JPH0133726B2 - - Google Patents
Info
- Publication number
- JPH0133726B2 JPH0133726B2 JP58238583A JP23858383A JPH0133726B2 JP H0133726 B2 JPH0133726 B2 JP H0133726B2 JP 58238583 A JP58238583 A JP 58238583A JP 23858383 A JP23858383 A JP 23858383A JP H0133726 B2 JPH0133726 B2 JP H0133726B2
- Authority
- JP
- Japan
- Prior art keywords
- primary
- fuel
- nozzle
- air
- combustion
- 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
Links
- 239000000446 fuel Substances 0.000 claims description 42
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims description 22
- 239000001301 oxygen Substances 0.000 claims description 22
- 229910052760 oxygen Inorganic materials 0.000 claims description 22
- 239000007789 gas Substances 0.000 claims description 20
- 238000002485 combustion reaction Methods 0.000 description 25
- 230000007423 decrease Effects 0.000 description 3
- 239000002737 fuel gas Substances 0.000 description 3
- 230000002459 sustained effect Effects 0.000 description 3
- 238000007796 conventional method Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 101100447665 Mus musculus Gas2 gene Proteins 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/32—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid using a mixture of gaseous fuel and pure oxygen or oxygen-enriched air
Description
本発明はガスバーナに関する。
従来から発熱量が低く、そのままでは燃焼の持
続が困難な低カロリーガスを燃焼させる方法とし
て、
高カロリーガスを混入してガスのカロリーア
ツプを図る方法、
高カロリー燃料の助燃バーナを設ける方法、
空気あるいは燃料ガスを予熱する方法、
などが知られている。
上記ではランニングコストが高くつき、
では従来、必要熱量が不明であつたために、すべ
ての空気または燃料ガスを予熱しており、このた
め加熱器が非常に大きくなり、設備費の増大をま
ねくという問題がある。
そこで本発明はかかる問題点を解消したガスバ
ーナを提供するものであつて、その特徴とすると
ころは、焚口先端を円錐状空間に形成し、その焚
口内に同心状に設けた一次空気ノズル内に一次燃
料ノズルを同心状に挿入し、一次空気ノズルの外
側に二次燃料ノズルを配設し、該二次燃料ノズル
の外側に二次空気ノズルを配設し、一次空気ノズ
ルに接続された一次空気供給管に酸素供給管を接
続したことにある。かかる構成によれば、燃料お
よび空気をそれぞれ一次と二次とに分け、酸素濃
度の上昇に伴つて自燃限界発熱量が低下するのに
着目して、その一次空気に酸素を添加するもので
あるから、低カロリーガスでも確実に着火させ
て、その燃焼を持続させることができ、しかも燃
料または空気を加熱するための加熱器が不要であ
り、かつ使用する酸素量も最少でよく、従来に比
ベランニングコストを下げることができる。
以下、本発明の一実施例を図に基づいて説明す
る。１は焚口であつて、その先端を円錐状空間に
形成してある。２は焚口１内に同心状に設けた一
次空気ノズル、３は該一次空気ノズル２内に同心
状に挿入された１次燃料ノズル、４は一次空気ノ
ズル２の外側に配設された二次燃料ノズル、５は
該二次燃料ノズル４の外側に配設された二次空気
ノズル、６，７は二次の燃料ノズル４および空気
ノズル５の先端に配設された旋回翼であつて、二
次燃料および二次空気を第１図にイで示すごとく
旋回させるものである。８は低カロリー燃料主供
給管であつて、これから２つに分岐した一次燃料
供給管８Ａと二次燃料供給管８Ｂとはそれぞれ一
次、二次の燃料ノズル３，４に接続してある。９
は空気主供給管であつて、これから２つに分岐し
た一次空気供給管９Ａと二次空気供給管９Ｂとは
それぞれ一次、二次の空気ノズル２，５に接続し
てある。１６は一次空気供給管９Ａに接続された
酸素供給管、１１は一次燃料供給管８Ａの途中に
介在させた開閉弁である。前記一次燃料ノズル３
の燃料噴射口は該ノズル３の半径方向に沿つて形
成されている。したがつてノズル３からその半径
方向に沿つて噴射された燃料ガスは一次空気ノズ
ル２内を流れる空気流によつて第１図にロで示す
ごとく焚口１から放射状に噴射されるものであ
る。
上記構成において、一次空気供給管９Ａ内を流
れる一次空気には酸素供給管１６から酸素が添加
され、酸素濃度が高い一次空気が一次空気ノズル
２内に入る。また一次燃料供給管８Ａから一次燃
料ノズル３内に入つた低カロリー燃料はその噴射
口から一次燃料ノズル３の半径方向へ噴射され、
一次空気ノズル２から噴射される酸素濃度の高い
一次空気流に乗つて焚口１から第１図のロで示す
ごとく放射状に噴射される。また二次燃料ノズル
４から低カロリーの二次燃料が第１図のイに示す
ごとく旋回させられながら噴射され、さらに二次
空気ノズル５から二次空気が旋回させられながら
噴射される。そして酸素濃度の上昇によつて燃料
の自然限界発熱量が低下するから、一次燃料が酸
素濃度の高い一次空気の作用により容易に着火さ
せられると共にその燃焼を持続させられ、また一
次燃料の燃焼熱によつて二次燃料および二次空気
を必要温度まで加熱し、全体として安定した燃焼
を持続するものである。
ここで第３図に示すごとく支燃ガス（一次空
気）中に酸素を添加し、酸素濃度を高くすれば自
燃限界発熱量（QL）を低下させることができる。
さらに第４図から明らかなように全ガス基準の発
熱量（QL′）Kcal／Ｎm3は(1)式で示されるように
一定であることがわかつた。
QL′＝QL・Ｇ／Ｇ＋Ｎ＝Ｋ（一定） ……(1)
ただしＧ：可燃ガス量（Ｎm3／ｈ）
Ｎ：支燃ガス量（Ｎm3／ｈ）
今、一次燃料ノズル３に供給される一次燃料の
全燃料に対する割合を（ｍ）とすれば、一次燃料
ノズル３で燃焼を持続させるために必要な熱量は
ｍ（QL−Qg）≡ｍ・ΔQ（Kcal／Ｎm3）である。こ
れによつて発生する熱量はｍ・QL（Kcal／Ｎm3）
であり、ｍ・QL≧ΔQであれば燃焼は持続する。
したがつてｍ≧ΔQ／QLであればよい。しかしな
がら実機では、ガスの混合や熱放散などにより火
炎を十分安定させるには、次式の関係が成り立つ
ようにすることが適当であることがわかつた。
1.3×ΔQ／QL≧ｍ≧1.1×ΔQ／QL
次に必要酸素量は(1)式から
mG・Qg／mG＋AL≧Ｋ
mG＋AL≦１／Ｋ（mG・Qg）
∴AL≦mG・Qg／Ｋ−mG＝mG（Qg／Ｋ−１）
ただしAL：限界支燃ガス量（Ｎm3／ｈ）
ここで(A)を一次燃料（mG）を燃焼させるに必
要な空気量（Ｎm3／ｈ）とすれば（ただし一次バ
ーナの空気比は1.05〜1.5が適当である）、酸素供
給量
Ｏ（Ｎm3／ｈ）はＯ＝21／79（Ａ−AL）である。
上記第１の実施例における旋回翼６，７に代え
て、第５図に示すごとくノズル４，５の内壁面に
ほぼ接線方向に沿う多数のスリツト１３を形成し
てもよいし（第２の実施例）、また第６図に示す
ごとくノズル４，５の端面に周方向に沿つてのび
る傾斜穴１４を形成してもよい（第３の実施例）。
（実施例）
ガス発熱量600Kcal／Ｎm3のCH4−N2低カロリ
ーガスの燃焼実験
（計算値）
第３図より空気中（O221％）の限界発熱量は
780Kcal／Ｎm3である。これより一次燃料の割合
（ｍ）は
780−600／780×1.3≧ｍ≧780−600／780×1.1
0.3≧ｍ≧0.25
となる。
空気比を1.2とすれば必要空気量は1.2×0.557＝
0.668Nm3／Ｎm3ガス、又第４図より全ガス中の
自燃限界発熱量は380Kcal／Ｎm3である。限界支
燃ガス量AL≦0.25×1.0×（600／380−１）＝0.14必要
酸
素量は
Ｏ＝21／79×（0.25×1.0×0.668−1.14）＝0.0270N
m3／Ｎm3Gas2.7％である。（ただし全可燃ガス量
に対する酸素供給量）
（実験）
燃焼実験結果を表１に示す。
The present invention relates to a gas burner. Conventional methods for burning low-calorie gases, which have a low calorific value and are difficult to sustain combustion as they are, include mixing high-calorie gas to increase the calorie content of the gas, installing an auxiliary combustion burner for high-calorie fuel, and using air. Alternatively, methods of preheating fuel gas are known. The above results in high running costs,
Conventionally, all the air or fuel gas was preheated because the amount of heat required was unknown, which resulted in a very large heater, leading to an increase in equipment costs. Therefore, the present invention provides a gas burner that solves these problems, and its characteristics are that the tip of the combustion opening is formed into a conical space, and the primary air nozzle is provided concentrically within the combustion opening. A primary fuel nozzle is inserted concentrically, a secondary fuel nozzle is disposed outside the primary air nozzle, a secondary air nozzle is disposed outside the secondary fuel nozzle, and the primary air nozzle is connected to the primary air nozzle. This is because the oxygen supply pipe is connected to the air supply pipe. According to this configuration, fuel and air are separated into primary and secondary air, respectively, and oxygen is added to the primary air by paying attention to the fact that the self-combustion limit calorific value decreases as the oxygen concentration increases. Therefore, even low-calorie gas can be reliably ignited and its combustion can be sustained, and there is no need for a heater to heat the fuel or air, and the amount of oxygen used is minimal, compared to conventional methods. It can reduce the running cost. Hereinafter, one embodiment of the present invention will be described based on the drawings. Reference numeral 1 is a fire pit, the tip of which is formed into a conical space. 2 is a primary air nozzle provided concentrically within the combustion opening 1; 3 is a primary fuel nozzle inserted concentrically within the primary air nozzle 2; 4 is a secondary air nozzle provided outside the primary air nozzle 2. A fuel nozzle, 5 is a secondary air nozzle disposed outside the secondary fuel nozzle 4, 6 and 7 are swirl vanes disposed at the tips of the secondary fuel nozzle 4 and air nozzle 5, The secondary fuel and secondary air are swirled as shown by A in Fig. 1. Reference numeral 8 denotes a low calorie fuel main supply pipe, and a primary fuel supply pipe 8A and a secondary fuel supply pipe 8B branched from this pipe are connected to the primary and secondary fuel nozzles 3 and 4, respectively. 9
is a main air supply pipe, and a primary air supply pipe 9A and a secondary air supply pipe 9B branched from this into two are connected to the primary and secondary air nozzles 2 and 5, respectively. 16 is an oxygen supply pipe connected to the primary air supply pipe 9A, and 11 is an on-off valve interposed in the middle of the primary fuel supply pipe 8A. The primary fuel nozzle 3
The fuel injection port is formed along the radial direction of the nozzle 3. Therefore, the fuel gas injected from the nozzle 3 along its radial direction is radially injected from the firing port 1 by the air flow flowing through the primary air nozzle 2, as shown by B in FIG. In the above configuration, oxygen is added from the oxygen supply pipe 16 to the primary air flowing through the primary air supply pipe 9A, and the primary air with a high oxygen concentration enters the primary air nozzle 2. Furthermore, the low-calorie fuel that enters the primary fuel nozzle 3 from the primary fuel supply pipe 8A is injected from its injection port in the radial direction of the primary fuel nozzle 3,
The primary air stream with high oxygen concentration is injected from the primary air nozzle 2 and is radially injected from the combustion opening 1 as shown by B in FIG. Further, low-calorie secondary fuel is injected from the secondary fuel nozzle 4 while being swirled as shown in FIG. 1A, and secondary air is further injected from the secondary air nozzle 5 while being swirled. As the natural limit calorific value of the fuel decreases as the oxygen concentration increases, the primary fuel can be easily ignited and its combustion can be sustained by the action of the primary air with a high oxygen concentration, and the combustion heat of the primary fuel can be increased. This heats the secondary fuel and secondary air to the required temperature and maintains stable combustion as a whole. Here, as shown in FIG. 3, by adding oxygen to the combustion supporting gas (primary air) and increasing the oxygen concentration, the self-combustion limit calorific value (Q L ) can be lowered.
Furthermore, as is clear from FIG. 4, it was found that the calorific value (Q L ') Kcal/Nm 3 on the basis of all gases is constant as shown by equation (1). Q L ′=Q L・G/G+N=K (constant) ...(1) where G: combustible gas amount (Nm 3 /h) N: combustible gas amount (Nm 3 /h) Now, primary fuel nozzle 3 If the ratio of the primary fuel supplied to the total fuel is (m), the amount of heat required to sustain combustion in the primary fuel nozzle 3 is m(Q L −Q g )≡m・ΔQ(Kcal/Nm 3 ). The amount of heat generated by this is m・Q L (Kcal/Nm 3 )
If m・Q L ≧ΔQ, combustion continues.
Therefore, it is sufficient if m≧ΔQ/Q L. However, in actual equipment, it has been found that in order to sufficiently stabilize the flame through gas mixing and heat dissipation, it is appropriate to establish the following relationship. 1.3×ΔQ/Q L ≧m≧1.1×ΔQ/Q L Next, the required amount of oxygen is obtained from equation (1): mG・Qg/mG＋A L ≧K mG＋A L ≦1/K (mG・Qg) ∴A L ≦mG・Qg/K-mG=mG (Qg/K-1) where A L : Limit amount of combustion-supporting gas (Nm 3 /h) Here, (A) is the amount of air required to burn the primary fuel (mG) ( (Nm 3 /h) (however, the air ratio of the primary burner is suitably 1.05 to 1.5), the oxygen supply amount O (Nm 3 /h) is O=21/79 (A-A L ). Instead of the swirling vanes 6 and 7 in the first embodiment, a large number of slits 13 may be formed along the substantially tangential direction on the inner wall surfaces of the nozzles 4 and 5 as shown in FIG. Embodiment) Alternatively, as shown in FIG. 6, inclined holes 14 extending along the circumferential direction may be formed in the end faces of the nozzles 4 and 5 (third embodiment). (Example) Combustion experiment of CH 4 -N 2 low calorie gas with gas calorific value of 600 Kcal/Nm 3 (calculated value) From Figure 3, the limit calorific value in air (O 2 21%) is
It is 780Kcal/ Nm3 . From this, the ratio of primary fuel (m) is 780-600/780×1.3≧m≧780-600/780×1.1 0.3≧m≧0.25. If the air ratio is 1.2, the required air amount is 1.2 x 0.557 =
0.668Nm 3 /Nm 3 gas, and from Figure 4, the self-combustion limit calorific value in all gases is 380 Kcal/Nm 3 . Limit combustion supporting gas amount A L ≦0.25×1.0×(600/380−1)=0.14The required oxygen amount is O=21/79×(0.25×1.0×0.668−1.14)=0.0270N m 3 /Nm 3 Gas2. 7%. (However, the amount of oxygen supplied relative to the total amount of combustible gas) (Experiment) Table 1 shows the results of the combustion experiment.
【表】
以上述べたごとく本発明によれば、燃料および
空気をそれぞれ一次と二次とに分け、酸素濃度の
上昇に伴つて自燃限界発熱量が低下するのに着目
して、その一次空気に酸素を添加することにより
一次燃焼安定させ、その一次燃焼火炎により二次
燃焼を接続させるものであるから、低カロリーガ
スでも確実に着火させて、その燃焼を持続させる
ことができ、しかも燃料または空気を加熱するた
めの加熱器や高カロリー燃料の添加が不要であ
り、かつ使用する酸素量も最少でよく、従来に比
ベランニングコストを下げることができる。[Table] As described above, according to the present invention, fuel and air are divided into primary and secondary, respectively, and by focusing on the fact that the limit heat value of self-combustion decreases as the oxygen concentration increases, the primary air is The primary combustion is stabilized by adding oxygen, and the primary combustion flame connects the secondary combustion, so even low-calorie gas can be reliably ignited and its combustion can be sustained. There is no need to add a heater or high-calorie fuel to heat the fuel, and the amount of oxygen used can be kept to a minimum, making it possible to reduce running costs compared to conventional systems.
第１図〜第４図は本発明の第１の実施例を示
し、第１図実線は概略縦断面図、第２図は要部の
概略正面図、第３図および第４図はO2濃度と自
燃限界発熱量の関係を示すグラフである。第５図
は本発明の第２の実施例を示す要部の斜視図、第
６図は本発明の第３の実施例を示す要部の斜視図
である。
１…焚口、２…一次空気ノズル、３…一次燃料
ノズル、４…二次燃料ノズル、５…二次空気ノズ
ル、９Ａ…一次空気供給管、１６…酸素供給管。
1 to 4 show a first embodiment of the present invention, in which the solid line in FIG. 1 is a schematic vertical sectional view, FIG. 2 is a schematic front view of the main parts, and FIGS. 3 and 4 are O 2 It is a graph showing the relationship between concentration and self-combustion limit calorific value. FIG. 5 is a perspective view of essential parts showing a second embodiment of the invention, and FIG. 6 is a perspective view of essential parts showing a third embodiment of the invention. 1... Fire opening, 2... Primary air nozzle, 3... Primary fuel nozzle, 4... Secondary fuel nozzle, 5... Secondary air nozzle, 9A... Primary air supply pipe, 16... Oxygen supply pipe.
Claims (1)
に同心状に設けた一次空気ノズル内に一次燃料ノ
ズルを同心状に挿入し、一次空気ノズルの外側に
二次燃料ノズルを配設し、該二次燃料ノズルの外
側に二次空気ノズルを配設し、一次空気ノズルに
接続された一次空気供給管に酸素供給管を接続し
たことを特徴とするガスバーナ。1. The tip of the fire mouth is formed into a conical space, the primary fuel nozzle is concentrically inserted into the primary air nozzle provided concentrically within the fire mouth, and the secondary fuel nozzle is arranged outside the primary air nozzle, A gas burner characterized in that a secondary air nozzle is disposed outside the secondary fuel nozzle, and an oxygen supply pipe is connected to a primary air supply pipe connected to the primary air nozzle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58238583A JPS60129516A (en) | 1983-12-16 | 1983-12-16 | Gas burner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58238583A JPS60129516A (en) | 1983-12-16 | 1983-12-16 | Gas burner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60129516A JPS60129516A (en) | 1985-07-10 |
| JPH0133726B2 true JPH0133726B2 (en) | 1989-07-14 |
Family
ID=17032356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58238583A Granted JPS60129516A (en) | 1983-12-16 | 1983-12-16 | Gas burner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60129516A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8256226B2 (en) * | 2009-04-23 | 2012-09-04 | General Electric Company | Radial lean direct injection burner |
| SE533731C2 (en) * | 2010-02-05 | 2010-12-14 | Linde Ag | Procedure for combustion of low-grade fuel |
| CN103196142B (en) * | 2013-04-18 | 2015-09-16 | 河北海丽特种石墨制造有限公司 | Combuster for roasting furnace |
| US20220290862A1 (en) * | 2021-03-11 | 2022-09-15 | General Electric Company | Fuel mixer |
-
1983
- 1983-12-16 JP JP58238583A patent/JPS60129516A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60129516A (en) | 1985-07-10 |
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