200928234 九、發明說明： 【發明所屬之技術領域】 相關申請案之交叉參考 5 此申請案係對於2〇〇7年9月6曰提申的臨時專利 60/967,915主張優先權，其揭示被合併於本文中以供案 發明背景 ’、考。 ❹ 10 15 ❿ 20 本發明有關大公用事業型爐具之暖機，其諸如用^ 此等爐具起動以開始其操作的生產階段之前供特別a 4 限於燃煤廠等大型發電廠產生蒸氣。. 疋—不【先前技術；J 此等大型爐具可具有大型建築物的尺寸，且其常採用 數十個分開的燃燒器來提供產生大量電力所需之熱量〜 些爐具以所有類型的燃料燃燒，包括但不限於油、瓦斯绝 煤、生質等。爐具需要一初始加熱使其内部來到所♦要的 操作溫度藉以所有燃燒器可完全燃燒而不造^燒火 (flameouts)、產生大量煙霧及其他污染物、由於過度熱I異 導致潛在損害爐具的部分、及類似現象。 ' ' 此等爐具的操作者希望具有盡量短的暖機期間，因為 在暖機階段期間將消耗昂貴燃料而不產生任何電力。 去，相較於較小的引火件燃燒器偏好採用所謂暖機搶在$ 別是對於燃煤爐具尤然，以在相對較短的時間期間中產生 足量的熱量使得爐具的生產階段可盡快開始。 雖然天然氣及油可被快速點燃且不需要長的暖機^ 間’燃煤爐具遭遇到必須充分加熱爐具藉以可點燃爐具在 5 200928234 其生產階段期間所消耗之大量的煤並將潔淨且完全地燃燒 而不釋放過度污染物之問題。亦對於主燃燒器點燃及火焰 穩疋化所使用之習知的燃燒器引火件燈係具有太低的熱量 輸出而無法在-段理想的時間期間中達成所需要的暖機， 5或者在穿過主燃燒器的空氣旁邊需具有一額外的空氣供應 件，故使其裝設過程更為複雜且昂責。 因為引火件配置於主燃燒器與周遭燃燒空氣導管之間 的相對較小環狀通道中，若要增大引火件燃燒器的尺寸以 增強其熱量輸出通常並不可行。這對於大部份工業裝設件 H)而言使得引火件尺寸限制為不大於約四至五对直徑。由於 此等尺寸限制，未使用額外空氣供應件之引火件的最大熱 量輸出一般係限於約3至7百萬BTU每小時。 使經過引火件的燃料流率增大超過該範圍將首先導致 對於經過主燃燒器的空氣流方案呈現敏感之不穩定操作。 15因為所產生的高速燃料噴注會掐滅引火件火焰，操作變得 無法令人滿意。 並且’高產能引火件需被設置於主燃燒器排放端以在 爐具内部中產生火焰並防止火焰焚燒主燃燒器。在同時， 需保護引火件不受主燃燒器火焰。為了符合這些要求，此 20等裝設件常需要複雜的機構以後續使引火件往後退出熱量 外及遠離進入燃燒空氣導管中的燃料粒子，其將耗費成 本、需要大幅維護、且容易早期失效。 因此廣泛採用未配備有主燃燒器點火之分離的暖機搶 以使爐具暖機。雖然此等搶能夠產生大量的熱量且因此即 200928234 . ㈣於燒煤公用事業型爐具亦可顯著地縮短暖機期間，其 需要有自己的燃燒空氣供應件及相對較複雜的裝設件，包 括其自己的管件、風扇、馬達、控制器、搶退回機構及類 似物，些都使得分離的暖機搶具有昂貴的裝設及維護成 5 本。 C發明内容】 發明概要 本發明改良了諸如商業發電所使用的大型爐具、特別 疋燒煤爐具當内部爐溫必須充分升高以開始爐具的生產燃 ίο燒時在爐具操作的初始啟動階段期間被預熱之方式。根據 本發明藉由將一具有遠為較高的熱量輸出之引火件燃燒器 (下文一般稱為“引火件，，)放置在燃料（譬如煤供應導管）與 周遭燃燒空氣供應導管之間的相同有限環狀通道中（過去 通常已在其中放置先前技藝的燃燒器）藉以達成此作用。本 15發明的引火件係以用於主燃燒器之燃燒空氣操作並不再需 要一用於引火件之分離的空氣供應件。引火件火焰藉由一 旋轉圖案喷射被輸送至引火件之氣態燃料的一部分而受到 點燃及穩定化，其生成經排放引火件燃料以及沿引火件穿 過主燃燒器的適量空氣之密集重新流通及混合。 20 此等引火件可提供一位於約4至50百萬BTU每小時範 圍中之熱量輸出，其遠高於在沒有額外空氣下操作的先前 技藝引火件所可達成之熱量輸出，並確保爐具的迅速加熱 及其生產階段的相對較快起動。因此可節省引火件原本使 用但未產生可用蒸氣或電力之顯著燃料量。 7 200928234 本發明提供一用於預熱爐具之方法及裝置，特別是具 有常以在爐具操作暖機階段期間難以點燃的煤操作之許多 燃燒器之大公用事業型爐具。一般而言，這包含一主生產 燃燒器，其包括一用於將一譬如煤等燃料導引至—爐具的 5 一内部中之第一導管。一空氣導管係圍繞煤導管以界定_ 進入爐具中之環狀燃燒空氣通道，其中使煤及燃燒空氣在 爐具操作的生產階段期間被混合及點燃。 一引火件喷嘴被定位於主燃燒器的空氣通道中以使喷 嘴的一下游端緊鄰於燃燒器的下游端。喷嘴被一管狀罩套 10 所圍繞，其具有一緊鄰於喷嘴下游端的開放下游端及一上 游端。藉由將一諸如板等流抑制器放置在罩套上游端上方 同時准許空氣經由罩套與板之間所形成的一間隙進入罩套 來防止流過用於空氣的主燃燒器之空氣直接地進入罩套。 一諸如氣體等經加壓流體燃料的一相對較小部分係以 15與管狀罩套内側之有限空間内的可燃燒數量相耩之一速率 流過位居管狀罩奢内側之喷嘴中的點燃器孔口。以便利將 空氣挾帶通過罩套之角度來導引罩套内側的燃料氣體喷 注。引火件氣體的一主要部分自主引火件孔口一緊鄰於罩 套之噴嘴的一下游端部分中之複數個隔開的引火件孔口 一 20 被排放。來自主弓丨火件孔口的燃料喷注係被定向成可使所 發射的燃料噴注在下游方向呈斜角地發散且相對於引火件 喷嘴縱轴線具有〆切線流組份。當自主引火件孔口排放的 燃料噴注通過罩套下游端附近’其亦便利空氣流通過罩套。 管狀罩套内側的黠燃器孔口所發射之燃料係混合於穿 200928234 . 過罩套之空氣且被點燃以產生一傳播過罩套下游端之點燃 器火焰。點燃器火焰則點燃來自主引火件孔口的燃料及穿 過主燃燒器的空氣之混合物以產生一延伸至爐具内部中且 予以加熱之引火件火焰。引火件火焰的部分及其成份氣體 5係自爐具内側往後重新流通朝向喷嘴，同時火焰整體相對 於噴嘴軸線旋轉以維持一穩定引火件火焰。 將高熱量輸出引火件燃燒器放置在主燃燒器的燃燒空 氣導管内側尚未能成功之一原因係在於：除非引火件有其 ® 自己的空氣供應件及控制器，由於不利的燃料對於空氣比 1〇值，流過導管之空氣容積可能實質地改變故以一固定速率 流動的引火件燃料常無法點燃、或維持火焰。因為進入罩 套的空氣量實質地與罩套内侧輸送經過點燃器孔口之燃料 成正比且由於其上游流抑制器有效地屏蔽住引火件燃料不 受到流經導管的高速空氣之效應而只受到經過導管的流量 15小程度地影響’藉由本發明可克服此問題。罩套形成一小 燃燒室，其中一相對較少量的引火件燃料被初始地點燃以 ® 形成在一下游方向中傳播過罩套下游端之點燃器火焰，其 中引火件燃料的主要部分經由經適當定位及定向之引火件 孔口被排放。 20 包括有早先所知^及的流轉向器之罩套亦有效地屏蔽住 諸如罩套内側的火花電極等敏感組件不受到主引火件火焰 及爐具之熱量，其可容許操作燃燒器而不必使引火件退回 至燃燒器中。 此外，為了維持一引火件火焰，其必須為穩定且保持 9 200928234 錨固至噴嘴。高熱量輸出引火件係需要高達500-1500呎/秒 之經過燃燒器孔口的高燃料速度。此等高燃料噴注速度係 導致不良的火焰不穩定度，根據本發明藉由對於噴嘴下游 5 10 15 的引火件火焰賦予旋轉以便利建立噴嘴下游的一重新流通 流來顯著地降低或消除此不穩定度。為了達成此旋轉，： 下文詳述，引火件孔口的軸線相對於引火件軸線呈切線地 偏移。噴注的切線餘份補由沿嘴嘴放£由於前述空間 限制無法放置在該處之相對較大的旋轉器來提供常見先驴 技藝燃燒器所獲得之旋轉結果。 别 本發明的另 更要優點係在於：因為所發射揪料 積變動時其速度將對應地變動、轉而與自點燃純口 ^ 射的燃料速度呈反㈣降低或升高罩套内側的燃料壓力， 進入罩套内部之錢量係依據罩套内侧的點燃器孔口 射之燃料量使其自身作觀。藉由降低的壓力，來自^ 導管的較多空氣被吸人罩套内部中藉以轉燃料與罩= 的空氣之間的-近似理想配比平衡。這即便在—暫時 事件中仍確未中斷的點燃器火如維持主引火^ 培。由於自喷嘴的點燃器孔口發射較少燃料且罩套 壓力對應地升高，抽人罩套中的空氣量係對應地降低。 因此，本發明的引火件燃燒器相對較便宜，原因在於 其不具有活動元件且不需要内部或外部控制器。 、 本發明達成之另-優點係在於：因為弓^件位居 導管内側，狀件魏轉屏蔽衫高溫錢體、塵土及 板子對於爐具内部之研磨性/腐#性/污染影響，其降低了維 20 ❹200928234 IX. INSTRUCTIONS: [Technical field to which the invention pertains] Cross-Reference to Related Applications 5 This application claims priority to Provisional Patent No. 60/967,915, filed on Sep. 6, 2007. In this article, the background of the invention is given, and the test. ❹ 10 15 ❿ 20 The warm-up machine of the present invention relates to a large utility-type stove, which is steamed to a large power plant such as a coal-fired power plant before the production stage, such as starting with a stove to start its operation.疋—Not [previous technology; J. These large stoves can have the size of large buildings, and they often use dozens of separate burners to provide the heat needed to generate a large amount of electricity. Fuel combustion, including but not limited to oil, gas, coal, and so on. The stove requires an initial heating to bring the interior to the desired operating temperature so that all burners can be completely burned without producing flameouts, generating a large amount of smoke and other contaminants, and potentially damaging the furnace due to excessive heat. Part, and similar phenomena. The operator of these stoves wants to have as short a warm-up period as it will consume expensive fuel during the warm-up phase without generating any electricity. Going, compared to the smaller fire-fighting burners, prefers to use so-called warm-ups, especially for coal-fired stoves, to generate enough heat in a relatively short period of time to make the stove's production stage Can start as soon as possible. Although natural gas and oil can be ignited quickly and do not require a long warming machine, the 'coal burning stove' encounters the need to fully heat the stove to ignite the large amount of coal consumed during the production phase of 5 200928234 and will be clean And the problem of burning completely without releasing excessive contaminants. Also known as burner ignition components for primary burner ignition and flame stabilization have too low a heat output to achieve the required warm-up during the desired period of time, 5 or in wear. An additional air supply is required next to the air passing through the main burner, making the installation process more complicated and cumbersome. Since the igniter is disposed in a relatively small annular passage between the main burner and the surrounding combustion air duct, it is generally not feasible to increase the size of the igniter burner to enhance its heat output. This limits the size of the pilot to no more than about four to five pairs of diameters for most industrial installations H). Due to these size limitations, the maximum heat output of a igniter that does not use an additional air supply is typically limited to about 3 to 7 million BTU per hour. Increasing the fuel flow rate through the pilot element beyond this range will firstly result in a sensitive, unstable operation for the air flow scheme through the main burner. 15 Because the high-speed fuel injection produced will extinguish the flame of the ignition, the operation becomes unsatisfactory. And 'high-capacity fire-fighting components need to be placed at the discharge end of the main burner to create a flame inside the oven and prevent the flame from burning the main burner. At the same time, it is necessary to protect the pilot from the main burner flame. In order to meet these requirements, the 20-piece assembly often requires a complicated mechanism to subsequently withdraw the pilot member from the heat and away from the fuel particles entering the combustion air conduit, which is costly, requires significant maintenance, and is prone to early failure. . Therefore, the warming machine that is not equipped with the separation of the main burner ignition is widely used to warm the stove. Although these rushes can generate a large amount of heat and therefore 200928234. (4) The coal-fired utility type stove can also significantly shorten the warm-up period, which requires its own combustion air supply parts and relatively complicated installation parts. Including its own fittings, fans, motors, controllers, retracting mechanisms and the like, all of which make the separate warm-ups expensive and easy to install and maintain. C SUMMARY OF THE INVENTION The present invention improves the large-scale stoves used in commercial power generation, especially the coal-fired stoves, when the internal furnace temperature must be sufficiently raised to start the production of the stoves. The way to be warmed up during the start-up phase. According to the present invention, a igniter burner having a much higher heat output (hereinafter generally referred to as a "fire igniter") is placed between the fuel (such as a coal supply conduit) and the surrounding combustion air supply conduit. This effect is achieved in a finite annular passage (a burner in which the prior art has been placed in the past). The fire-fighting member of the present invention is operated with combustion air for the main burner and no longer requires a fire-fighting member. a separate air supply member. The igniter flame is ignited and stabilized by a rotating pattern jet that is delivered to a portion of the gaseous fuel of the igniter, which generates a proper amount of fuel that passes through the igniter and passes through the main burner along the igniter Intensive recirculation and mixing of air. 20 These pilots provide a heat output in the range of approximately 4 to 50 million BTU per hour, which is much higher than that of prior art ignitions operating without additional air. The heat output and ensure the rapid heating of the stove and the relatively quick start of the production phase, thus saving the original use of the ignition but not producing A significant amount of fuel that can be used with steam or electricity. 7 200928234 The present invention provides a method and apparatus for preheating a furnace, particularly a large number of burners that are often operated with coal that is difficult to ignite during the warm-up phase of the furnace operation. Utility-type stove. In general, this includes a main production burner that includes a first conduit for directing a fuel such as coal to the interior of the furnace. The coal conduit defines an annular combustion air passage into the furnace, wherein the coal and combustion air are mixed and ignited during the production phase of the furnace operation. A pilot nozzle is positioned in the air passage of the main burner A downstream end of the nozzle is adjacent to the downstream end of the burner. The nozzle is surrounded by a tubular casing 10 having an open downstream end and an upstream end adjacent the downstream end of the nozzle. By means of a flow suppressor such as a plate Placed over the upstream end of the shroud while permitting air to enter the shroud via a gap formed between the shroud and the shroud to prevent air flow through the main burner for air directly Into a hood. A relatively small portion of the pressurized fluid fuel, such as a gas, flows through the nozzle located inside the tubular hood at a rate 15 that is comparable to the flammable quantity in the limited space inside the tubular hood. The igniter aperture of the illuminator guides the fuel gas injection inside the hood so as to facilitate the passage of the air entanglement through the cover. A major portion of the igniter gas is adjacent to the nozzle of the hood. A plurality of spaced firefighter orifices 20 in a downstream end portion are discharged. The fuel injection system from the orifice of the primary bow firearm is oriented such that the injected fuel is injected at an oblique angle in the downstream direction Diverging and having a tangent line flow component with respect to the longitudinal axis of the pilot member nozzle. When the fuel is discharged through the orifice of the autonomous pilot member through the downstream end of the cover, it also facilitates air flow through the cover. The fuel emitted by the burner orifice is mixed with the air passing through the shroud and ignited to create an igniter flame that propagates through the downstream end of the shroud. The igniter flame ignites the mixture of fuel from the orifice of the main pilot and the air passing through the main burner to create a pilot flame that extends into the interior of the oven and is heated. The portion of the pilot flame and its component gas 5 are recirculated from the inside of the oven toward the nozzle while the flame as a whole rotates relative to the nozzle axis to maintain a stable pilot flame. One reason for placing a high-heat output igniter burner inside the combustion air duct of the main burner is that unless the igniter has its own air supply and controller, due to the unfavorable fuel-to-air ratio At 1 turn, the volume of air flowing through the conduit may vary substantially so that the pilot fuel that flows at a fixed rate often fails to ignite or maintain the flame. Because the amount of air entering the shroud is substantially proportional to the fuel transported through the igniter orifice on the inside of the shroud and is only affected by the effect of its upstream flow suppressor effectively shielding the pilot fuel from the high velocity air flowing through the conduit The flow through the conduit 15 is affected to a small extent 'by the present invention overcoming this problem. The shroud forms a small combustion chamber in which a relatively small amount of pilot fuel is initially ignited to form an igniter flame that propagates through the downstream end of the shroud in a downstream direction, wherein a major portion of the pilot fuel passes through The appropriately positioned and oriented firing element orifices are discharged. 20 Included with the previously known flow diverter cover also effectively shields sensitive components such as spark electrodes inside the cover from heat from the main pilot flame and the oven, which allows operation of the burner without having to Return the pilot to the burner. In addition, in order to maintain a pilot flame, it must be stable and maintained at 9 200928234 anchored to the nozzle. High heat output pilots require high fuel velocities through the burner orifices of up to 500-1500 mph. Such high fuel injection rates result in poor flame instability, which is substantially reduced or eliminated in accordance with the present invention by imparting rotation to the igniter flame downstream of the nozzle 5 10 15 to facilitate establishing a recirculation flow downstream of the nozzle. Unstable. To achieve this rotation, the axis of the firing element orifice is tangentially offset relative to the firing element axis, as detailed below. The tangential allowance of the jet is provided by the relatively large rotator that is placed along the mouth of the mouth due to the aforementioned space constraints to provide the rotation results obtained by the conventional ram art burner. Another advantage of the present invention is that since the velocity of the emitted helium product changes, the speed will correspondingly change, and in turn, the fuel velocity of the self-igniting pure port will be reversed (four) to reduce or increase the fuel inside the cover. Pressure, the amount of money entering the inside of the hood is based on the amount of fuel injected from the igniter orifice on the inside of the hood. By the reduced pressure, more air from the conduit is absorbed by the inside of the casing to balance the approximately stoichiometric ratio between the fuel and the air of the hood =. This is even if the igniter fire is still uninterrupted in the temporary event, such as maintaining the main fire. Since less fuel is emitted from the igniter orifice of the nozzle and the jacket pressure is correspondingly increased, the amount of air in the hood is correspondingly reduced. Thus, the igniter burner of the present invention is relatively inexpensive because it does not have moving elements and does not require an internal or external controller. The other advantage achieved by the present invention is that since the bow member is located inside the duct, the high-speed body, dust and board of the piece of the Wei-turned shield are affected by the abrasiveness/corrosion/contamination of the interior of the stove, which is reduced. Dimension 20 ❹
200928234 護成本且延長燃燒器壽命。尚且， 燒器不需要外部控㈣、分㈣火件燃 其可在工業燃燒器的空氣導管路一 相對較大。這轉而可以增加燃燒 間中製成 ^ ^ , lik “、、篁翰出且因此縮短 期間，其皆降低了用於爐具暖機及敎件燃燒 器維護之操作成本。 圖式簡單說明 第1圖示意地顯示用於驅動如大型發電廠中所用的一 蒸氣輪機之一大型譬如公用事業型爐具配置； 第2圖為經過一燃燒器的示意橫剖視圖，其包括一用於 裝設在第1圖所示的爐具中之根據本發明所構成的高熱量 輸出引火件； 第3A及3B圖為本發明的引火件之剖視圖； 第4圖為第1圖所示的主燃燒器及引火件之示意正視 15 圖； 第5圖示意地顯示根據本發明之一引火件火焰重新流 通區的形態； 第6圖為第3A及3B圖所示之引火件的一空氣流限制器 板的端視圖； 20 第7圖為一用於防止燃燒空氣直接地流入一圍繞弓丨火 件的罩套中之空氣流直化器的端視圖； 第8A及8B圖分別為第3A及3B圖所示之引火件的噴嘴 之端視圖及側視圖。 【實施方式3 11 200928234 較佳實施例之詳細說明 第1圖示意地顯示一大型發電裝設件’其譬如常供公共 公用事業公司用來發電予公眾。裝設件具有至少一大型公 用事業型爐具2及許多個、通常數十個主生產燃燒器4，其 5延伸經過爐具的至少一壁6進入其内部8中。此等爐具可以 且正以全部種類的燃料作燃燒，最常採用油、煤及天然氣。 本發明對於爐具燃燒通常磨成細粉或塵的煤具有特定（但 不唯獨）的可適用性。如熟知，爐具内部上的燃料所產生之 熱量係產生可用來驅動一輪機12之蒸氣丨〇，輪機12可譬如 10 連接至一發電機（未圖不）。來自爐具的排氣通常係在被適當 地清理及/或清除以限制大氣污染之後經由一堆積體14釋 放至大氣。 第2圖示意地顯示使用安裝有一主生產燃燒器4且操作 性延伸經過一爐具璧6之本發明，其構成為可燒煤、通常為 15細微地研磨或粉样的煤。其具有一煤供應源18及一煤供應 導管20，其中粉末狀、經粉碎或類似的煤在一下游方向中 流至一排放端22，其可包括一旋轉器或轉向器24以經由爐 具壁ό中之一往外擴張的燃燒器喉％將煤排放至爐具内部8 中。主燃燒器4進〆步具有一同心地圍繞煤供應導管20之燃 20燒空氣供應導管32以在煤供應導管與燃燒空氣導管之間形 成一環狀燃燒空氟通道34。操作期間，燒煤（或其他燃料） 所需要的燃燒空氣係自燃燒器的下游端22被排放至爐具内 部中。主燃燒器 < 包括一補充性燃料供應管28，其同軸地 運行經過主燃燒器的（的水平部分）且具有一燃料排放端蓋 200928234 30，其可譬如當需要較大熱量輸出時在電力的高峰需求其 間中用來自燒油或瓦斯(gas)提供額外熱量。 ，月 此等主燃燒器的構造及操作係由一般熟習該技 暸解因而此處不作進一步描述。 斤 5 燃、燒器裝設件4包括一引火件燃燒找，其根據本發明 構成為可在爐具内部中引發燃燒且在爐具操作 J ps*200928234 Protects costs and extends burner life. Moreover, the burner does not require external control (4), sub-(four) fire parts, and the air conduit of the industrial burner can be relatively large. This in turn can increase the manufacturing cost of the ^ ^ , lik ", and the han" and thus shorten the period in the combustion chamber, which reduces the operating cost for the furnace warming and the maintenance of the burner. 1 is a schematic view showing a large-scale utility model such as a utility type for driving a steam turbine used in a large power plant; FIG. 2 is a schematic cross-sectional view through a burner, which includes a device for mounting a high-heat output fire-extinguishing member constructed according to the present invention in the present invention shown in Fig. 1; Figs. 3A and 3B are cross-sectional views of the fire-extinguishing member of the present invention; and Fig. 4 is a main burner shown in Fig. 1 and Figure 15 is a schematic view showing the form of the flame recirculation zone of the igniter according to the present invention; and Fig. 6 is an air flow restrictor plate of the igniter shown in Figs. 3A and 3B. End view; 20 Figure 7 is an end view of an air flow straightener for preventing combustion air from flowing directly into a shroud surrounding the bow fire; Figures 8A and 8B are Figures 3A and 3B, respectively. An end view and a side view of the nozzle of the ignition element. [Embodiment 3 11 200928234 DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Fig. 1 schematically shows a large power generating assembly 'which is used by public utility companies to generate electricity to the public as usual. The mounting has at least one large utility type Furnace 2 and a plurality of, usually dozens of, main production burners 4, 5 extending through at least one wall 6 of the oven into its interior 8. These stoves can and are being burned with all types of fuel, most Oil, coal and natural gas are often used. The present invention has specific (but not exclusively) applicability to the burning of coal which is usually ground into fine dust or dust. As is well known, the heat generated by the fuel inside the furnace is A steam enthalpy is generated that can be used to drive a turbine 12, which can be connected, for example, to a generator (not shown). The exhaust from the furnace is typically after being properly cleaned and/or purged to limit atmospheric pollution. Released to the atmosphere via a stack 14. Figure 2 is a schematic illustration of the invention using a main production burner 4 and operatively extending through a grate 6 which is constructed to burn coal, typically 15 subtle Grinded or powdered coal having a coal supply source 18 and a coal supply conduit 20, wherein the powdered, pulverized or similar coal flows in a downstream direction to a discharge end 22, which may include a rotator or turn The machine 24 discharges the coal into the interior 8 of the furnace with a burner throat % expanded outwardly through one of the grate walls. The main burner 4 has a combustion air supply conduit concentrically surrounding the coal supply conduit 20 32 to form an annular combustion empty fluorine passage 34 between the coal supply conduit and the combustion air conduit. During operation, the combustion air required for burning coal (or other fuel) is discharged from the downstream end 22 of the burner to the furnace. In the interior, the main burner < includes a supplemental fuel supply tube 28 that runs coaxially through the (horizontal portion) of the main burner and has a fuel discharge end cap 200928234 30, such as when a large heat output is required Additional heat from the oil or gas is provided during peak demand for electricity. The construction and operation of these main burners are generally familiar to the art and are therefore not further described herein. The fuel-burning burner assembly 4 includes a fire-fighting member for combustion, which is constructed according to the present invention to initiate combustion in the interior of the oven and to operate in the oven J ps*
段期間將爐具内部予以暖機直到爐具内部抵達所需要π产 之後主燃燒器16可燃燒為止以維持穩定且完全的煤（或= 他燃料)燃燒。引火件具有一進給管38, _諸如天然氣 1〇體燃料經由其自一適當來源（未圖示）被供應至—引火件噴 嘴40。喷嘴被-管狀屏蔽件或罩套42所圍繞，其端點為開 啟，且提供-點燃器、譬如—電火花點燃器44以點燃燃料， 如下文進一步描述。 第3Α、Β及4圖更詳細地顯示本發明的引火件燃燒器。 15喷嘴40係包括且附接至進給管38的一下游端，具有一排放 (或下游)端50’且具有複數個可供引火件燃料嘴注自其流動 之引火件燃料排放孔口 52。引火件燃料喷注相對於引火件 燃燒器的縱轴線以·—歪斜角度被排放，且其額外地對於引 火件軸線呈切線狀，如下文進一步描述。 20 管狀罩套42分別具有開放的上游及下游端66、68。一 流直化器及調控器70(亦顯示於第7圖）被定位於罩套的上游 端内側且延伸入罩套中某段距離。一燃料進給管38及一點 燃器支撐管76分別延伸至罩套42中。流直化器包括複數個 肋80，其平行於點燃器燃燒器軸線96放置在罩套42與燃料 13 200928234 進給管38之間。肋界定延伸於引火件的軸向方向中之多重 的流直化通道82。流動於肋80之間的空氣係變成被更好地 定向於引火件的軸向方向中’ 一種例如當流過通道34的空 氣相對於引火件軸線處於一歪斜角度時將特別有用之特徵 5 結構。 引火件36進一步配合於一與罩套42的上游端66分開之 減振器板84(亦顯示於第6圖）。減振器包括一圍繞引火件燃 料進給管38且可沿其可滑地移動之管狀轂86。相對的轂86 係為一供點燃器支撐管76延伸經過之U形切口 88。 10 可藉由使板沿著引火件燃燒器的燃料供應管38移動來 調整減振器板84相對於罩套上游端之軸向位置以改變罩套 上游端與減振器板間之一間隙90的寬度以容納燃料的特定 特徵及提供經過燃燒器32之一範圍的空氣流。 點燃器支樓管76的下游端終止於一附接至管狀罩套42 15内側之峭壁體部％(第3A、B圖）。一電子點燃器舛放置在支 撐管76内側且大約齊平於峭壁體部92。在面對流之側上， 峭壁體部92被定形為具有一斜坡93藉以消除位於點燃器94 上游的流之停滯區域。用於電子點燃器之適當硬體及配線 (未圖示）係延伸經過點燃器管76來到一點燃器控制器（未圖 20 示）。 本發明的一目前較佳實施例中，引火件噴 成為-附接至燃料進給管38下游端且具有排列於在喷嘴袖 向方向分開的複數列譬如兩列52A、52时的多數健料排 放孔口 52之蓋’如第3B圖所示。各孔口相對於引火件燃燒 200928234 . 器軸線96以位於約20。至80。範圍、較佳約35。至75。範圍且目 前較佳實施例中約為60。角度的一角度α發散於一下游方向 中（如第8Β圖所示）。 此外，各孔口 52排列為使其中心線98相對於一半徑線 5 1〇〇偏移，其原點位於喷嘴的中心96所以各孔口亦相對於此 中心呈切線，如第8Α圖所示。這造成位於喷嘴50尾跡中之 燃料流及火焰以類比於習知旋轉器的方式作旋轉且儘管自 孔口所發射的高速燃料喷注仍將火焰錨固至引火件。 一目前較佳實施例中，引火件喷嘴4〇額外地包括相對 10較小直控的中心孔102。使用中，氣體係流過中心孔藉以冷 卻喷嘴中心。 參照第4圖，引火件噴嘴4〇及點燃器44相對於管狀罩套 42轴線呈偏移以使引火件噴嘴相鄰於罩套42的一側，藉以 界定引火件喷嘴的周邊及罩套的相對壁之間的一經放大空 15間104，在其中產生一初始點燃器火焰，如下文進一步描 述。第4圖的箭頭1〇6顯示燃料喷注53的切線性定位及定向 (顯示於第5圖）。 現在描述用於起動一冷爐具之引火件36的操作，燃燒 空氣係在一下游方向中流過燃燒器32的環狀通道34經過管 20狀罩套42然後進入爐具空間8中。用於引火件之氣體係流過 進給官38來到孔口 46及引火件喷嘴4〇。孔口46的尺寸可使 得燃料的一相對較小部分經由進給管38中的點燃器孔口46 離開’點燃器孔口 46被定向為可將所產生的燃料喷注導引 至罩套内側的經放大空間1〇4中及點燃器44附近。在同時， 15 200928234 來自主燃燒器的環狀通道34之空氣係經由罩套的上游端與 減振器板84之間的間隙90進入罩套42内部。流直化器70令 入進空氣變直使其概括流動於引火件軸線方向中且混合於 來自點燃器孔口 46之燃料。所產生的混合物被火花點燃器 5 94點燃以在經放大空間1〇4中形成一點燃器火焰47，其在— 下游方向中傳播經過罩套的下游端68，如第5圖所示。 用於預熱爐具之燃料體塊係經由噴嘴40中的孔口 52射 出成為在下游方向往外發散的氣體喷注53故使所射出的燃 料變成混合於流過主燃燒器的環狀通道34之燃燒空氣。此 10 混合物係被離開用於維持主引火件火焰5 4之罩套的下游端 之點燃器火焰47所點燃。 通常流過環狀通道34之燃燒空氣量係依據方案的操作 需求而定並實質地獨立於引火件燃燒器操作。可基於操作 性理由來改變引火件需要燃料之速率。為了維持點燃器火 15焰47 ’進給至燃燒器的空氣量必須反映點燃器孔口所射出 的燃料量以在峭壁體部92的下游端上維持罩套42内側的— 整體可焰燃混合物。 為了妥當地控制進入罩套42中的空氣流，減振器板84 係陴絕流經環狀空間34直接進入罩套中之燃燒空氣。取而 20代之，燃燒空氣必須先在一徑向方向（相對於罩套42)自環形 通道流經間隙9 〇而然後被重新導引經過流直化器7 〇進入罩 套内部，故盡量降低經過通道34的空氣流速度對於進入罩 套42的空氣流量之效應。可藉由沿著進給管％移動減振器 板84且括其凸緣86來調整減振器板84相對於上游罩套端 16 200928234 1軸向位置以設定對於間__ t寬度以准許充分空氣 抓進入罩套中同時防止環狀通道中之燃燒空氣流的變異實 吳地影響經過罩套的空氣流率。During the period, the interior of the oven is warmed up until the interior of the furnace reaches the required π production and the main burner 16 can be burned to maintain a stable and complete coal (or = other fuel) combustion. The igniter has a feed tube 38, such as natural gas 1 steroid fuel being supplied thereto via a suitable source (not shown) to the igniter nozzle 40. The nozzle is surrounded by a tubular shield or shroud 42 that has an open end and provides an igniter, such as an electric spark igniter 44, to ignite the fuel, as described further below. Figures 3, 4 and 4 show the fire burner burner of the present invention in more detail. The nozzle 40 is comprised and attached to a downstream end of the feed tube 38, having a discharge (or downstream) end 50' and having a plurality of igniter fuel discharge orifices 52 from which the pilot fuel nozzle is injected. . The pilot fuel injection is discharged at an oblique angle relative to the longitudinal axis of the pilot burner and is additionally tangential to the axis of the pilot, as further described below. The tubular casing 42 has open upstream and downstream ends 66, 68, respectively. A flow straightener and governor 70 (also shown in Figure 7) is positioned inside the upstream end of the shroud and extends a certain distance into the shroud. A fuel feed pipe 38 and a single burner support pipe 76 extend into the shroud 42, respectively. The flow straightener includes a plurality of ribs 80 that are placed parallel to the igniter burner axis 96 between the shroud 42 and the fuel 13 200928234 feed tube 38. The ribs define a plurality of straightening passages 82 that extend in the axial direction of the firing elements. The air flowing between the ribs 80 becomes better oriented in the axial direction of the firing element. A feature that is particularly useful when the air flowing through the passage 34 is at an oblique angle with respect to the axis of the firing element. . The igniter 36 is further adapted to a damper plate 84 (also shown in Figure 6) that is separate from the upstream end 66 of the shroud 42. The damper includes a tubular hub 86 that surrounds the igniter fuel feed tube 38 and is slidably movable therewith. The opposite hub 86 is a U-shaped slit 88 through which the igniter support tube 76 extends. 10 Adjusting the axial position of the damper plate 84 relative to the upstream end of the shroud by moving the plate along the fuel supply tube 38 of the igniter burner to change a gap between the upstream end of the shroud and the damper plate The width of 90 is to accommodate specific characteristics of the fuel and to provide a flow of air through a range of burners 32. The downstream end of the igniter branch pipe 76 terminates in a % of the cliff body attached to the inside of the tubular shroud 42 15 (Fig. 3A, B). An electronic igniter 舛 is placed inside the support tube 76 and is approximately flush with the cliff body 92. On the side facing the flow, the cliff body 92 is shaped to have a ramp 93 to eliminate stagnant areas of the flow upstream of the igniter 94. Appropriate hardware and wiring (not shown) for the electronic igniter extends through the igniter tube 76 to an igniter controller (not shown in Figure 20). In a presently preferred embodiment of the invention, the igniter is sprayed into a plurality of condiments that are attached to the downstream end of the fuel feed tube 38 and have a plurality of columns, such as two columns 52A, 52, that are arranged in the direction of the sleeve sleeve. The cover of the discharge orifice 52 is as shown in Fig. 3B. Each orifice is fired relative to the igniter. 200928234. The axis 96 is located at approximately 20. To 80. The range is preferably about 35. To 75. The range and currently preferred embodiment is about 60. An angle α of the angle diverge in a downstream direction (as shown in Fig. 8). In addition, each of the apertures 52 is arranged such that its centerline 98 is offset relative to a radius line 5 1 ,, the origin of which is located at the center 96 of the nozzle, so that the apertures are also tangential to the center, as shown in Fig. 8 Show. This causes the fuel flow and flame located in the wake of the nozzle 50 to rotate in a manner analogous to conventional rotators and although the high velocity fuel injection from the orifice still anchors the flame to the igniter. In a presently preferred embodiment, the igniter nozzle 4 〇 additionally includes a central bore 102 that is relatively small and directly controlled relative to 10. In use, the gas system flows through the center hole to cool the center of the nozzle. Referring to Figure 4, the igniter nozzle 4 〇 and the igniter 44 are offset relative to the axis of the tubular shroud 42 such that the igniter nozzle is adjacent to one side of the shroud 42 to define the perimeter of the igniter nozzle and the shroud An enlarged space between the opposing walls 15 is 104, in which an initial igniter flame is generated, as further described below. The arrow 1〇6 of Fig. 4 shows the tangential positioning and orientation of the fuel injection 53 (shown in Fig. 5). The operation of the igniter 36 for starting a cold cooker is now described. The combustion air is passed through the tube-like shroud 42 and then into the hob space 8 in a downstream direction through the annular passage 34 of the combustor 32. The gas system for the igniter is passed through the feed officer 38 to the orifice 46 and the pilot nozzle 4 〇. The aperture 46 is sized such that a relatively small portion of the fuel exits through the igniter aperture 46 in the feed tube 38. The igniter aperture 46 is oriented to direct the generated fuel injection to the inside of the casing. The enlarged space is 1 〇 4 and near the igniter 44. At the same time, 15 200928234 air from the annular passage 34 of the main burner enters the interior of the shroud 42 via the gap 90 between the upstream end of the shroud and the damper plate 84. The straightener 70 straightens the incoming air to flow generally in the direction of the pilot axis and is mixed with fuel from the igniter orifice 46. The resulting mixture is ignited by spark igniter 5 94 to form an igniter flame 47 in the enlarged space 1 〇 4 which propagates through the downstream end 68 of the shroud in the downstream direction, as shown in FIG. The fuel body block for preheating the furnace is injected through the orifice 52 in the nozzle 40 to be a gas injection 53 that is diverged outward in the downstream direction, so that the injected fuel is mixed into the annular passage 34 flowing through the main burner. Burning air. This 10 mixture is ignited by an igniter flame 47 that exits the downstream end of the shroud for maintaining the main pilot flame 54. The amount of combustion air typically flowing through the annular passage 34 is dependent upon the operational requirements of the scheme and is substantially independent of the pilot burner operation. The rate at which the pilot is required for fuel can be varied based on operational reasons. In order to maintain the igniter fire 15 flame 47' the amount of air fed to the burner must reflect the amount of fuel injected by the igniter orifice to maintain the inside of the casing 42 at the downstream end of the cliff body 92 - the overall flame-retardant mixture . In order to properly control the flow of air into the shroud 42, the damper plate 84 is vented through the annular space 34 directly into the combustion air in the shroud. In the 20th generation, the combustion air must first flow from the annular passage through the gap 9 in a radial direction (relative to the cover 42) and then be redirected through the flow straightener 7 into the cover, so try to The effect of the air flow rate through passage 34 on the flow of air entering the shroud 42 is reduced. The axial position of the damper plate 84 relative to the upstream shroud end 16 200928234 1 can be adjusted by moving the damper plate 84 along the feed tube % and including its flange 86 to set the width for the __t to permit Sufficient air is captured into the shroud while preventing variations in the flow of combustion air in the annular passage that affect the air flow rate through the shroud.
使用中’減振器板的位置通常不變。然而因為當經過 5點燃=孔口的氣體速度增大或減小時經由間隙％進入草套 中的空氣攝入係以經過點燃器孔口 46之氣體流率的函數自 動地變動，罩套内側的壓力係與壓力變化呈反向變化。經 過點燃器孔口的氣體速度之增加將降低罩套中的壓力，其 造成經過間隙90進入罩套中之空氣流率增加且反之亦然。、 10此空氣流變異係自動地發生且不需要任何類型的控制。 。為此’本發明的引火件燃燒器係自我調節並維持點燃 器及弓丨火件火焰47、54而無關乎燃燒空氣流率的變化，同 時可穩定化引火件火焰54且將其錯固至引火件燃燒器的端 點。這確保了引火件燃燒器的-連續、未中斷、自我調節 15操作以盡量快速地完全加熱爐具。 通常較佳對於引火件燃燒器操作的歷程維持罩套似 側的點燃器火焰47，所以在引火件所產生的主火焰變成# 滅之事件中，其立即被引火件火焰重新點燃。 第5圖示意地顯示引火件燃燒器％下游所產生之主引 20 ^件火焰54及其與自罩套下游端68延伸的引火件火焰歡 交互作用。如較早所述，自引火件噴嘴辦孔叫所散發 之燃料喷注53係被往外導引且遠離引火件轴線％進入爐具 内部中H成所需要的熱量輸人，氣態燃料喷注53具 有通常介於500至1500呎/秒之間的速度。這些高速度亦幫 17 200928234 助燃料噴注混合於充足空氣以有效率地燃燒經由引火件所 - 輸送之大量燃料氣體。 . 為了經由高速燃料噴注53確保來自火焰47的可靠火焰 傳播，必須在點燃燃料所需要的歷程中達成且維持緊鄰於 5喷嘴40之流的實質部份中之可焰燃混合物。藉由將孔口 52 以彼此軸向分隔之交錯的兩列或更多列沿喷嘴4 〇圓周放置 且藉由將旋除自引火件孔σ52發射的燃料之孔口作切線式 - 定位來達成此作用。各列中，孔口一般係分隔有孔口直徑 - 的約一至二倍。—目前較佳實施例巾，孔口之間的間隔近 ❿ 10 似為噴嘴直徑的兩倍。 對於火焰54穩定化而言，經由氣體喷注53的火焰傳播 作用並不足夠《藉由孔口的切線式定位所造成被自引火件 孔口 5 2發射的燃料旋轉所增強之流重新流通5 S係使得引火 件具有有效率且可靠的操作。 15 如熟習該技藝者熟知，被賦予燃料喷注形成一往前導 引的螺旋動作之-切線性組份係便利形成氣態重新流通 案。螺旋效應愈大，則重新流通愈好。氣體的重新流通组 〇 伤係為根據下列公柄所謂“舰數”s之-函數：The position of the 'damper plate' in use is usually the same. However, because the air intake into the straw through the gap % automatically increases as the velocity of the gas passing through the 5 ignition = orifice increases or decreases, as a function of the gas flow rate through the igniter orifice 46, the inside of the casing The pressure system changes inversely with the pressure change. An increase in the velocity of the gas passing through the orifice of the igniter will reduce the pressure in the shroud which causes an increase in the air flow rate through the gap 90 into the shroud and vice versa. 10 This airflow variation occurs automatically and does not require any type of control. . To this end, the igniter burner of the present invention self-adjusts and maintains the igniter and bow fire flames 47, 54 regardless of changes in the combustion air flow rate, while stabilizing the igniter flame 54 and staggering it to The end of the pilot burner. This ensures a continuous, uninterrupted, self-adjusting operation of the pilot burner to completely heat the oven as quickly as possible. It is generally preferred to maintain the hood-like igniter flame 47 for the operation of the igniter burner so that it is immediately reignited by the igniter flame in the event that the primary flame produced by the igniter becomes # 灭. Figure 5 is a schematic representation of the main lead flame 54 produced downstream of the pilot burner combustor and its interaction with the pilot flame extending from the downstream end 68 of the shroud. As mentioned earlier, the fuel injection 53 emitted from the ignition nozzle nozzle is guided outward and away from the axis of the ignition element. The heat input into the interior of the furnace is required for the heat input. Gaseous fuel injection 53 has a speed typically between 500 and 1500 mph. These high speeds also help 17 200928234. The fuel injection is mixed with sufficient air to efficiently burn a large amount of fuel gas delivered through the pilot. In order to ensure reliable flame propagation from the flame 47 via the high velocity fuel injection 53, the combustible mixture in the substantial portion of the flow immediately adjacent to the 5 nozzles 40 must be achieved and maintained in the course required to ignite the fuel. By arranging the two or more rows of the openings 52 axially separated from each other along the circumference of the nozzle 4 and by tangentially positioning the orifice of the fuel emitted from the igniter hole σ52. This effect. In each column, the orifice is generally separated by about one to two times the diameter of the orifice. - The preferred embodiment of the present invention, the spacing between the orifices is approximately ❿ 10 which is twice the diameter of the nozzle. For the stabilization of the flame 54, the flame propagation through the gas jet 53 is not sufficient. "The flow re-circulation enhanced by the rotation of the fuel emitted from the pilot orifice 52 by the tangential positioning of the orifice 5 The S system allows the ignition to operate efficiently and reliably. 15 As is well known to those skilled in the art, the linear component of the helical action imparted with fuel injection to form a forward guide facilitates the formation of a gaseous recirculation. The larger the spiral effect, the better the recirculation. The gas recirculation group 〇 The injury system is based on the following function of the so-called “ship number” s:
S = ^動量的軸向通量 轴向推力xR 20 其中軸向推力係為蜓燒空氣及進入重新流通區的氣體 /仙所施加之轴向力，r為引火件孔σ52的徑向距離(從引火 件喷嘴的中心）’而角動量為氣體喷注53所產生之處於尺的 旋轉力。 18 200928234 5 ❹ 10 15 ❹ 20 對於諸如油等特定燃料，引火件喷嘴40會延伸經過主 燃燒器4的下游端進入燃燒器喉26中。然而，對於燒煤的燃 燒器，引火件係凹入煤供應導管20與燃燒空氣導管32之間 的環狀空間3 4中以使引火件保持遠離燃煤爐具内部常出現 但其被燃燒空氣流保持位於環狀通道3 4外且因此亦遠離引 火件喷嘴之熱量、煙霧、塵土、顆粒及類似物。 來自引火件36之燃料繼續燃燒直到爐具内部抵達所想 要溫度為止’其時’諸如煤等生產燃料可被點燃及穩定地 燃燒而不會產生如同抵達所需爐溫前即開始燃燒時所發生 之大量污染物。S = ^ momentum axial flux axial thrust xR 20 where the axial thrust is the axial force applied by the smoldering air and the gas/sen in the recirculation zone, and r is the radial distance of the igniter hole σ52 ( From the center of the pilot nozzle, 'the angular momentum is the rotational force of the ruler generated by the gas jet 53. 18 200928234 5 ❹ 10 15 ❹ 20 For a specific fuel such as oil, the pilot nozzle 40 extends through the downstream end of the main burner 4 into the burner throat 26. However, for a coal-burning burner, the igniter is recessed into the annular space 34 between the coal supply conduit 20 and the combustion air conduit 32 to keep the igniter away from the interior of the coal-fired stove but is burned by the air. The flow remains in the heat, smoke, dust, particles and the like that are located outside the annular passage 34 and thus also away from the pilot nozzle. The fuel from the igniter 36 continues to burn until the interior of the furnace reaches the desired temperature. 'At the time', the production fuel, such as coal, can be ignited and burned steadily without burning as before the desired furnace temperature is reached. A large number of pollutants have occurred.
【圖式簡單說明；J 第1圖示意地顯示用於驅動如大型發電廠中所用的一 蒸氣輪機之一大型譬如公用事業型爐具配置； 第2圖為經過一燃燒器的示意橫剖視圖，其包括一用於 裝設在第1圖所示的爐具中之根據本發明所構成的高熱量 輸出引火件； 第3A及3B圖為本發明的引火件之剖視圖； 第4圖為第1圖所示的主燃燒器及引火件之示意正視 圖； 第5圖示意地顯示根據本發明之一引火件火焰重新流 通區的形態； 第6圖為第3A及3B圖所示之引火件的一空氣流限制器 板的端視圖； 第7圖為一用於防止燃燒空氣直接地流入一圍繞引火 19 200928234 件的罩套中之空氣流直化器的端視圖； 第8 A及8B圖分別為第3A及3B圖所示之引火件的喷嘴 之端視圖及側視圖。 【主要元件符號說明】 2···大型公用事業型爐具 42···管狀屏蔽件或罩套 4···主生產燃燒器,燃燒器裝設件 44…電火花點燃器 6…爐具壁 47…點燃器火焰 8…爐具内部 10…蒸氣 50…排放或下游端 — 52…引火件燃料排放孔口 ® 12…輪機 52A，52B...列 14…堆積體 53…氣體喷注 16···主燃燒器 54…主引火件火焰 18…煤供應源 58…流重新流通 20…煤供應導管 66…罩套的上游端 22…燃燒器的下游端,排放端 68…罩套的下游端 24…旋轉器或轉向器 26…燃燒器喉 70…流直化器及調控器 76…點燃器支撐f .❹ 28…補充性燃料供應管 80…肋 30…燃料排放端蓋 82…流直化通道 32…燃燒空氣供應導管 84…減振器板 34…環狀燃燒空氣通道 86…凸緣,管狀轂 36…引火件燃燒器 88···υ形切口 38…燃料進給管 90…罩套上游端與減振器板間 40…引火件喷嘴 之間隙 20 200928234 . 92…峭壁體部 102···引火件喷嘴相對較小直 93…斜坡 徑的中心孔 94…電子點燃器 104…經放大空間 96…引火件燃燒器軸線，噴嘴 106…箭頭，燃料喷注的切線性 的中心，點燃器燃燒器軸線 定位及定向 98…孔口中心線 100…半徑線 α…發散角度 ❹ 21BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic view showing a large-scale utility model such as a utility type furnace for driving a steam turbine used in a large power plant; FIG. 2 is a schematic cross-sectional view through a burner, The utility model comprises a high-heat output fire-extinguishing member constructed according to the invention for installing in the stove shown in Fig. 1; 3A and 3B are cross-sectional views of the fire-extinguishing member of the invention; A schematic front view of the main burner and the igniter shown in the drawing; Fig. 5 is a view schematically showing the form of the recirculation zone of the igniting flame according to the present invention; Fig. 6 is a view of the igniter shown in Figs. 3A and 3B An end view of an air flow restrictor plate; Figure 7 is an end view of an air flow straightener for preventing combustion air from flowing directly into a shroud surrounding the fire 19 19928234; Figures 8A and 8B respectively It is an end view and a side view of the nozzle of the igniter shown in Figs. 3A and 3B. [Explanation of main component symbols] 2··· Large-scale utility type stove 42···Tubular shield or cover 4···Main production burner, burner assembly 44...Electrical spark igniter 6...Heat Wall 47...Ignitor flame 8...Heat interior 10...Vapor 50...Drain or downstream end - 52...Firearm fuel discharge orifices® 12...Engines 52A, 52B...Column 14...Stack 53...Gas injection 16 Main burner 54... main pilot flame 18... coal supply 58... flow recirculation 20... coal supply conduit 66... upstream end 22 of the casing... downstream end of the burner, discharge end 68... downstream of the casing End 24... rotator or diverter 26... burner throat 70... flow straightener and governor 76... igniter support f. ❹ 28... supplemental fuel supply tube 80... rib 30... fuel discharge end cap 82... straight Channel 32...combustion air supply conduit 84...damper plate 34...annular combustion air passage 86...flange, tubular hub 36...fire burner burner 88·υ-shaped slit 38...fuel feed tube 90...hood Between the upstream end and the damper plate 40... the gap between the pilot nozzles 20 . 92...The cliff body 102···The firing member nozzle is relatively small straight 93...the center hole 94 of the ramp diameter...the electronic igniter 104...the enlarged space 96...the igniter burner axis, the nozzle 106...the arrow, the fuel injection Tangent linear center, igniter burner axis positioning and orientation 98... orifice centerline 100...radius line a... divergence angle ❹ 21