion burner tip portion and a heating element portion of an exhaust gas circulation type indirect heating heat generating device according to a second embodiment of the present invention.
【図４】図３の装置部分の側面図である。FIG. 4 is a side view of the device portion of FIG.
【図５】本発明の第３実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、斜視図である。FIG. 5 is a perspective view of a tip portion of a regenerative combustion burner and a heating element of an exhaust gas circulation type indirect heating heat generating device according to a third embodiment of the present invention.
【図６】本発明の第４実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、斜視図である。FIG. 6 is a perspective view of a tip portion of a heat storage combustion burner and a heating element of an exhaust gas circulation type indirect heating heat generating device according to a fourth embodiment of the present invention.
【図７】本発明の第５実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、斜視図である。FIG. 7 is a perspective view of a tip portion of a regenerative combustion burner and a heating element of an exhaust gas circulation type indirect heating heat generating device according to a fifth embodiment of the present invention.
【図８】本発明の第６実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、断面図である。FIG. 8 is a sectional view of a tip portion of a regenerative combustion burner and a heating element of an exhaust gas circulation type indirect heating heat generating device according to a sixth embodiment of the present invention.
【図９】本発明の第７実施例の排ガス循環式間接加熱発
熱装置の、蓄熱燃焼バーナ先端部および発熱体の部分
の、断面図である。FIG. 9 is a cross-sectional view of a tip portion of a regenerative combustion burner and a heating element of an exhaust gas circulation indirect heating device according to a seventh embodiment of the present invention.
【図１０】本発明の何れの実施例にも適用可能な、シン
グル型蓄熱燃焼バーナの断面図である。FIG. 10 is a cross-sectional view of a single type regenerative combustion burner applicable to any of the embodiments of the present invention.
１ 排ガス循環式間接加熱発熱装置 １０ 蓄熱燃焼バーナ １１ 給排気切替機構 １２ 蓄熱体 １３ バーナ先端部 １４ 給排気面 １５ 燃料開放部 １６ バーナ先端外管 １７ 排気循環穴 １８ 給排気ポート １９ スパーク部 ２０ 発熱体 ２１ バーナ側チューブ ２２ 反バーナ側チューブ ２３ パネル ２４ 仕切板 ２５ 内筒 ２６ 外筒 ３０ 排ガスヘッダー ３１ 仕切板 ３２ 穴 ３３ エスケイプ孔 ３４ 弁 1 Exhaust gas circulation type indirect heating device 10 Heat storage combustion burner 11 Air supply / exhaust switching mechanism 12 heat storage 13 Burner tip 14 Air supply / exhaust surface 15 Fuel release section 16 burner tip outer tube 17 Exhaust circulation hole 18 Air supply / exhaust port 19 Spark club 20 heating element 21 Burner tube 22 Tube on non-burner side 23 panels 24 partition boards 25 inner cylinder 26 Outer cylinder 30 exhaust gas header 31 Partition Plate 32 holes 33 Escape hole 34 valves
───────────────────────────────────────────────────── フロントページの続き (72)発明者 西山 智彦 愛知県豊田市西町１丁目132番地１ 株 式会社テラ・コーポレーション内 (56)参考文献 特開 平９−79524（ＪＰ，Ａ) 特開 平８−114309（ＪＰ，Ａ) 特開 平９−217926（ＪＰ，Ａ) 特開 平８−128608（ＪＰ，Ａ) 特開 平６−193823（ＪＰ，Ａ) 特開 平９−280516（ＪＰ，Ａ) 実開 昭52−74539（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F23C 3/00 301 F23C 11/00 318 F23C 11/00 ZAB F23D 14/12 F23L 15/02 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tomohiko Nishiyama 1-132 Nishimachi, Toyota-shi, Aichi 1 Terra Corporation Corporation (56) References JP-A-9-79524 (JP, A) JP-A 8-114309 (JP, A) JP-A-9-217926 (JP, A) JP-A-8-128608 (JP, A) JP-A-6-193823 (JP, A) JP-A-9-280516 (JP, A) A) Actual development Sho 52-74539 (JP, U) (58) Fields investigated (Int.Cl. 7 , DB name) F23C 3/00 301 F23C 11/00 318 F23C 11/00 ZAB F23D 14/12 F23L 15 / 02
Claims (4)
あり、 前記シングル型蓄熱燃焼バーナと発熱体とからなり、 前記シングル型蓄熱燃焼バーナが、給排気面と、該給排
気面より給気流れ方向下流に位置する燃料開放部と、前
記給排気面とそれより下流側部位を囲み壁に排気循環穴
があけられたバーナ先端外管と、を有し、 前記発熱体が、一端が前記バーナ先端外管に接続され、
他端が前記排気循環穴に連通され、内部に燃焼ガスを流
し排気をバーナ先端外管内に循環させる通路が形成され
た、チューブまたはパネルからなり、 前記バーナ先端外管が前記排気循環穴より下流側に絞り
部を有し、前記燃料開放部が給気流れ方向に前記絞り部
と同じ位置かまたはそれより下流側に位置する排ガス循
環式間接加熱発熱装置。1. The heating medium is a single type regenerative combustion burner.
There consists of a heating element and the single-type regenerative combustion burner, the single-type regenerative combustion burner, the air supply and exhaust surface, fed-discharge
The fuel release part located downstream of the air level in the supply air flow direction,
Exhaust circulation holes on the wall surrounding the supply and exhaust surface and the downstream side
And a burner tip outer tube opened, wherein the heating element has one end connected to the burner tip outer tube,
The other end communicates with the exhaust circulation hole and allows combustion gas to flow inside.
A passage is formed to circulate the exhaust gas into the burner tip outer tube.
In addition, the burner tip outer tube is formed of a tube or a panel, the burner tip outer tube has a throttle portion downstream of the exhaust circulation hole, and the fuel opening portion is at the same position as the throttle portion in the supply air flow direction or downstream thereof. Exhaust gas circulation type indirect heating device located in.
ダーを有し、前記発熱体が該排ガスヘッダーに接続され
ており、排ガスヘッダー内部は前記バーナ先端外管内部
と前記排気循環穴で連通している請求項１記載の排ガス
循環式間接加熱発熱装置。2. An exhaust gas header is provided outside the burner tip outer tube, the heating element is connected to the exhaust gas header, and the inside of the exhaust gas header communicates with the burner tip outer tube inside by the exhaust circulation hole. The exhaust gas circulation type indirect heating heat generating device according to claim 1 .
設けられている請求項２記載の排ガス循環式間接加熱発
熱装置。3. The exhaust gas circulation type indirect heating device according to claim 2, wherein a partition plate with a hole is provided in the exhaust gas header.
在な排気エスケイプ孔が設けられている請求項２または
請求項３記載の排ガス循環式間接加熱発熱装置。Wherein said exhaust gas header exhaust gas circulation type indirect-heating apparatus according to claim 2 or claim 3, wherein an openable exhaust Escape holes are provided outside space.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35848099A JP3511585B2 (en) | 1999-12-17 | 1999-12-17 | Exhaust gas circulation type indirect heating heating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35848099A JP3511585B2 (en) | 1999-12-17 | 1999-12-17 | Exhaust gas circulation type indirect heating heating device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001173905A JP2001173905A (en) | 2001-06-29 |
| JP3511585B2 true JP3511585B2 (en) | 2004-03-29 |
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ID=18459538
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP35848099A Expired - Lifetime JP3511585B2 (en) | 1999-12-17 | 1999-12-17 | Exhaust gas circulation type indirect heating heating device |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003097803A (en) * | 2001-09-25 | 2003-04-03 | Kanto Yakin Kogyo Co Ltd | Single end type tubular combustion burner |
| DE202008009065U1 (en) * | 2008-07-04 | 2008-10-09 | WS Wärmeprozesstechnik GmbH | Radiant heating arrangement with delay compensation |
| ATE492775T1 (en) * | 2008-11-07 | 2011-01-15 | Ws Waermeprozesstechnik Gmbh | REGENERATOR FLOX BURNER |
-
1999
- 1999-12-17 JP JP35848099A patent/JP3511585B2/en not_active Expired - Lifetime
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