200817638 九、發明說明： 【發明所屬之技術領域】 本發明係關於一種爐床式焚化爐之燃燒控制裝置，其係 自投入有垃圾、產業廢棄物等被燃燒物之爐床下方導入一 次空氣，並於該爐床上方之燃燒室内進行一次燃燒後，於 該燃燒室之上方部位進行二次燃燒。 【先前技術】 爐床式焚化爐係構成方式如下之焚化爐：具備火格子以 固定段及可動段交替配置而成之爐床，利用油壓裝置使可 動段往返移動，藉此對自進料斗投入之垃圾（被燃燒物）進 行攪拌並使之前進，並且在配置於該爐床上游側之乾燥帶 内使垃圾乾燥，繼而於其後之主燃燒帶内投入一次空氣並 且進行主燃燒’進而於最下游側之後燃燒帶内進行燃燒殘 餘部分之後燃燒。 關於如此之爐床式焚化爐，專利文獻1 (曰本專利第 3582710號公報）提供有下述技術：使抽出爐床上之燃燒室 内一部分燃燒排氣後所得的再循環氣體，經由再循環通道 回流至上述燃燒室内之二次燃燒部，與二次空氣一起供給 用於燃燒。 專利文獻1所提供之技術中，抽出爐床上方之燃燒室内 一部分燃燒排氣，作為再循環氣體送入熱交換器，於該熱 交換器中使該再循環氣體與一次空氣及二次空氣進行熱交 換，以預熱該一次空氣及二次空氣並且冷卻該再循環氣 體，進而藉由配置於上述熱交換器尾侧的風扇，將該已降 118513.doc 200817638 溫的再循環氣體投入上述燃燒室内之二次空氣供給口之上 游側部位，使二次空氣供給口上游側之氣體環境成為弱還 原性氣體環境，並將二次空氣供給後燃燒室内之全部空氣 所占比率控制為1.3左右，使未燃燒氣體或未燃燒物完全 燃燒並且減少NOx。 專利文獻1:曰本專利第3582710號公報 【發明内容】 [發明所欲解決之問題] 然而，如上所述專利文獻1之先前技術中，存在以下問 題。 亦即，於上述先前技術中，抽出爐床上方之燃燒室内一 部分燃燒排氣，作為再循環氣體送入熱交換器，於該熱交 換器内藉由與一次空氣及二次空氣進行熱交換而冷卻該再 循環氣體後，藉由配置於上述熱交換器尾側之風扇，將該 已降/BZL的再循環氣體投入燃燒室内之二次空氣供給口之上 游側部位，因此，必須使用熱交換器，用以使該再循環氣 體與空氣（一次空氣及二次空氣）進行熱交換而降溫後再送 入風扇，從而燃燒排氣再循環系統之構造變得複雜，並且 部件數變多導致裝置成本提高。 又，雖藉由上述熱交換器而得以降溫但腐蝕成分較多的 燃燒排氣，直接送入上述風扇，故風扇容易受到腐蝕，導 致该風扇之耐久性及壽命下降。 為解決上述先前技術之問題，本案發明人等已提供日本 專利特願2〇〇5-059846號（2005年3月4日申請）之發明。 118513.doc 200817638 關於藉由風扇，使自爐床上方之辦焊 燃燒排氣，铖± $ y w 、 “、、疋至内抽出之一部分 請之發明中，焱认 …心至内，於該先前申 再循心，述再循環通道中風屬之上游部位，使 再循u財直接混合由缝用-次 一古讲4装_L、 乳4 一 \空氣之任 冓成的空氣，並導入至再循環 而Μ由兮η $ ’、體回 用風扇’繼 燒室内，心 再风《再循％氣體回流至燃 精此，可利用空氣使燃燒排氣降溫，並且藉由與 稀釋燃燒排氣後將其導入風扇，因此，無需如 "述“技術之用以使再循環氣體冷卻降溫的熱交換器， ::吏燃燒排氣再循環系統之構造變簡單，並且減少構成 邛件數而降低了焚化設備之裝置成本。 又’於該先前中請之發明中，再循環氣體回流用風扇中 二導入之再循環氣體’係藉由低溫空氣受到冷卻降溫、又 精由該空氣而稀釋，從而使得燃燒排氣濃度變低，進而藉 由上述冷部使作為排氣中之腐蝕成分之鹽類固化而使得腐 钱成分減少，因此，風扇溫度下降且該風扇之熱應力變 小，並且如上所述可藉由冑已減少腐钕成分之再循環氣體 導入風扇而抑制風扇腐蝕，藉此可獲得低成本之風扇而無 需使用高價耐熱材料，且所需耐久性及壽命得以維持。 然而，於上述先前申請之發明中，僅提出有上述爐床式 焚化爐中再循環氣體與空氣（燃燒用一次空氣及二次空氣） 之混合及向焚化爐侧之回流方法、以及用以進行該混合及 向焚化爐側之回流的裝置，而上述先前申請之發明中i未 揭示，向焚化爐側回流之再循環氣體與空氣的具體混合比 118513.doc 200817638 控制、及利用空氣混合再循環氣體之回流所進行之焚化爐 内的燃燒控制等。 本發明係鑒於如此之現狀而完成者，其目的在於提供一 種爐床式焚化爐之燃燒控制裝置，能以高精度對經由具備 再循環風扇之再循環通道向焚化爐侧回流的空氣混合再循 環氣體實施混合比控制、及實施焚化爐内之燃燒控制，且 可藉由相對簡單且低成本之結構來抑制NOx、CO等有害成 分之產生，並且以較高之燃燒效率實現完全燃燒。 [解決問題之技術手段] 為解決上述先前技術之課題，本發明中請求項1之發明 係一種爐床式焚化爐之燃燒控制裝置，其係構成為自投入 被焚化物之爐床下方導入一次空氣，於該爐床上方之燃燒 室内進行一次燃燒後，於該燃燒室上方進行二次燃燒，並 且混合抽出上述燃燒室内一部分燃燒排氣之再循環氣體與 經由空氣通道而供給之空氣，藉由風扇使該空氣混合再循 環氣體經由再循環通道而供給至爐内，該爐床式焚化爐之 燃燒控制裝置的特徵在於：於上述空氣通道中設有調整空 氣流量之空氣流量調整機構，另一方面設有溫度檢測機構 及燃燒控制機構，上述溫度檢測機構係檢測上述空氣混合 再循環氣體之溫度，上述燃燒控制機構係輸入來自上述温 度檢測機構之上述空氣混合再循環氣體之溫度檢測值，根 據該溫度檢測值算出上述空氣混合再循環氣體之溫度成為 預先設定之目標溫度的上述空氣流量調整機構之通道面 積，並將上述空氣流量調整機構控制於上述通道面積算出 118513.doc 200817638 值。 又，本發明中請求項2之發明係，於上述燃燒控制裝置 中，於上述空氣通道中設有調整空氣流量之空氣流量調整 機構，另一方面設有氣體濃度檢測機構及燃燒控制機構， 上述氣體濃度檢測機構係檢測上述空氣混合再循環氣體之 氣體濃度，上述燃燒控制機構係輸入來自上述氣體濃度檢 測機構的上述空氣混合再循環氣體之氣體濃度檢測值，根 據该氣體濃度檢測值算出上述空氣混合再循環氣體之氣體 濃度成為預先設定之目標氣體濃度的上述空氣流量調整機 構之通道面積，並將上述空氣流量調整機構控制於上述通 道面積算出值。 請求項2之發明以外，請求項3之發明中，設置檢測上述 燃燒排氣中NOx濃度之NOx濃度檢測機構、及檢測上述燃 燒排氣中CO濃度之CO濃度檢測機構，而上述燃燒控制機 構較好的是構成為根據自上述氣體濃度檢測機構輸入之該 氣體濃度檢測值、自上述ΝΟχ濃度檢測機構輸入之]^〇乂濃 度檢測值及自上述CO濃度檢測機構輸入之c〇濃度檢測 值’算出上述空氣混合再循環氣體之氣體濃度成為預先設 定之目標氣體濃度、上述燃燒排氣中之Ν〇χ濃度成為預先 設定之目標ΝΟχ濃度以下及上述燃燒排氣中之c〇濃度成為 預先設定之目標CO濃度以下的上述空氣流量調整機構之 通道面積，並將上述空氣流量調整機構控制於上述通道面 積算出值。 又’本發明中請求項4之發明係，於上述燃燒控制裝置 118513.doc •10- 200817638 中，於上述空氣通道中設置調整空氣流量之空氣流量調整 機構，另一方面設有溫度檢測機構、氣體濃度檢測機構及 燃燒控制機構，上述溫度檢測機構係檢測上述空氣混合再 循環氣體之溫度，上述氣體濃度檢測機構係檢測上述空氣 混合再循環氣體之氣體濃度，上述燃燒控制機構係輸入來 自上述溫度檢測機構的上述空氣混合再循環氣體之溫度檢 測值及來自上述氣體濃度檢測機構的上述空氣混合再循環 氣體之氣體濃度檢測值’根據該等溫度檢測值及氣體濃度 檢測值，算出上述空氣混合再循環氣體之溫度成為預先設 定之目標溫度且上述空氣混合再循環氣體之氣體濃度成為 預先設定之目標氣體濃度的上述空氣流量調整機構之通道 面積，並將上述空氣流量調整機構控制於上述通道面積算 出值。 進而，本發明中請求項5之發明係，於上述燃燒控制裝 置中，於空氣混合再循環氣體所流通的再循環氣體通道中 設置調整空氣混合再循環氣體流量之再循環氣體流量調整 機構，該空氣混合再循環氣體係將空氣混合至上述再循環 氣體中後供給至上述燃燒室者；並且設置氣體流量計及燃 燒控制機構，上述氣體流量計係檢測上述空氣混合再循環 氣體之流量，上述燃燒控制機構係根據自上述氣體流量計 輸入的再循環氣體之流量檢測值，算出該再循環氣體之流 量成為預先設定之目標流量的上述再循環氣體流量調整機 構之通道面積，並將上述再循環氣體流量調整機構控制於 上述通道面積算出值。 118513.doc 11 200817638 ^求項5之發明以外，請求項6之發明中，於上述燃燒室 之稷數處設置再循環氣體吹出口，並且設置複數個上述再 循環氣體通道連接於上述各再猶環氣體吹出口，於上述各 再循環氣體通道中設置調整空氣混合再循環氣趙流量之再 循環氣體流量調整機構’對應於再循環氣體流量調整機構 設置檢測上述燃燒室之塵力的上述燃_力檢測機構， 而上述燃燒控制機構較好的是構成為根據來自上述複數個 燃燒室壓力檢測機構的上述燃燒室遷力檢測值，算出上述 複數處燃燒室壓力成為預先設定之目標壓力的上述各再循 =體流量調整機構之通道面積，並將上述各再循環氣體 流Ϊ调整機構控制於上述通道面積算出值。 [發明之效果] 請求項1之發明中，利用燃燒控制機構，根據運送空氣 混合再循環氣體的再循環風扇中所導人之空氣混合再循環 ^體之溫度檢測值，調整空氣流量調整機構之開度而控制 此入上述空氣混合再循環氣體中的空氣量，以使該空氣混 合再循環氣體之溫度變為預先設定之容許最高溫度以下， =此，即便因某些原因造成上述再循環氣體之溫度上升 時，亦可藉由對應於該溫度上升使空氣量增加，而將上述 再循環風扇所吸入的空氣混合再循環氣體之溫度一直適當 保持於上述容許最高溫度以下。 藉此，可防止上述空氣混合再循環氣體所引起的再循環 風扇之過熱，且無須對該再循環風扇使用由特殊耐熱材料 構成之高成本風扇，即可保持較高之耐久性。 118513.doc -12 - 200817638 請求項2之發明中，利用燃燒控制機構，根據再循環風 扇中所導入的空氣混合再循環氣體之氣體濃度檢測值（較 好的是氧濃度檢測值），調整空氣流量調整機構之開度（通 道面積）而控制混入上述空氣混合再循環氣體中的空氣 量，以使該空氣混合再循環氣體之氣體濃度變為預先設定 的容許氣體濃度，因此，例如，即便再循環氣體中之氧受 到消耗而導致氧濃度變得過小時，亦可藉由增大上述空氣 流量調整機構之開度使空氣量增加，而一直於上述容許最 小氧濃度以上之狀態下進行穩定燃燒。 又，若構成如請求項3之發明，則由於利用燃燒控制機 構調整空氣流量調整機構之開度，故可使燃燒排氣中之 NOx濃度一直保持於容許最大NOx濃度以下、且使燃燒排 氣中之CO濃度一直保持於容許最大CO濃度以下，從而可 促進排氣之淨化。 根據請求項4之發明，可獲得請求項1之發明與請求項2 之發明的相乘效果。 即，請求項4之發明中， (1)利用燃燒控制機構，根據再循環風扇中所導入之空氣 混合再循環氣體之溫度檢測值，調整空氣流量調整機構之 開度而控制混入上述空氣混合再循環氣體中的空氣量，以 使該空氣混合再循環氣體之溫度變為預先設定之容許最高 溫度以下，因此，即便因某些原因引起上述再循環氣體之 温度上升時，亦可藉由對應於該溫度上升使空氣量增加， 而將上述再循環風扇所吸入的空氣混合再循環氣體之溫度 118513.doc •13- 200817638 一直適當保持於上述容許最高溫度以下。 藉此，可防止上述空氣混合再循環氣體所引起的再循環 風扇之過熱5無須對該再循壞風扇使用由特殊耐熱材料構 成之高成本風扇，即可保持較高之耐久性。 (2)利用燃燒控制機構，根據再循環風扇中所導入的空氣 混合再循環氣體之氣體濃度檢測值（較好的是氧濃度檢測 值），調整空氣流量調整機構之開度（通道面積）而控制混入 上述空氣混合再循環氣體的空氣量，以使該空氣混合再循 環氣體之氣體濃度變為預先設定的容許氣體濃度，因此， 例如，即便再循環氣體中之氧受到消耗而導致氧濃度變得 過小時，亦可藉由增大上述空氣流量調整機構之開度使空 氣量增加，而一直於上述容許最小氧濃度以上之狀態下進 行穩定燃燒。 請求項5之發明中，於空氣混合再循環氣體所流通的吸 入通道（再循環氣體通道）中設置用於調整空氣混合再循環 氣體流量的該再循環氣體流量調整機構，並且根據來自檢 測上述空氣混合再循環氣體之流量的氣體流量計之再循環 氣體之流量檢測值，控制再循環氣體流量調整機構，以使 該再循環氣體之流量變為預先設定之目標流量，因此，藉 由控制再循環氣體流量調整機構之開度以使再循環氣體之 流量變為目標流量，可將作為二次空氣的空氣混合再循環 氣體之量，穩定地保持於該空氣混合再循環氣體可完全燃 燒之量，從而可使燃燒狀態平均化而保持穩定燃燒。 又，若構成如請求項6之發明，則於燃燒室之複數處設 118513.doc -14- 200817638 置再循環氣體吹出口，且對應於再循環氣體流量調整機構 設置燃燒室壓力檢測機構，該再循環氣體流量調整機構係 設置於與上述再循環氣體吹出口連接的各再循環氣體通道 中，並利用燃燒控制機構，檢測再循環氣體吹出口附近之 再循環氣體壓力，利用再循環氣體量與再循環氣體壓力成 比例此種關係，控制該再循環氣體壓力使之變為目標氣體 壓力，因此，可自由調整對設於燃燒室之複數處之再循環 氣體吹出口的空氣混入再循環氣體量之分配，從而可將空 氣混入再循環氣體均勻地供給於燃燒室之周方向上，由此 可使燃燒平均化。 【實施方式】 以下，根據圖示之實施形態，詳細說明本發明。 [第1實施形態] 圖1係本發明之第1實施形態之爐床式焚化爐之結構圖， 圖2係上述第1實施形態之燃燒控制機構之概略結構圖，圖 3係上述第1實施形態之燃燒控制區塊圖。 於圖1中，1為用於投入垃圾或產業廢棄物等被燃燒物之 垃圾進料斗，2為爐床式焚化爐。該爐床式焚化爐2中，自 垃圾進料斗1開始之投入口至爐内底部，鋪設有主要構成 乾燥帶之乾燥帶爐床21、主要構成燃燒帶之主燃燒帶爐床 22、及主要構成後燃燒帶之後燃燒帶爐床以。乾燥帶爐床 21位於最上游側，主燃燒帶爐床22位於乾燥帶爐床^之下 游側，後燃燒帶爐床23在主燃燒帶爐床22之下游位於最下 游側。此處，主燃燒帶係指於垃圾層上燃起火焰而燃燒的 118513.doc -15- 200817638 區域。 上述各爐床21、22、23具備配設於固定火格子之間的移 動火格子，投入垃圾（被燃燒物）後，藉由該移動火格子之 往返運動，使該垃圾於爐床21内乾燥，於爐床22内進行主 燃燒，最後於爐床23内進行後燃燒。再者，於本實施形態 中上述主燃燒帶爐床22為3個，然而亦可設為“固或複數 個。8為儲灰槽。 又，於上述爐床21、22、23上方設有一次燃燒室3，進 而’於其上方設有二次燃燒室4。 19a、19b、19c、19d係面朝二次燃燒室4設置之再循環 氣體吹出噴嘴。又，81係與二次燃燒室4之排氣出口連接 之鋼爐。 於乾燥帶爐床21、燃燒帶爐床22及後燃燒帶爐床23，配 設有開口於各自下部之風箱的一次空氣管51、52(3個）、 53，一次空氣由該一次空氣管供給。6為一次空氣供給用 風扇，5為一次空氣主管，與該風扇6、及各一次空氣管 51 5^(3個）、53連接；由風扇6壓送而來之一次空氣係， 自次空氣主管5分配至一次空氣管51、52、53中。於一 次空氣管5 1、52、53中，設有分別開閉該等一次空氣管之 開閉阻尼器54、55、56。又，於一次空氣主管5中，設有 開閉該一次空氣主管之開閉阻尼器7。 40為再循環氣體抽出口，用於抽出上述一次燃燒室3内 (亦可為二次燃燒室4内）之一部分燃燒排氣作為再循環氣 體，自該再循環氣體抽出口 40所抽出的再循環氣體，經由 118513.doc -16- 200817638 再循環通道16、混合氣體通道14及用於分離混合氣體中之 固體異物的旋風分離器12，導入至再循環風扇13之吸入通 道3 1。亦即，使再循環氣體抽出口 40與吸入通道3 1經由再 循環通道16而連接，於吸入通道3 1中，設有開閉再循環風 扇13之入口的氣體阻尼器013。 30為混入空氣通道，自一次空氣主管5分支且與作為再 循環風扇13之上游部位的吸入通道31連接，30a為空氣阻 尼器（開閉阻尼器），用於開閉混入空氣通道30，若打開該 空氣阻尼器30a，則來自一次空氣主管5的一次空氣經由混 入空氣通道30而投入至吸入通道31之再循環風扇13之入 口，由此一次空氣混合至上述再循環氣體中，繼而經由混 合氣體通道14、旋風分離器12及吸入通道31而導入再循環 風扇13中。 上述空氣阻尼器30a係可接收來自後文將述的燃燒控制 機構60之控制信號而自動進行開度調整（流量調整），藉由 調整該空氣阻尼器30a之開度，對流過混入空氣通道30的 一次空氣之流量加以調整，從而調整空氣混合再循環氣體 中再循環氣體與一次空氣之混合比例，該空氣混合再循環 氣體係經由混合氣體通道14、旋風分離器12及吸入通道31 而導入再循環風扇13的再循環氣體與一次空氣之混合氣 體。 繼而，藉由再循環風扇13而壓送至再循環通道1 5的一次 空氣混合後之空氣混合再循環氣體，分流至2個再循環通 道17、1 8中，並由一侧之再循環通道17送入一側之2行再 118513.doc -17- 200817638 循環氣體吹出噴嘴19a、19c，由另一側之再循環通道“送 入另一側之2行再循環氣體吹出噴嘴191)、19d，進而由再 循環氣體吹出噴嘴19a、19c及19b、19d噴出至二次燃燒室 4内。又，於再循環通道17中設有開閉該再循環通道π的 分支氣體阻尼器B33，於再循環通道1 8中設有開閉該再循 環通道18的分支氣體阻尼器A32。 3 5為溫度感測器，設於上述再循環通道丨5中、用於檢測 上述空氣混合再循環氣體之溫度（亦可於混合氣體通道Μ 中設置溫度感測器35a。以下就溫度感測器35進行說明）。 36為空氣阻尼器開度檢測器，用於檢測上述空氣阻尼器 30a之開度。 本發明之第1實施形態之爐床式焚化爐2具備燃燒控制機 構60，該燃燒控制機構60電性連接於溫度感測器35(包括 35a)、空氣阻尼器30a及空氣阻尼器開度檢測器％，自溫 度感測器35輸入上述空氣混合再循環氣體之溫度檢測值， 並且自空氣阻尼器開度檢測器36輸入空氣阻尼器3(^之開 度檢測值，根據該等檢測值調整空氣阻尼器3(^之開度， 將上述空氣混合再循環氣體中再循環氣體與一次空氣之混 合比例控制為目標混合比例，以使上述空氣混合再循環氣 體之溫度變為目標溫度。 於該爐床式焚化爐2運轉時，將經由再循環氣體抽出口 40自爐床上方之燃燒室（一次燃燒室3或者二次燃燒室4)内 抽出的一部分燃燒排氣作為再循環氣體，經由再循環通道 16,與來自混入空氣通道30的一次空氣混合，繼而經由混 118513.doc •18- 200817638 合氣體通道14、旋風分離器12及吸入通道31而導入再循環 風扇13中。 再者，藉由再循環風扇13壓送至再循環通道15的一次空 氣混合後之空氣混合再循環氣體，分流至2個再循環通道 17、18中，並分別送入一側之再循環氣體吹出喷嘴19a、 19c及另一側之再循環氣體吹出喷嘴19b、19d，進而由再 循環氣體吹出喷嘴19a、19c及19b、19d喷出至二次燃燒室 4内。 如此般，可使由一部分燃燒排氣組成之再循環氣體，因 一次空氣而降溫，並且藉由與該一次空氣之混合使燃燒排 氣稀釋後，再導入再循環風扇13。 繼而，根據圖2及圖3，就第1實施形態之燃燒控制機構 及燃燒控制順序加以說明。 本實施形態之燃燒控制機構60，具備氣體溫度比較部 61、基準氣體溫度設定部62、氣體溫度/空氣量設定部 63、空氣量調整量算出部64、空氣阻尼器開度調整量算出 部65、及空氣阻尼器開度算出部66，由溫度感測器35檢測 出的空氣混合再循環氣體之溫度檢測值輸入至該燃燒控制 機構60之氣體溫度比較部61。於基準氣體溫度設定部62 内，設定有送入上述再循環風扇13中的上述空氣混合再循 環氣體之容許最高溫度（較佳為300°C左右）。 又，於氣體溫度比較部61中，算出溫度偏差，該溫度偏 差係來自溫度感測器35的空氣混合再循環氣體之溫度檢測 值與基準氣體溫度設定部62中所設定之容許最高溫度的溫 118513.doc -19- 200817638 度偏差。 繼而，按照以下順序，利用圖2所示的空氣阻尼器開度 算出機構600算出空氣阻尼器30a之開度。 於圖3中，來自氣體溫度比較部61的溫度偏差之算出 值，輸入至空氣量調整量算出部64。 於氣體溫度/空氣量設定部63中，藉由試驗結果或者模 擬計算，預先設定經由混入空氣通道30而供給的空氣之空 氣量、及上述空氣與來自再循環通道16的再循環氣體混合 後之上述空氣混合再循環氣體溫度的關係。 又，於空氣量調整量算出部64中，自上述氣體溫度/空 氣量設定部63算出（提取）與來自氣體溫度比較部61的上述 溫度偏差之算出值相對應的空氣量偏差，並輸出至空氣阻 尼器開度調整量算出部65。於空氣阻尼器開度調整量算出 部65中，設定有空氣量與空氣阻尼器開度之關係作為上述 空氣阻尼器30a之開度特性，於該空氣阻尼器開度調整量 算出部65中，算出與來自空氣量調整量算出部64的空氣量 偏差算出值相對應之空氣阻尼器開度調整量，並輸出至空 氣阻尼器開度算出部66。 於該空氣阻尼器開度算出部66中，對自上述空氣阻尼器 開度檢測器36輸入的空氣阻尼器30a之開度檢測值，加上 或減去來自上述空氣阻尼器開度調整量算出部65的空氣阻 尼器開度調整量，算出空氣阻尼器開度的目標值、即與上 述基準氣體溫度相對應的空氣阻尼器開度，並將上述空氣 阻尼器30a控制為該目標開度。 118513.doc -20- 200817638 如此於第1實施形態之爐床式焚化爐2之燃燒控制裝置 中’利用燃燒控制機構60，根據通過上述再循環風扇丨3的 空氣混合再循環氣體之溫度檢測值，調整空氣阻尼器3〇a 之開度而控制混入上述空氣混合再循環氣體的空氣量，以 使泫空氣混合再循環氣體之溫度變為預先設定的容許最高 溫度以下，因此，即便因某些原因引起上述再循環氣體之 溫度上升時，亦可藉由對應於該溫度上升使空氣量增加， 而將上述再循環風扇13所吸入的空氣混合再循環氣體之溫 度一直適當地保持在上述容許最高溫度以下。 藉此，可防止上述空氣混合再循環氣體所引起的再循環 風扇13之過熱，故無須對再循環風扇13使用由特殊的耐熱 材料所構成之咼成本風扇，即可保持較高的耐久性。 [第2實施形態] 圖4係本發明第2實施形態之爐床式焚化爐之結構圖，圖 5係上述第2實施形態之燃燒控制機構之概略結構圖，圖6 係上述第2實施形態之燃燒控制區塊圖。 於本發明之第2實施形態中，在檢測上述空氣混合再循 環氧體之氣體濃度並根據該氣體濃度控制空氣阻尼器3 ^ 之開度的機構中，使用氧濃度作為氣體濃度。再者，亦可 使用C〇2等空氣混合再循環氣體中其他成分之濃度，替代 該氧濃度。 亦即，於本發明第2實施形態之爐床式焚化爐2中，如圖 4所示，設有檢測空氣混合再循環氣體中之氧濃度的氧濃 度计3 7(或者氧濃度計37a)、檢測上述二次燃燒室4出口侧 118513.doc -21- 200817638 之燃燒排氣中之ΝΟχ濃度的NOx濃度感測器38、及檢測c〇 濃度的CO濃度感測器39。 再者，本實施形態之燃燒控制機構60，如圖5及圖6所 示’具備氧濃度比較部71、基準氧濃度設定部72、NOx濃 度比較部73、基準ΝΟχ濃度設定部74、CO濃度比較部75、 基準CO濃度設定部76、空氣量調整量算出部77、氧濃度/ 空氣量設定部78、空氣量調整量算出部79、ΝΟχ濃度/空氣 量設定部80、空氣量調整量算出部81、CO濃度/空氣量設 定部82、空氣阻尼器開度調整量算出部65及空氣阻尼器開 度算出部66，根據來自氧濃度計37之氧濃度檢測值，算出 使上述空氣混合再循環氣體之氧濃度變為預先設定之目標 氧濃度的空氣阻尼器30a之開度，並將空氣阻尼器30a之開 度控制為該開度算出值。 又，燃燒控制機構60根據來自NOx濃度感測器38之n〇x 濃度檢測值及來自CO濃度感測器39之CO濃度檢測值，算 出使上述燃燒排氣中之NOx濃度變為預先設定之目標ΝΟχ 濃度以下、且燃燒排氣中CO濃度變為預先設定之目標CO 濃度以下的空氣阻尼器30a之開度，並將空氣阻尼器30a之 開度控制為該開度算出值。 以下，根據圖5及圖6，說明第2實施形態之燃燒控制機 構及燃燒控制順序。 圖5係摘選顯示該第2實施形態中之如下步驟，即，利用 空氣阻尼器開度算出機構600根據來自氧濃度計37(37a)的 氧濃度檢測值而算出空氣阻尼器30a之開度，而以下動作 118513.doc -22- 200817638 說明係參照圖6，就除上述氧濃度以外使用有燃燒排氣中 之NOx濃度及CO濃度的燃燒控制加以說明的。 於圖6中，由氧濃度計37(或氧濃度計37a)檢測出的上述 空氣混合再循環氣體之氧濃度檢測值，輸入至燃燒控制機 構60之氧濃度比較部71中。又，由NOx濃度感測器38檢測 出的燃燒排氣中之ΝΟχ濃度檢測值，輸入至燃燒控制機構 60之ΝΟχ濃度比較部73中。進而，由CO濃度感測器39檢測 出的燃燒排氣中之CO濃度檢測值，輸入至燃燒控制機構 60之CO濃度比較部75中。 於基準氧濃度設定部72中，設定有送入再循環風扇13的 上述空氣混合再循環氣體之容許最小氧濃度。於基準ΝΟχ 濃度設定部74中，設定有上述燃燒排氣中之容許最大ΝΟχ 濃度。於基準CO濃度設定部76中，設定有上述燃燒排氣 中之容許最大CO濃度。 於氧濃度比較部71中，算出來自氧濃度計37的空氣混合 再循環氣體中之氧濃度檢測值與基準氧濃度設定部72中所 設定之容許最小氧濃度的氧濃度偏差，並輸入至空氣量調 整量算出部77。 又，於NOx濃度比較部73中，算出來自NOx濃度感測器 38的燃燒排氣中之ΝΟχ濃度檢測值與基準ΝΟχ濃度設定部 74中所設定之容許最大ΝΟχ濃度的ΝΟχ濃度偏差’並輸入 至空氣量調整量算出部79。 進而，於CO濃度比較部75中，算出來自CO濃度感測器 39的燃燒排氣中之CO濃度檢測值與基準CO濃度設定部76 118513.doc -23- 200817638 中所設定之容許最大CO濃度的CO濃度偏差，並輸入至空 氣量調整量算出部81。 繼而，於氧濃度/空氣量設定部78中，藉由試驗結果或 者模擬計算，預先設定有通過混入空氣通道30而供給的空 氣之空氣量、與混合上述空氣與來自再循環通道16的再循 環氣體後之上述空氣混合再循環氣體中氧濃度的關係。 又，於NOx濃度/空氣量設定部80中，藉由試驗結果或模 擬計算，預先設定有通過混入空氣通道30而供給的空氣之 空氣量與上述燃燒排氣中ΝΟχ濃度的關係。 進而，於CO濃度/空氣量設定部82中，藉由試驗結果或 模擬計算，預先設定有通過混入空氣通道30而供給的空氣 之空氣量與上述燃燒排氣中CO濃度的關係。 繼而，於空氣量調整量算出部77中，自氧濃度/空氣量 設定部78算出（提取）與來自氧濃度比較部71的上述氧濃度 偏差之算出值相對應的空氣量偏差，並輸入至空氣阻尼器 開度調整量算出部65。 又，於空氣量調整量算出部79中，自ΝΟχ濃度/空氣量設 定部80算出（提取）與來自ΝΟχ濃度比較部73的上述ΝΟχ濃 度偏差之算出值相對應的空氣量偏差，並輸入至空氣阻尼 器開度調整量算出部65。 進而，於空氣量調整量算出部81中，自CO濃度/空氣量 設定部82算出（提取）與來自CO濃度比較部75的上述CO濃 度偏差之算出值相對應的空氣量偏差，並輸入至空氣阻尼 器開度調整量算出部65。 118513.doc -24- 200817638 於空氣阻尼器開度調整量算出部65中，設定有空氣量與 空氣阻尼器開度的關係作為空氣阻尼器3〇a之開度特性， 於该空氣阻尼器開度調整量算出部65中，依序算出以與上 述氧濃度偏差相對應之空氣量偏差為根據的空氣阻尼器開 度調整量、以與上述NOx濃度偏差相對應之空氣量偏差為 根據的空氣阻尼器開度調整量、及以與上述C Q濃度偏差 相對應之空氣量偏差為根據的空氣阻尼器開度調整量，並 自上述空氣阻尼器開度調整量中選出最佳空氣阻尼器開度 調整量，輸入至空氣阻尼器開度算出部％。 繼而，於空氣阻尼器開度算出部66中，對自空氣阻尼器 開度檢測器36輸入的空氣阻尼器30a之開度檢測值，加上 或減去來自空氣阻尼器開度調整量算出部65之空氣阻尼器 開度調整量，算出空氣阻尼器開度之目標值、即與上述基 準氧濃度或上述基準NOx濃度或者上述基準〇〇濃度相適應 的空氣阻尼器30a之開度’並將空氣阻尼器3〇a控制為該目 標開度。 其他結構與上述第1實施形癌相同，並使用相同符號表 示與上述第1實施形態相同之構件。 如此，於第2實施形態之爐床式焚化爐2之燃燒控制裝置 中’利用燃燒控制機構60,根據上述再循環風扇13中所導 入的空氣混合再循ί哀氣體之氧濃度檢測值，調整空氣阻尼 器30a之開度而控制混入上述空氣混合再循環氣體的空氣 量，以使該空氣混合再循環氣體之氧濃度變為預先設定的 容許最小氧濃度以上，因此，即便再循環氣體中之氧受到 H8513.doc -25- 200817638 消耗導致氧濃度變得過小時，亦可藉由增大空氣阻尼器 3〇a之開度使空氣量增加，而一直在上述容許最小氧濃度 以上之條件下進行穩定燃燒。 又，藉由利用燃燒控制機構60調整空氣阻尼器3〇a之開 度，可使燃燒排氣中之ΝΟχ濃度一直保持在容許最大州^ 濃度以下、又可使燃燒排氣中之c〇濃度一直保持在容許 最大CO濃度以下，從而可促進排氣之淨化。 [第3實施形態] 圖7係本發明第3實施形態之爐床式焚化爐之結構圖，圖 8係摘選出上述第3實施形態中根據氧濃度及空氣混合再循 環氣體之溫度所進行之燃燒控制的流程圖。 本發明第3實施形態係將圖1〜圖3所示之第1實施形態及 圖4〜圖6所示之第2實施形態組合而成者。 亦即，於該第3實施形態中，利用燃燒控制機構6〇，根 據來自溫度感測器35a(亦或圖1中之溫度感測器35)的空氣 混合再循環氣體之溫度檢測值，調整空氣阻尼器3〇a之開 度而控制混入上述空氣混合再循環氣體的空氣量，以使該 空氣混合再循環氣體之溫度變為預先設定的容許最高溫度 以下’並且，根據檢測上述空氣混合再循環氣體中之氧濃 度的氧濃度計37之氧濃度檢測值，算出使上述空氣混合再 循環氣體之氧濃度變為預先設定之容許最小氧濃度以上的 空氣阻尼器30a之開度，並將空氣阻尼器3〇a之開度控制為 該開度算出值。 又’於第3實施形態中，與上述第2實施形態相同，於二 118513.doc -26- 200817638 次燃燒室4出口側設有檢測燃燒排氣中NOx濃度之NOx濃度 感測器38、及檢測CO濃度之CO濃度感測器39，且根據來 自NOx濃度感測器38之NOx濃度檢測值及來自CO濃度感測 器39之CO濃度檢測值，算出使上述燃燒排氣中之Ν〇χ濃度 變為預先設定的目標ΝΟχ濃度以下、且使燃燒排氣中之c〇 濃度變為預先設定的目標CO濃度以下的空氣阻尼器3〇a之 開度，並將空氣阻尼器30a之開度控制為該開度算出值。 其他結構與上述第1實施形態相同，並使用相同符號表 示與上述第1實施形態相同之構件。 圖8係表示摘選出如此之第3實施形態中根據氧濃度及空 氣混合再循環氣體之溫度所進行的燃燒控制之流程圖，該 燃燒控制按下述順序進行。 亦即’利用氧濃度計37檢測出空氣混合再循環氣體之氧 浪度Cg(步驟（1))，將該氧濃度檢測值Cg與目標氧濃度cg0 進行比較（步驟（2))，當氧濃度Cg大於目標氧濃度(：§〇時（(^ > cg〇)關閉空氣阻尼器3〇a以減少空氣量（步驟（3)),當氧 /辰度Cg小於目標氧濃度Cg0時（Cg < Cg〇)打開空氣阻尼器 3〇a以增加空氣量（步驟（4))。 繼而’於根據該根據氧濃度而進行的空氣阻尼器3(^之 開度控制之後，按下述順序根據空氣混合再循環氣體之溫 度而進行空氣阻尼器30a之開度控制。 亦即，於圖8中，利用溫度感測器35a(亦或圖i中之溫度 ^ 器3 5)檢測出空氣混合再循環氣體之溫度丁㊂（步驟 (5))，將該溫度檢測值Tg與目標溫度Tg〇進行比較（步驟 H8513.doc -27- 200817638 (6))，當溫度檢測值Tg與目標溫度Tgo—致時將空氣阻尼 器3 0a之開度保持於現狀，當溫度檢測值Tg高於目標溫度 Tgo時（Tg> Tgo)打開空氣阻尼器30a以增加空氣量，降低 空氣混合再循環氣體之溫度Tg(步驟（7))，當溫度檢測值Tg 低於目標溫度Tgo時（Tg< Tgo)關閉空氣阻尼器30a以減少 空氣量，提昇空氣混合再循環氣體之溫度Tg(步驟（8))。 根據本發明之第3實施形態，可獲得上述第1實施形態及 第2實施形態的相乘效果。 亦即，於第3實施形態之爐床式焚化爐2之燃燒控制裝置 中， (1) 利用燃燒控制機構60，根據再循環風扇13中所導入的 空氣混合再循環氣體之溫度檢測值，調整空氣阻尼器30a 之開度而控制混入上述空氣混合再循環氣體的空氣量，以 使該空氣混合再循環氣體之溫度變為預先設定的容許最高 溫度以下，因此，即便因某些原因使得上述再循環氣體之 溫度上升時，亦可藉由對應於該溫度上升使空氣量增加， 而一直使再循環風扇13所吸入的空氣混合再循環氣體之溫 度適當地保持在上述容許最高溫度以下。 藉此，可防止上述空氣混合再循環氣體所引起的再循環 風扇13之過熱，無須對再循環風扇13使用由特殊的耐熱材 料所構成之高成本風扇，即可保持較高之耐久性。 (2) 利用燃燒控制機構60，根據上述再循環風扇13中所導 入的空氣混合再循環氣體之氧濃度檢測值，調整空氣阻尼 器3 0a之開度而控制混入上述空氣混合再循環氣體的空氣 118513.doc -28- 200817638[Technical Field] The present invention relates to a combustion control device for a hearth incinerator, which introduces primary air from below a hearth into which incineration materials such as garbage and industrial waste are put into use. After one combustion in the combustion chamber on the hearth, secondary combustion is performed on the upper portion of the combustion chamber. [Prior Art] The hearth type incinerator is an incinerator having the following configuration: a hearth having a fire lattice fixedly arranged in a fixed section and a movable section, and the movable section is moved back and forth by the hydraulic device, thereby the self-feeding hopper The put-in garbage (burned matter) is stirred and advanced, and the garbage is dried in a drying belt disposed on the side of the hearth, and then the air is injected into the main combustion zone and the main combustion is performed. After the most downstream side, the combustion residue is burned in the combustion zone and then burned. With regard to such a hearth type incinerator, Patent Document 1 (Japanese Patent No. 3582710) provides a technique of recirculating a portion of a combustion chamber extracted from a combustion chamber on a hearth after combustion of the exhaust gas via a recirculation passage. The secondary combustion portion to the combustion chamber is supplied together with the secondary air for combustion. In the technique disclosed in Patent Document 1, a part of the combustion exhaust gas in the combustion chamber on the hearth is extracted and sent to the heat exchanger as a recirculation gas, and the recirculation gas is subjected to the primary air and the secondary air in the heat exchanger. Heat exchange to preheat the primary air and secondary air and to cool the recycle gas, which is then lowered by a fan disposed on the tail side of the heat exchanger. Doc 200817638 The warm recirculating gas is supplied to the upstream side of the secondary air supply port in the combustion chamber, so that the gas environment on the upstream side of the secondary air supply port becomes a weak reducing gas atmosphere, and the secondary air is supplied to the combustion chamber. The ratio of total air is controlled to 1. Around 3, the unburned gas or unburnt is completely burned and NOx is reduced. [Problem to be Solved by the Invention] However, in the prior art of Patent Document 1 as described above, there are the following problems. That is, in the above prior art, a part of the combustion exhaust gas in the combustion chamber on the hearth is extracted and sent as a recirculation gas to the heat exchanger, in which heat exchange is performed with the primary air and the secondary air. After the recirculation gas is cooled, the reduced/BZL recirculated gas is introduced into the upstream side of the secondary air supply port in the combustion chamber by the fan disposed on the tail side of the heat exchanger. Therefore, heat exchange must be used. The device is configured to make the recirculating gas exchange heat with air (primary air and secondary air) to be cooled and then sent to the fan, so that the structure of the combustion exhaust gas recirculation system becomes complicated, and the number of components increases to cause the device cost. improve. Further, the combustion exhaust gas which is cooled by the heat exchanger but has a large amount of corrosive components is directly supplied to the fan, so that the fan is easily corroded, resulting in deterioration of durability and life of the fan. In order to solve the problems of the prior art described above, the inventors of the present invention have provided the invention of Japanese Patent Application No. 2-5-059846 (filed on March 4, 2005). 118513. Doc 200817638 About the use of a fan to make the welding and exhausting from the furnace, 铖± $ yw, ",, 疋 to the inside of the part of the invention, please recognize the heart, in the previous application According to the heart, the upstream part of the recirculation passage is the upstream part of the recirculation passage, so that the direct mixing of the u-finance is carried out by the seam--the first time, the air of the air, and the air is introduced into the recirculation. By 兮η $ ', the body is returned to the room with a fan, and then the heart is re-circulated. The gas is returned to the fuel, and the combustion exhaust gas can be cooled by the air, and the exhaust gas is introduced by diluting and exhausting it. The fan, therefore, does not need to be a heat exchanger for cooling and cooling the recirculating gas as in the "Technology", the construction of the ::吏 combustion exhaust gas recirculation system is simple, and the number of components is reduced to reduce the incineration equipment. The cost of the device. In the invention of the prior invention, the recirculated gas introduced into the fan for recirculating gas recirculation is cooled by the low temperature air and diluted by the air, so that the combustion exhaust gas concentration is lowered. Further, by the cold portion, the salt which is a corrosive component in the exhaust gas is solidified, and the rotten component is reduced. Therefore, the fan temperature is lowered and the thermal stress of the fan is reduced, and as described above, the crucible can be reduced. The recirculating gas of the rot component is introduced into the fan to suppress fan corrosion, whereby a low-cost fan can be obtained without using a high-priced heat-resistant material, and durability and life required are maintained. However, in the invention of the above-mentioned prior application, only the mixing of the recirculating gas and the air (primary air and secondary air for combustion) in the above-described hearth incinerator and the method of refluxing to the incinerator side, and the method for carrying out The apparatus for mixing and refluxing to the incinerator side, and the invention of the above-mentioned prior application does not disclose the specific mixing ratio of the recycled gas to the air refluxed to the incinerator side 118,513. Doc 200817638 Control and combustion control in incinerators using backflow of air mixed recycle gas. The present invention has been made in view of such circumstances, and an object thereof is to provide a combustion control device for a hearth incinerator capable of recirculating air mixed back to the incinerator side via a recirculation passage having a recirculation fan with high precision. The gas is subjected to mixing ratio control and combustion control in the incinerator, and the generation of harmful components such as NOx and CO can be suppressed by a relatively simple and low-cost structure, and complete combustion can be achieved with high combustion efficiency. [Means for Solving the Problems] In order to solve the problems of the prior art described above, the invention of claim 1 is a combustion control device for a hearth type incinerator, which is configured to be introduced once from the bottom of the hearth into which the incineration is introduced. After performing one combustion in the combustion chamber on the hearth, the air is subjected to secondary combustion above the combustion chamber, and the recycled gas of a part of the combustion exhaust gas in the combustion chamber and the air supplied through the air passage are mixed and extracted by the air. The fan supplies the air mixed recirculation gas to the furnace via a recirculation passage, and the combustion control device of the hearth incinerator is characterized in that an air flow adjustment mechanism for adjusting an air flow is provided in the air passage, and the other Providing a temperature detecting means for detecting a temperature of the air mixed recirculating gas, and a combustion detecting means for inputting a temperature detecting value of the air mixed recirculating gas from the temperature detecting means, The temperature detection value calculates the air mixed recycle gas The temperature becomes the channel area of the air flow rate adjusting mechanism of the preset target temperature, and the air flow rate adjusting mechanism is controlled to calculate the channel area. Doc 200817638 value. According to the invention of claim 2, in the combustion control device, the air passage is provided with an air flow rate adjusting mechanism for adjusting an air flow rate, and a gas concentration detecting unit and a combustion control unit are provided. The gas concentration detecting means detects the gas concentration of the air-mixed recirculation gas, and the combustion control means inputs a gas concentration detection value of the air-mixed recirculation gas from the gas concentration detecting means, and calculates the air based on the gas concentration detection value. The gas concentration of the mixed recycle gas is a passage area of the air flow rate adjusting mechanism that is a predetermined target gas concentration, and the air flow rate adjusting mechanism is controlled to the channel area calculated value. According to the invention of claim 2, in the invention of claim 3, the NOx concentration detecting means for detecting the NOx concentration in the combustion exhaust gas and the CO concentration detecting means for detecting the CO concentration in the combustion exhaust gas are provided, and the combustion control means is Preferably, the gas concentration detection value input from the gas concentration detecting means, the detection value input from the enthalpy concentration detecting means, and the c 〇 concentration detection value input from the CO concentration detecting means are configured. It is calculated that the gas concentration of the air-mixed recirculation gas is a predetermined target gas concentration, the enthalpy concentration in the combustion exhaust gas is equal to or lower than a predetermined target enthalpy concentration, and the c 〇 concentration in the combustion exhaust gas is set in advance. The passage area of the air flow rate adjustment mechanism equal to or lower than the target CO concentration, and the air flow rate adjustment mechanism is controlled to the channel area calculation value. Further, the invention of claim 4 of the present invention is the above combustion control device 118513. Doc • 10-200817638, wherein an air flow adjustment mechanism for adjusting an air flow is provided in the air passage, and a temperature detecting mechanism, a gas concentration detecting mechanism, and a combustion control mechanism are provided, and the temperature detecting mechanism detects the air mixing. a temperature of the circulating gas, wherein the gas concentration detecting means detects a gas concentration of the air mixed recirculating gas, and the combustion control means inputs a temperature detecting value of the air mixed recirculating gas from the temperature detecting means and the gas concentration detecting The gas concentration detection value of the air-mixed recirculation gas of the mechanism is calculated based on the temperature detection value and the gas concentration detection value, and the temperature of the air-mixed recirculation gas is set to a predetermined target temperature and the air is mixed with the gas of the recirculation gas. The concentration is a passage area of the air flow rate adjustment mechanism that is a predetermined target gas concentration, and the air flow rate adjustment mechanism is controlled to the channel area calculation value. Further, in the invention of claim 5, in the combustion control device, a recirculation gas flow rate adjusting mechanism that adjusts a flow rate of the air mixed recirculation gas is provided in a recirculation gas passage through which the air mixed recirculation gas flows, The air-mixed recirculation gas system supplies air to the above-mentioned recirculated gas and supplies it to the combustor; and provides a gas flow meter and a combustion control mechanism that detects a flow rate of the air-mixed recirculation gas, the combustion The control unit calculates a passage area of the recirculation gas flow rate adjustment mechanism that is a predetermined target flow rate based on a flow rate detection value of the recirculation gas input from the gas flow meter, and calculates the recirculation gas. The flow rate adjustment mechanism controls the channel area calculation value. 118513. In addition to the invention of claim 5, in the invention of claim 6, a recirculation gas outlet is provided at a number of turns of the combustion chamber, and a plurality of the recirculation gas passages are provided to be connected to each of the recirculation gases a recirculation gas flow rate adjusting mechanism that adjusts a flow rate of the air mixed recirculation gas in each of the recirculation gas passages, and a recirculation gas flow rate adjustment mechanism that is configured to detect the dust force of the combustion chamber Preferably, the combustion control means is configured to calculate, according to the combustion chamber relocation detection value from the plurality of combustion chamber pressure detecting means, the respective combustion pressures at the plurality of combustion chamber pressures to be preset target pressures = the passage area of the body flow rate adjusting mechanism, and the respective recirculating gas flow rate adjusting mechanisms are controlled to the channel area calculated value. [Effects of the Invention] In the invention of claim 1, the air flow rate adjusting mechanism is adjusted by the combustion control means based on the temperature detection value of the air-mixing recirculation body of the person in the recirculation fan that carries the air-mixed recirculating gas. Controlling the amount of air in the air mixed recycle gas so that the temperature of the air mixed recycle gas becomes below a predetermined allowable maximum temperature, ie, even for some reason When the temperature rises, the air amount may be increased in accordance with the temperature increase, and the temperature of the air-mixed recirculation gas sucked by the recirculation fan may be appropriately maintained below the allowable maximum temperature. Thereby, overheating of the recirculating fan caused by the above air mixed recirculation gas can be prevented, and high durability can be maintained without using a high cost fan composed of a special heat resistant material for the recirculating fan. 118513. Doc -12 - 200817638 In the invention of claim 2, the combustion control mechanism is used to adjust the air flow rate adjustment based on the gas concentration detection value (preferably the oxygen concentration detection value) of the air mixed with the recirculation gas introduced in the recirculation fan. The opening degree (channel area) of the mechanism controls the amount of air mixed into the air-mixed recirculation gas so that the gas concentration of the air-mixed recirculation gas becomes a predetermined allowable gas concentration, and thus, for example, even if the gas is recycled When the oxygen is consumed and the oxygen concentration is too small, the amount of air can be increased by increasing the opening degree of the air flow rate adjusting means, and stable combustion can be performed in a state of being equal to or higher than the allowable minimum oxygen concentration. Further, according to the invention of claim 3, since the opening degree of the air flow rate adjusting means is adjusted by the combustion control means, the NOx concentration in the combustion exhaust gas can be kept at or below the allowable maximum NOx concentration, and the combustion exhaust can be made. The concentration of CO in the medium is kept below the maximum allowable CO concentration, thereby promoting the purification of the exhaust gas. According to the invention of claim 4, the multiplication effect of the invention of claim 1 and the invention of claim 2 can be obtained. In other words, in the invention of claim 4, (1) the combustion control means adjusts the opening degree of the air flow rate adjusting means based on the temperature detection value of the air-mixed recirculation gas introduced in the recirculation fan, and controls the mixing of the air mixture. The amount of air in the circulating gas is such that the temperature of the air-mixed recirculating gas becomes equal to or lower than a predetermined allowable maximum temperature. Therefore, even if the temperature of the recirculating gas rises for some reason, it may correspond to The temperature rise increases the amount of air, and the air sucked by the above-mentioned recirculation fan is mixed with the temperature of the recirculation gas 118513. Doc •13- 200817638 has been properly maintained below the above allowable maximum temperature. Thereby, it is possible to prevent the overheating of the recirculating fan caused by the above air mixed recirculation gas. 5 It is possible to maintain high durability without using a high-cost fan composed of a special heat-resistant material for the re-circulating fan. (2) adjusting the opening degree (channel area) of the air flow rate adjusting mechanism based on the gas concentration detection value (preferably the oxygen concentration detection value) of the air mixed recirculation gas introduced into the recirculation fan by the combustion control mechanism Controlling the amount of air mixed into the air-mixed recirculation gas so that the gas concentration of the air-mixed recirculation gas becomes a predetermined allowable gas concentration, and thus, for example, even if oxygen in the recirculating gas is consumed, the oxygen concentration is changed. When it is too small, the amount of air may be increased by increasing the opening degree of the air flow rate adjusting means, and stable combustion may be performed in a state of being above the allowable minimum oxygen concentration. In the invention of claim 5, the recirculation gas flow rate adjusting mechanism for adjusting the flow rate of the air mixed recirculation gas is provided in a suction passage (recirculation gas passage) through which the air mixed recirculation gas flows, and based on the detection of the air a flow rate detection value of the recycle gas of the gas flow meter that mixes the flow rate of the recycle gas, and controls the recycle gas flow rate adjustment mechanism to change the flow rate of the recycle gas to a predetermined target flow rate, thereby controlling the recycle The opening degree of the gas flow rate adjusting mechanism is such that the flow rate of the recirculating gas becomes the target flow rate, and the amount of the air mixed recirculating gas as the secondary air can be stably maintained in an amount that the air mixed recirculating gas can be completely burned. Thereby, the combustion state can be averaged to maintain stable combustion. Further, if the invention of claim 6 is constructed, then 118513 is provided in the plural of the combustion chamber. Doc -14- 200817638 a recirculation gas outlet, and a combustion chamber pressure detecting mechanism corresponding to the recirculation gas flow adjustment mechanism, the recirculation gas flow adjustment mechanism being disposed at each recirculation connected to the recirculation gas outlet In the gas passage, the combustion control mechanism is used to detect the pressure of the recirculation gas near the recirculation gas outlet, and the recirculation gas pressure is proportional to the recirculation gas pressure, and the recirculation gas pressure is controlled to become a target. The gas pressure, therefore, the distribution of the amount of air mixed with the recirculation gas to the recirculation gas outlets provided at a plurality of portions of the combustion chamber can be freely adjusted, so that the air mixed with the recirculation gas can be uniformly supplied to the circumferential direction of the combustion chamber. Thereby, the combustion can be averaged. [Embodiment] Hereinafter, the present invention will be described in detail based on the embodiments shown in the drawings. [First Embodiment] Fig. 1 is a configuration diagram of a hearth incinerator according to a first embodiment of the present invention, Fig. 2 is a schematic configuration diagram of a combustion control mechanism according to the first embodiment, and Fig. 3 is the first embodiment. Form of combustion control block diagram. In Fig. 1, 1 is a garbage feed hopper for discharging burned materials such as garbage or industrial waste, and 2 is a hearth type incinerator. In the hearth incinerator 2, from the input port of the garbage feed hopper 1 to the bottom of the furnace, a drying belt hearth 21 mainly constituting the drying belt, a main combustion belt hearth 22 mainly constituting the combustion belt, and main After the post-combustion zone is formed, the combustion belt is placed on the hearth. The drying belt hearth 21 is located on the most upstream side, the main combustion zone hearth 22 is located on the lower side of the drying belt hearth, and the rear combustion zone hearth 23 is located on the lowermost side downstream of the main combustion zone hearth 22. Here, the main combustion zone refers to the burning of the flame on the garbage layer and 118513. Doc -15- 200817638 area. Each of the hearths 21, 22, and 23 includes a moving fire lattice disposed between the fixed fire lattices, and after the garbage (burned matter) is put into the garbage, the garbage is moved in the hearth 21 by the reciprocating movement of the moving fire lattice. Drying, main combustion is carried out in the hearth 22, and finally post-combustion is carried out in the hearth 23. Further, in the present embodiment, the number of the main combustion zone hearths 22 is three, but it may be "solid or plural. 8 is an ash storage tank. Further, the furnace beds 21, 22, and 23 are provided above. The primary combustion chamber 3 is further provided with a secondary combustion chamber 4 above it. 19a, 19b, 19c, and 19d are recirculating gas blowing nozzles disposed toward the secondary combustion chamber 4. Further, the 81 series and the secondary combustion chamber 4 steel furnace connected to the exhaust outlet. The drying belt hearth 21, the combustion belt hearth 22 and the post-combustion belt hearth 23 are provided with primary air pipes 51, 52 (3 in the bellows of the lower part). , 53, primary air is supplied by the primary air pipe. 6 is a primary air supply fan, 5 is a primary air main pipe, and is connected to the fan 6, and each primary air pipe 51 5 (three), 53; 6 The primary air system is sent from the secondary air main pipe 5 to the primary air pipes 51, 52, 53. The primary air pipes 5 1 , 52 , 53 are respectively opened and closed to open and close the primary air pipes. Damper 54, 55, 56. Further, in the primary air main pipe 5, an opening and closing resistance of the primary air main pipe is opened and closed 40 is a recirculation gas extraction port for extracting a portion of the combustion exhaust gas in the primary combustion chamber 3 (which may also be in the secondary combustion chamber 4) as a recirculation gas, from the recirculation gas extraction port 40 The extracted recycle gas is via 118513. Doc -16- 200817638 The recirculation passage 16, the mixed gas passage 14, and the cyclone 12 for separating solid foreign matter in the mixed gas are introduced to the suction passage 31 of the recirculation fan 13. That is, the recirculation gas outlet 40 and the suction passage 31 are connected via the recirculation passage 16, and the suction passage 31 is provided with a gas damper 013 that opens and closes the inlet of the recirculation fan 13. 30 is a mixed air passage, which is branched from the primary air main pipe 5 and connected to the suction passage 31 which is an upstream portion of the recirculation fan 13, and 30a is an air damper (opening and closing damper) for opening and closing the mixed air passage 30, if it is opened The air damper 30a, the primary air from the primary air main pipe 5 is supplied to the inlet of the recirculation fan 13 of the suction passage 31 via the mixed air passage 30, whereby the primary air is mixed into the above-mentioned recirculation gas, and then through the mixed gas passage. 14. The cyclone 12 and the suction passage 31 are introduced into the recirculation fan 13. The air damper 30a can automatically perform opening degree adjustment (flow rate adjustment) by receiving a control signal from a combustion control mechanism 60 to be described later, and adjusts the opening degree of the air damper 30a to flow through the mixed air passage 30. The flow rate of the primary air is adjusted to adjust the mixing ratio of the recirculating gas and the primary air in the air mixed recirculation gas, and the air mixed recirculation gas system is introduced through the mixed gas passage 14, the cyclone 12, and the suction passage 31. A mixed gas of the recycle gas of the circulation fan 13 and the primary air. Then, the air mixed with the primary air mixed by the recirculation fan 13 to the recirculation passage 15 is mixed with the recirculation gas, branched into the two recirculation passages 17, 18, and recirculated through one side. 17 is sent to the side of the 2 lines and then 118513. Doc -17- 200817638 The circulation gas blowing nozzles 19a, 19c are "returned to the other side of the two rows of the recirculating gas blowing nozzles 191", 19d by the recirculation passages on the other side, and are further blown out of the nozzles 19a, 19c by the recirculating gas And 19b, 19d are ejected into the secondary combustion chamber 4. Further, a branch gas damper B33 that opens and closes the recirculation passage π is provided in the recirculation passage 17, and the recirculation passage is opened and closed in the recirculation passage 18. The branch gas damper A32 of 18 is a temperature sensor disposed in the recirculation passage 丨5 for detecting the temperature of the air mixed recirculation gas (the temperature sensing can also be set in the mixed gas passage Μ) The temperature sensor 35 is described below. 36 is an air damper opening degree detector for detecting the opening degree of the air damper 30a. The hearth type incinerator 2 according to the first embodiment of the present invention A combustion control mechanism 60 is provided. The combustion control mechanism 60 is electrically connected to the temperature sensor 35 (including 35a), the air damper 30a, and the air damper opening detector %, and the air sensor is input from the temperature sensor 35. Circulating gas The temperature detection value is input, and the air damper detector 36 is input from the air damper opening detector 36 (the opening degree detection value of the air damper 3, and the air damper 3 is adjusted according to the detection values, and the air mixture is recirculated and recirculated. The mixing ratio of the recirculating gas and the primary air in the gas is controlled to a target mixing ratio so that the temperature of the air mixed recirculating gas becomes the target temperature. When the hearth incinerator 2 is operated, the recirculation gas is taken out. 40. A part of the combustion exhaust gas extracted from the combustion chamber (primary combustion chamber 3 or secondary combustion chamber 4) in the furnace bed is used as a recirculation gas, and is mixed with the primary air from the mixed air passage 30 via the recirculation passage 16, and then Via mixing 118513. Doc •18- 200817638 The gas passage 14, the cyclone 12 and the suction passage 31 are introduced into the recirculation fan 13. Further, the air mixed with the primary air mixed by the recirculation fan 13 to the recirculation passage 15 is mixed with the recirculated gas, branched into the two recirculation passages 17, 18, and sent to the recirculation gas on one side. The nozzles 19a and 19c and the other side of the recirculation gas blowing nozzles 19b and 19d are blown out, and are further discharged into the secondary combustion chamber 4 by the recirculating gas blowing nozzles 19a, 19c and 19b and 19d. In this manner, the recirculating gas composed of a part of the combustion exhaust gas can be cooled by the primary air, and the combustion exhaust gas is diluted by the mixing with the primary air, and then introduced into the recirculation fan 13. Next, the combustion control mechanism and the combustion control sequence of the first embodiment will be described with reference to Figs. 2 and 3 . The combustion control unit 60 of the present embodiment includes a gas temperature comparison unit 61, a reference gas temperature setting unit 62, a gas temperature/air amount setting unit 63, an air amount adjustment amount calculation unit 64, and an air damper opening degree adjustment amount calculation unit 65. The air damper opening degree calculation unit 66 inputs the temperature detection value of the air-mixed recirculation gas detected by the temperature sensor 35 to the gas temperature comparison unit 61 of the combustion control unit 60. The allowable maximum temperature (preferably about 300 ° C) of the air-mixed recirculating gas fed into the recirculation fan 13 is set in the reference gas temperature setting unit 62. Further, the gas temperature comparison unit 61 calculates a temperature deviation which is the temperature detection value of the air-mixed recirculation gas from the temperature sensor 35 and the temperature of the allowable maximum temperature set in the reference gas temperature setting unit 62. 118513. Doc -19- 200817638 Degree deviation. Then, the air damper opening degree calculating means 600 shown in Fig. 2 calculates the opening degree of the air damper 30a in the following order. In Fig. 3, the calculated value of the temperature deviation from the gas temperature comparing unit 61 is input to the air amount adjustment amount calculating unit 64. In the gas temperature/air amount setting unit 63, the amount of air supplied through the air passage 30 and the air and the recirculation gas from the recirculation passage 16 are mixed in advance by a test result or a simulation calculation. The relationship of the above air mixed recycle gas temperature. Further, the air amount adjustment amount calculation unit 64 calculates (extracts) the air amount deviation corresponding to the calculated value of the temperature deviation from the gas temperature comparison unit 61 from the gas temperature/air amount setting unit 63, and outputs it to the air amount/air amount setting unit 63. Air damper opening degree adjustment amount calculation unit 65. The air damper opening degree adjustment amount calculation unit 65 sets the relationship between the air amount and the air damper opening degree as the opening degree characteristic of the air damper 30a, and the air damper opening degree adjustment amount calculation unit 65 The air damper opening degree adjustment amount corresponding to the air amount deviation calculation value from the air amount adjustment amount calculation unit 64 is calculated and output to the air damper opening degree calculation unit 66. The air damper opening degree calculation unit 66 calculates or calculates the opening degree detection value of the air damper 30a input from the air damper opening degree detector 36 by adding or subtracting the air damper opening degree adjustment amount. The air damper opening degree adjustment amount of the portion 65 calculates a target value of the air damper opening degree, that is, an air damper opening degree corresponding to the reference gas temperature, and controls the air damper 30a to the target opening degree. 118513. Doc -20-200817638 In the combustion control device for the hearth incinerator 2 of the first embodiment, the combustion control unit 60 adjusts the temperature detection value of the air-mixed recirculation gas passing through the recirculation fan 丨3. The air damper 3〇a is opened to control the amount of air mixed into the air-mixed recirculation gas so that the temperature of the helium-air mixed recirculation gas becomes lower than a predetermined allowable maximum temperature, and therefore, even for some reason When the temperature of the recirculating gas rises, the amount of air may be increased in accordance with the temperature increase, and the temperature of the air-mixed recirculation gas sucked by the recirculating fan 13 may be appropriately maintained below the allowable maximum temperature. . Thereby, the overheating of the recirculating fan 13 by the air-mixed recirculation gas can be prevented, so that it is not necessary to use a cost-effective fan composed of a special heat-resistant material for the recirculating fan 13, so that high durability can be maintained. [Second Embodiment] Fig. 4 is a configuration diagram of a hearth incinerator according to a second embodiment of the present invention, Fig. 5 is a schematic configuration diagram of a combustion control mechanism according to the second embodiment, and Fig. 6 is a second embodiment. The combustion control block diagram. In the second embodiment of the present invention, the oxygen concentration is used as the gas concentration in the mechanism for detecting the gas concentration of the air-mixing re-circulation body and controlling the opening degree of the air damper 3 ^ based on the gas concentration. Further, instead of the oxygen concentration, the concentration of other components in the air mixed recycle gas such as C 〇 2 may be used. In the hearth incinerator 2 according to the second embodiment of the present invention, as shown in Fig. 4, an oxygen concentration meter 3 (or an oxygen concentration meter 37a) for detecting the oxygen concentration in the air-mixed recirculation gas is provided. Detecting the outlet side of the secondary combustion chamber 4 118513. Doc-21-200817638 The NOx concentration sensor 38 of the ruthenium concentration in the combustion exhaust gas, and the CO concentration sensor 39 for detecting the c〇 concentration. Further, the combustion control mechanism 60 of the present embodiment includes the oxygen concentration comparison unit 71, the reference oxygen concentration setting unit 72, the NOx concentration comparison unit 73, the reference enthalpy concentration setting unit 74, and the CO concentration as shown in Figs. 5 and 6 . Comparison unit 75, reference CO concentration setting unit 76, air amount adjustment amount calculation unit 77, oxygen concentration/air amount setting unit 78, air amount adjustment amount calculation unit 79, krypton concentration/air amount setting unit 80, and air amount adjustment amount calculation The unit 81, the CO concentration/air amount setting unit 82, the air damper opening degree adjustment amount calculation unit 65, and the air damper opening degree calculation unit 66 calculate and mix the air based on the oxygen concentration detection value from the oxygen concentration meter 37. The oxygen concentration of the circulating gas becomes the opening degree of the air damper 30a of the predetermined target oxygen concentration, and the opening degree of the air damper 30a is controlled to the opening degree calculated value. Further, the combustion control unit 60 calculates that the NOx concentration in the combustion exhaust gas is set in advance based on the n〇x concentration detection value from the NOx concentration sensor 38 and the CO concentration detection value from the CO concentration sensor 39. The target ΝΟχ concentration is equal to or lower than the opening degree of the air damper 30a in which the CO concentration in the combustion exhaust gas is equal to or lower than the predetermined target CO concentration, and the opening degree of the air damper 30a is controlled to the opening degree calculated value. Hereinafter, the combustion control mechanism and the combustion control sequence of the second embodiment will be described with reference to Figs. 5 and 6 . In the second embodiment, the air damper opening degree calculation means 600 calculates the opening degree of the air damper 30a based on the oxygen concentration detection value from the oxygen concentration meter 37 (37a). And the following action 118513. Doc -22-200817638 The description will be made with reference to Fig. 6 on the combustion control using the NOx concentration and the CO concentration in the combustion exhaust gas in addition to the above oxygen concentration. In Fig. 6, the oxygen concentration detection value of the air-mixed recirculation gas detected by the oxygen concentration meter 37 (or the oxygen concentration meter 37a) is input to the oxygen concentration comparison unit 71 of the combustion control mechanism 60. The enthalpy concentration detection value in the combustion exhaust gas detected by the NOx concentration sensor 38 is input to the enthalpy concentration comparison unit 73 of the combustion control unit 60. Further, the detected CO concentration in the combustion exhaust gas detected by the CO concentration sensor 39 is input to the CO concentration comparison unit 75 of the combustion control unit 60. The allowable minimum oxygen concentration of the air-mixed recirculation gas fed to the recirculation fan 13 is set in the reference oxygen concentration setting unit 72. The allowable maximum enthalpy concentration in the combustion exhaust gas is set in the reference enthalpy concentration setting unit 74. The allowable maximum CO concentration in the combustion exhaust gas is set in the reference CO concentration setting unit 76. In the oxygen concentration comparison unit 71, the oxygen concentration detection value in the air-mixed recirculation gas from the oxygen concentration meter 37 and the oxygen concentration deviation of the allowable minimum oxygen concentration set in the reference oxygen concentration setting unit 72 are calculated and input to the air. The amount adjustment amount calculation unit 77. Further, the NOx concentration comparing unit 73 calculates the enthalpy concentration deviation value of the enthalpy concentration detected value in the combustion exhaust gas from the NOx concentration sensor 38 and the allowable maximum enthalpy concentration set in the reference enthalpy concentration setting unit 74, and inputs The air amount adjustment amount calculation unit 79 is used. Further, the CO concentration comparison unit 75 calculates the CO concentration detection value and the reference CO concentration setting unit 76 118513 in the combustion exhaust gas from the CO concentration sensor 39. The CO concentration deviation of the allowable maximum CO concentration set in doc -23-200817638 is input to the air amount adjustment amount calculation unit 81. Then, in the oxygen concentration/air amount setting unit 78, the amount of air supplied by the air mixed in the air passage 30 and the mixing of the air and the recirculation from the recirculation passage 16 are set in advance by test results or simulation calculations. The relationship between the oxygen concentration in the above air mixed recycle gas after the gas. Further, in the NOx concentration/air amount setting unit 80, the relationship between the amount of air supplied by the air passage 30 and the concentration of helium in the combustion exhaust gas is set in advance by a test result or a simulation calculation. Further, in the CO concentration/air amount setting unit 82, the relationship between the amount of air supplied by the air passage 30 and the CO concentration in the combustion exhaust gas is set in advance by a test result or an analog calculation. Then, the air amount adjustment amount calculation unit 77 calculates (extracts) the air amount deviation corresponding to the calculated value of the oxygen concentration deviation from the oxygen concentration comparison unit 71 from the oxygen concentration/air amount setting unit 78, and inputs it to Air damper opening degree adjustment amount calculation unit 65. In the air amount adjustment amount calculation unit 79, the air amount deviation corresponding to the calculated value of the enthalpy concentration deviation from the erbium concentration comparison unit 73 is calculated (extracted) from the enthalpy concentration/air amount setting unit 80, and is input to Air damper opening degree adjustment amount calculation unit 65. Further, the air amount adjustment amount calculation unit 81 calculates (extracts) the air amount deviation corresponding to the calculated value of the CO concentration deviation from the CO concentration comparison unit 75 from the CO concentration/air amount setting unit 82, and inputs it to Air damper opening degree adjustment amount calculation unit 65. 118513. Doc -24-200817638 The air damper opening degree adjustment amount calculation unit 65 sets the relationship between the air amount and the air damper opening degree as the opening characteristic of the air damper 3〇a, and adjusts the air damper opening degree. The amount calculation unit 65 sequentially calculates an air damper opening degree adjustment amount based on the deviation of the air amount corresponding to the oxygen concentration deviation, and an air damper based on the air amount deviation corresponding to the NOx concentration deviation. The opening degree adjustment amount and the air damper opening degree adjustment amount based on the air amount deviation corresponding to the CQ concentration deviation, and selecting the optimal air damper opening degree adjustment amount from the air damper opening degree adjustment amount It is input to the air damper opening degree calculation unit %. Then, the air damper opening degree calculation unit 66 adds or subtracts the air damper opening degree adjustment amount calculation unit to the opening degree detection value of the air damper 30a input from the air damper opening degree detector 36. An air damper opening degree adjustment amount of 65, and calculating a target value of the air damper opening degree, that is, an opening degree of the air damper 30a adapted to the reference oxygen concentration or the reference NOx concentration or the reference enthalpy concentration, and The air damper 3〇a is controlled to the target opening degree. The other configuration is the same as that of the first embodiment, and the same reference numerals are used to denote the same members as those of the first embodiment. In the combustion control device for the hearth incinerator 2 of the second embodiment, the combustion control unit 60 adjusts the oxygen concentration detection value of the gas according to the air introduced in the recirculation fan 13 to adjust the value. The opening degree of the air damper 30a controls the amount of air mixed in the air mixed recirculation gas so that the oxygen concentration of the air mixed recirculation gas becomes equal to or higher than a predetermined allowable minimum oxygen concentration, and therefore, even in the recirculating gas Oxygen is subject to H8513. Doc -25- 200817638 The consumption causes the oxygen concentration to become too small, and the amount of air can be increased by increasing the opening degree of the air damper 3〇a, and stable combustion is performed under the above-described allowable minimum oxygen concentration. Further, by adjusting the opening degree of the air damper 3〇a by the combustion control mechanism 60, the concentration of helium in the combustion exhaust gas can be kept below the allowable maximum state concentration, and the concentration of c〇 in the combustion exhaust gas can be made. It is kept below the maximum allowable CO concentration, which promotes the purification of exhaust gas. [Third Embodiment] Fig. 7 is a configuration diagram of a hearth type incinerator according to a third embodiment of the present invention, and Fig. 8 is a view showing the third embodiment according to the oxygen concentration and the temperature of the air mixed recycle gas. Flow chart of combustion control. The third embodiment of the present invention combines the first embodiment shown in Figs. 1 to 3 and the second embodiment shown in Figs. 4 to 6 . That is, in the third embodiment, the combustion control means 6A is used to adjust the temperature detection value of the air-mixed recirculation gas from the temperature sensor 35a (or the temperature sensor 35 in Fig. 1). Controlling the amount of air mixed into the air-mixed recirculation gas by the opening degree of the air damper 3〇a such that the temperature of the air-mixed recirculation gas becomes lower than a predetermined allowable maximum temperature' and detecting the air mixture according to the detection The oxygen concentration detection value of the oxygen concentration meter 37 of the oxygen concentration in the circulating gas is calculated, and the opening degree of the air damper 30a is set such that the oxygen concentration of the air mixed recirculation gas is equal to or higher than the allowable minimum oxygen concentration set in advance. The opening degree of the damper 3〇a is controlled to be the calculated value of the opening degree. Further, in the third embodiment, it is the same as the second embodiment described above, and is in the second embodiment. Doc -26- 200817638 The outlet side of the secondary combustion chamber 4 is provided with a NOx concentration sensor 38 for detecting the NOx concentration in the combustion exhaust gas, and a CO concentration sensor 39 for detecting the CO concentration, and according to the NOx concentration sensor 38 The NOx concentration detection value and the CO concentration detection value from the CO concentration sensor 39 are calculated such that the enthalpy concentration in the combustion exhaust gas is equal to or lower than a predetermined target enthalpy concentration, and the c 〇 concentration in the combustion exhaust gas is made. The opening degree of the air damper 3〇a which is equal to or lower than the preset target CO concentration is set, and the opening degree of the air damper 30a is controlled to the opening degree calculated value. Other configurations are the same as those of the above-described first embodiment, and the same members as those of the first embodiment are denoted by the same reference numerals. Fig. 8 is a flow chart showing the combustion control performed in accordance with the oxygen concentration and the temperature of the air-mixed recirculation gas in the third embodiment, and the combustion control is performed in the following order. That is, 'the oxygen concentration Cg of the air mixed recycle gas is detected by the oxygen concentration meter 37 (step (1)), and the oxygen concentration detection value Cg is compared with the target oxygen concentration cg0 (step (2)), when oxygen The concentration Cg is greater than the target oxygen concentration (: § ( ((^ > cg〇) closes the air damper 3〇a to reduce the amount of air (step (3)), when the oxygen/time Cg is less than the target oxygen concentration Cg0 ( Cg <Cg〇) Open the air damper 3〇a to increase the amount of air (step (4)). Then, after the air damper 3 according to the oxygen concentration is controlled, the opening degree control of the air damper 30a is performed in accordance with the temperature of the air mixed recirculation gas in the following order. That is, In Fig. 8, the temperature of the air mixed recirculation gas is detected by the temperature sensor 35a (or the temperature controller 35 in Fig. i) (step (5)), and the temperature detection value Tg is compared with the target temperature. Tg〇 is compared (step H8513.doc -27- 200817638 (6)), when the temperature detection value Tg is the same as the target temperature Tgo, the opening degree of the air damper 30a is maintained, and when the temperature detection value Tg is higher than When the target temperature Tgo (Tg > Tgo), the air damper 30a is opened to increase the amount of air, and the temperature Tg of the air mixed recirculation gas is lowered (step (7)), when the temperature detection value Tg is lower than the target temperature Tgo (Tg <Tgo) The air damper 30a is turned off to reduce the amount of air, and the temperature Tg of the air mixed recirculation gas is raised (step (8)). According to the third embodiment of the present invention, the multiplication effect of the first embodiment and the second embodiment can be obtained. In the combustion control device of the hearth incinerator 2 of the third embodiment, (1) the combustion control unit 60 adjusts the temperature detection value of the recirculated gas according to the air introduced in the recirculation fan 13 The opening degree of the air damper 30a controls the amount of air mixed into the air mixed recirculation gas so that the temperature of the air mixed recirculation gas becomes equal to or lower than a predetermined allowable maximum temperature, and therefore, even for some reason When the temperature of the circulating gas rises, the amount of air may be increased in accordance with the increase in temperature, and the temperature of the air-mixed recirculating gas sucked by the recirculating fan 13 may be appropriately maintained below the allowable maximum temperature. Thereby, it is possible to prevent overheating of the recirculation fan 13 caused by the above-described air-mixed recirculation gas, and it is possible to maintain high durability without using a high-cost fan composed of a special heat-resistant material for the recirculation fan 13. (2) The combustion control mechanism 60 adjusts the opening degree of the air damper 30a based on the oxygen concentration detection value of the air-mixed recirculation gas introduced in the recirculation fan 13, and controls the air mixed in the air-mixed recirculation gas. 118513.doc -28- 200817638
3〇a之開度使空氣量增加，而一 即便再循環氣體中之氧受到 亦可藉由增大空氣阻尼器 一直在上述容許最小氧濃度 以上之條件下進行穩定燃燒。 又，藉由利用燃燒控制機構6〇調整空氣阻尼器3〇a之開 度，可使燃燒排氣中之NOx濃度一直保持在容許最大 濃度以下、又可使燃燒排氣中之c〇濃度一直保持在容許 袁大CO濃度以下，從而可促進排氣之淨化。 [第4實施形態] 圖9係本發明第4實施形態之爐床式焚化爐之結構圖，圖 1 〇係上述第4實施形態之燃燒控制流程圖。 於本發明之第4實施形態中，除上述第3實施形態之外， 在空氣混合再循環氣體所流通之吸入通道（再循環氣體通 道）3 1中u又有调整空氣混合再循j哀氣體流量之氣體阻尼器 013，该空氣混合再循環氣體係將空氣混合至再循環氣體 中而供給於二次燃燒室4的；並且藉由設於再循環通道i 5 中的混合氣體流量計90檢測空氣混合再循環氣體之流量， 繼而利用燃燒控制機構60，根據來自上述氣體流量計的空 氣混合再循環氣體之流量檢測值，控制氣體阻尼器〇13之 開度，以使該再循環氣體之流量變為預先設定的目標流 量。 亦即，圖10中之步驟（1)〜(8)與圖8所示之上述第3實施形 態的情形相同。 118513.doc -29- 200817638 於圖1 0中，藉由燃燒控制機構60，比較來自混合氣體流 量計90的空氣混合再循環氣體之流量檢測值Qg與預先設定 之目標流量Qg〇(步驟（9))。當上述流量檢測值QgA於目標 流量Qg〇時（Qg>Qg〇) ’關閉氣體阻尼器〇13(嚴格地說，係 減小開度）（步驟（10))，當上述流量檢測值Qg小於目標流量 Qg〇時（Qg<Qg〇)，打開上述氣體阻尼器013(嚴格地說，係 增大開度）（步驟（11))’以此控制空氣混合再循環氣體之流 量以使之變為目標流量。 因此，藉由控制氣體阻尼器013之開度以使再循環氣體 之流量Qg變為目標流量Qgo，可將作為二次空氣的空氣混 合再循環氣體之量穩定地保持於可使該空氣混合再循環氣 體完全燃燒之量，從而可使燃燒狀態平均化而保持穩定燃 燒。 又，於本發明之第4實施形態中，於二次燃燒室4之左右 複數處相對向地設有再循環氣體吹出噴嘴19a、i9c及再循 ( 環氣體吹出喷嘴19b、Bd，於與該等再循環氣體吹出噴嘴 19a、19c及再循環氣體吹出噴嘴191)、19d連接之各再循環 氣體通道17、18中設有調整空氣混合再循環氣體流量的分 支氣體阻尼器B33及分支氣體阻尼器A32，並且於二次燃 燒至4中空氣混合再循環氣體之再循環氣體吹出喷嘴丨9a、 19c及再循環氣體吹出噴f19b、19d附近設有檢測其等之 壓力（以下’稱為再循環氣體壓力）的氣體壓力感測器 B42、及氣體壓力感測器Ac。 如此之第4實施形態構成為，利用燃燒控制機構6〇，根 118513.doc •30- 200817638 據來自對向設置於二次燃燒室4之左右複數處（左側2處、 右側2處）的氣體壓力感測器B42、及氣.體壓力感測器A41的 上述氣體壓力之檢測值，算出使上述複數處之氣體壓力變 為預先設定之目標壓力的各分支氣體阻尼器B33及分支氣 體阻尼器A32之開度，並將各分支氣體阻尼器B33及分支 氣體阻尼器A32之開度控制為算出值。 亦即，於圖10中，藉由燃燒控制機構6〇，比較氣體壓力 感測器B42及氣體壓力感測器A41之氣體壓力檢測值pg與 預先設定之目標氣體壓力Pg0(圖1〇中步驟（丨2))。當上述氣 體壓力檢測值Pg大於目標氣體壓力1^〇時（1>§> pg〇)，關閉 分支氣體阻尼器B33及分支氣體阻尼器A32(嚴格地說，係 減小開度）（步驟（13))，由此減少朝向再循環氣體吹出喷嘴 19a、19c及再循環氣體吹出喷#19b、I9d之空氣混入再循 環氣體量。 當上述氣體壓力檢測值Pg小於目標氣體壓力Pg〇時（pg< Pgo) ’打開分支氣體阻尼器B33及分支氣體阻尼器A32(嚴 格地說，係增大開度）（步驟（14)),由此增加朝向再循環氣 體吹出喷嘴19a、19c及再循環氣體吹出噴嘴19b、19d之空 氣混入再循環氣體量。 由於第4實施形態之爐床式焚化爐2之燃燒控制裝置係如 上述般構成的，因此，可利用再循環氣體量與再循環氣體 壓力成比例此種關係，檢測出再循環氣體吹出噴嘴附近之 再循環氣體壓力，並控制上述分支氣體阻尼器B33及分支 氣體阻尼器A3 2之開度，以使該再循環氣體壓力pg變為目 118513.doc • 31 · 200817638 標氣體壓力Pgo，藉此，可將作為二次空氣的空氣混合再 循環氣體之量穩定地保持為該空氣混合再循環氣體可完全 燃燒之量，從而可使燃燒狀態平均化而保持穩定燃燒。 又’根據來自對向設置於二次燃燒室4之左右複數處（左 側2處、右側2處）之氣體壓力感測器B42、及氣體壓力感測 器A41的上述氣體壓力之檢測值，算出各分支氣體阻尼器 B33及分支氣體阻尼器A32之開度而將各分支氣體阻尼器 B33及分支氣體阻尼器A32之開度控制於算出值，以使上 述複數處之氣體壓力變為預先設定之目標壓力，因此，可 自由地調整對設置在二次燃燒室4之複數處的再循環氣體 吹出噴嘴19a、19c及再循環氣體吹出喷嘴19b、19d進行的 空氣混入再循環氣體量之分配，可將空氣混入再循環氣體 均勻地供給於燃燒室之周方向上，從而可使燃燒平均化。 以上，就本發明之實施形態進行了詳細說明，然而本發 明並未限定於所述實施形態，可依據本發明之技術思想而 進行各種變形及改變。 【圖式簡單說明】 圖1係表示本發明第1實施形態之爐床式焚化爐之結構 圖。 圖2係表示上述第1實施形態中燃燒控制機構之概略結構 圖。 圖3係上述第1實施形態之燃燒控制區塊圖。 圖4係表示本發明第2實施形態之爐床式焚化爐之結構 圖0 118513.doc -32- 200817638 圖5係表示上述第2實施形態中燃燒控制機構之概略結構 圖。 圖6係上述第2實施形態之燃燒控制區塊圖。 圖7係表示本發明第3實施形態之爐床式焚化爐之結構 圖0 圖8係上述第3實施形態之燃燒控制流程圖。 圖9係表示本發明第4實施形態之爐床式焚化爐之結構 圖0 圖10係上述第4實施形態之燃燒控制流程圖。 / 1.. 【主要元件符號說明】 1 2 3 4 5 6 7 、 54 、 55 、 56 8 12 13 013 14 15 、 16 、 17 、 18 19a、19b、19c、19d 垃圾進料斗 爐床式焚化爐 一次燃燒室 二次燃燒室 一次空氣主管 風扇 開閉阻尼器 儲灰槽 旋風分離器 再循環風扇 氣體阻尼器 混合氣體通道 再循環通道 再循環氣體吹出喷嘴 118513.doc -33 - 200817638 21 乾燥帶爐床 22 主燃燒帶爐床 23 後燃燒帶爐床 30 混入空氣通道 30a 空氣阻尼器 31 吸入通道 32 分支氣體阻尼器A 33 分支氣體阻尼器B 35(35a) 溫度感測器 36 空氣阻尼器開度檢測器 37(37a) 氧濃度計 38 NOx濃度感測器 39 CO濃度感測器 40 再循環氣體抽出口 41 氣體壓力感測器A 42 氣體壓力感測器B 51 > 52、53 一次空氣管 60 燃料控制機構 61 溫度比較部 62 基準氣體溫度設定部 63 氣體溫度/空氣量設定部 64、 77 > 79 ^ 81 空氣量調整量算出部 65 空氣阻尼器開度調整量算出部 66 空氣阻尼器開度算出部 118513.doc 34- 200817638 71 氧濃度比較部 72 基準氧濃度設定部 73 NOx濃度比較部 74 基準ΝΟχ濃度設定部 75 CO濃度比較部 76 基準CO濃度設定部 78 氧濃度/空氣量設定部 80 ΝΟχ濃度/空氣量設定部 82 CO濃度/空氣量設定部 90 混合氣體流量計 600 空氣阻尼器開度算出機構 118513.doc -35-The opening of 3〇a increases the amount of air, and even if the oxygen in the recirculating gas is received, stable combustion can be performed under the condition that the air damper is kept above the allowable minimum oxygen concentration. Further, by adjusting the opening degree of the air damper 3〇a by the combustion control mechanism 6〇, the NOx concentration in the combustion exhaust gas can be kept below the allowable maximum concentration, and the c〇 concentration in the combustion exhaust gas can be kept at all times. It is kept below the allowable concentration of CO and CO, which can promote the purification of exhaust gas. [Fourth Embodiment] Fig. 9 is a configuration diagram of a hearth type incinerator according to a fourth embodiment of the present invention, and Fig. 1 is a flowchart of a combustion control in the fourth embodiment. According to the fourth embodiment of the present invention, in addition to the third embodiment, in the suction passage (recirculation gas passage) 31 through which the air-mixed recirculation gas flows, u is adjusted to mix air and then smear gas. a flow gas damper 013 that supplies air to the recirculating gas to be supplied to the secondary combustion chamber 4; and is detected by the mixed gas flow meter 90 provided in the recirculation passage i 5 The flow rate of the air mixed recycle gas, and then the combustion control mechanism 60, controls the opening degree of the gas damper 〇13 based on the flow rate detection value of the air mixed recycle gas from the gas flow meter to make the flow rate of the recycle gas It becomes a preset target flow rate. That is, steps (1) to (8) in Fig. 10 are the same as those in the above-described third embodiment shown in Fig. 8. 118513.doc -29- 200817638 In FIG. 10, the flow detection value Qg of the air mixed recirculation gas from the mixed gas flow meter 90 is compared with the preset target flow rate Qg by the combustion control mechanism 60 (step (9) )). When the flow rate detection value QgA is at the target flow rate Qg ( (Qg > Qg 〇) 'the gas damper 〇 13 is turned off (strictly speaking, the opening degree is decreased) (step (10)), when the flow rate detection value Qg is smaller than When the target flow rate Qg ( (Qg < Qg 〇 ), the gas damper 013 (strictly speaking, the opening degree is increased) (step (11)) is turned on to control the flow rate of the air mixed recirculation gas to make it Target traffic. Therefore, by controlling the opening degree of the gas damper 013 so that the flow rate Qg of the recirculation gas becomes the target flow rate Qgo, the amount of the air mixed recirculation gas as the secondary air can be stably maintained so that the air can be mixed again. The amount of circulating gas is completely combusted so that the combustion state can be averaged to maintain stable combustion. Further, in the fourth embodiment of the present invention, the recirculation gas blowing nozzles 19a and i9c and the recirculation (ring gas blowing nozzles 19b and Bd) are provided in the right and left of the secondary combustion chamber 4, respectively. a branch gas damper B33 and a branch gas damper for adjusting the flow rate of the air mixed recirculation gas are provided in the respective recirculation gas passages 17, 18 to which the recirculating gas blowing nozzles 19a, 19c and the recirculating gas blowing nozzles 191), 19d are connected. A32, and the recirculation gas blowing nozzles 9a, 19c and the recirculating gas blowing nozzles f19b, 19d which are secondary combustion to 4 air mixed recirculation gases are provided with a pressure for detecting them (hereinafter referred to as "recycle gas" Pressure) gas pressure sensor B42, and gas pressure sensor Ac. In the fourth embodiment, the combustion control mechanism 6 is used, and the root 118513.doc • 30-200817638 is derived from the gas which is disposed opposite to the right and left of the secondary combustion chamber 4 (2 on the left side and 2 on the right side). The detected values of the gas pressures of the pressure sensor B42 and the gas pressure sensor A41 calculate the branch gas dampers B33 and the branch gas dampers that cause the gas pressure at the plurality of points to become a predetermined target pressure. The opening degree of A32 is controlled to the calculated value of the opening degree of each branch gas damper B33 and branch gas damper A32. That is, in FIG. 10, the gas pressure detection value pg of the gas pressure sensor B42 and the gas pressure sensor A41 is compared with the preset target gas pressure Pg0 by the combustion control mechanism 6 (steps in FIG. (丨2)). When the gas pressure detection value Pg is greater than the target gas pressure 1^〇 (1 > § > pg 〇), the branch gas damper B33 and the branch gas damper A32 are closed (strictly speaking, the opening degree is decreased) (step (13)), thereby reducing the amount of the recirculated gas mixed into the air of the recirculating gas blowing nozzles 19a and 19c and the recirculating gas blowing nozzles #19b and I9d. When the gas pressure detection value Pg is smaller than the target gas pressure Pg ( (pg < Pgo) 'opens the branch gas damper B33 and the branch gas damper A32 (strictly speaking, increases the opening degree) (step (14)), This increases the amount of recirculated gas mixed into the air of the recirculating gas blowing nozzles 19a and 19c and the recirculating gas blowing nozzles 19b and 19d. Since the combustion control device of the hearth type incinerator 2 of the fourth embodiment is configured as described above, it is possible to detect the vicinity of the recirculation gas blowing nozzle by using the relationship between the amount of the recirculated gas and the pressure of the recirculation gas. Recirculating gas pressure, and controlling the opening degree of the branch gas damper B33 and the branch gas damper A3 2, so that the recirculation gas pressure pg becomes the target gas pressure Pgo, thereby The amount of the air mixed recirculation gas as the secondary air can be stably maintained as the amount at which the air mixed recirculation gas can be completely burned, so that the combustion state can be averaged to maintain stable combustion. Further, it is calculated based on the detected values of the gas pressures from the gas pressure sensor B42 and the gas pressure sensor A41 which are disposed opposite to each other in the right and left plural positions (two on the left side and two on the right side) of the secondary combustion chamber 4. The opening degrees of the branch gas dampers B33 and the branch gas dampers A32 are controlled to the calculated values of the branch gas dampers B33 and the branch gas dampers A32 so that the gas pressure at the plurality of points becomes a predetermined value. Since the target pressure is applied, the distribution of the amount of air mixed with the recirculation gas to the recirculation gas blowing nozzles 19a and 19c and the recirculation gas blowing nozzles 19b and 19d provided in the plurality of secondary combustion chambers 4 can be freely adjusted. The air is mixed into the recirculating gas and uniformly supplied to the circumferential direction of the combustion chamber, so that the combustion can be averaged. The embodiment of the present invention has been described in detail above. However, the present invention is not limited to the embodiment, and various modifications and changes can be made in accordance with the technical idea of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing the configuration of a hearth type incinerator according to a first embodiment of the present invention. Fig. 2 is a view showing a schematic configuration of a combustion control mechanism in the first embodiment. Fig. 3 is a view showing a combustion control block of the first embodiment. Fig. 4 is a view showing the structure of a hearth type incinerator according to a second embodiment of the present invention. Fig. 0 is a view showing a schematic configuration of a combustion control mechanism according to the second embodiment. Fig. 6 is a view showing a combustion control block of the second embodiment. Fig. 7 is a view showing the structure of a hearth type incinerator according to a third embodiment of the present invention. Fig. 0 is a flow chart showing the combustion control of the third embodiment. Fig. 9 is a view showing the structure of a hearth type incinerator according to a fourth embodiment of the present invention. Fig. 10 is a flow chart showing the combustion control of the fourth embodiment. / 1.. [Description of main component symbols] 1 2 3 4 5 6 7 , 54 , 55 , 56 8 12 13 013 14 15 , 16 , 17 , 18 19a , 19b , 19c , 19d Garbage feed hopper hearth incinerator Primary combustion chamber secondary combustion chamber primary air main fan fan opening and closing damper ash storage tank cyclone recirculation fan gas damper mixed gas passage recirculation passage recirculation gas blowing nozzle 118513.doc -33 - 200817638 21 drying belt hearth 22 Main combustion belt hearth 23 Rear combustion belt hearth 30 Mixed air passage 30a Air damper 31 Suction passage 32 Branch gas damper A 33 Branch gas damper B 35 (35a) Temperature sensor 36 Air damper opening detector 37(37a) Oxygen concentration meter 38 NOx concentration sensor 39 CO concentration sensor 40 Recirculation gas extraction port 41 Gas pressure sensor A 42 Gas pressure sensor B 51 > 52, 53 Primary air tube 60 Fuel Control unit 61 Temperature comparison unit 62 Reference gas temperature setting unit 63 Gas temperature/air amount setting unit 64, 77 > 79 ^ 81 Air amount adjustment amount calculation unit 65 Air damper opening degree calculation unit 66 damper opening degree calculation unit 118513.doc 34- 200817638 71 Oxygen concentration comparison unit 72 Reference oxygen concentration setting unit 73 NOx concentration comparison unit 74 Reference enthalpy concentration setting unit 75 CO concentration comparison unit 76 Reference CO concentration setting unit 78 Oxygen concentration/air amount setting unit 80 ΝΟχ concentration/air amount setting unit 82 CO concentration/air amount setting unit 90 Mixed gas flow meter 600 Air damper opening degree calculation mechanism 118513.doc -35-