JP3967843B2

JP3967843B2 - Burner equipment

Info

Publication number: JP3967843B2
Application number: JP08691499A
Authority: JP
Inventors: 努若林; 浩二守家
Original assignee: Osaka Gas Co Ltd
Current assignee: Osaka Gas Co Ltd
Priority date: 1999-03-29
Filing date: 1999-03-29
Publication date: 2007-08-29
Anticipated expiration: 2019-03-29
Also published as: JP2000283422A

Description

【０００１】
【発明の属する技術分野】
本発明は、燃焼用ガスを燃焼するためのバーナ装置に関する。
【０００２】
【従来の技術】
地域発電、地域暖房などを行うために、種々のコージェネレーションシステムが提案され実用に供されている。このようなコージェネレーションシステムの代表的な一つのシステムは、燃焼用ガスを燃焼するためのバーナ装置と、バーナ装置によって燃焼された燃焼ガスによって回転駆動されるガスタービンとを備え、ガスタービンの回転を利用して発電が行われる。
【０００３】
このようなガスタービンに用いられるバーナ装置は、第１のガス供給手段からの燃焼用ガスが供給される一次ノズル手段と、第２のガス供給手段からの燃焼用ガスが供給される二次ノズル手段とを備えている。一次ノズル手段は第１の流路を規定し、第１の流路を流れる空気流に第１のガス供給手段からの燃焼用ガスが噴出され、これによって安定して燃焼する希薄混合ガスが生成される。また、二次ノズル手段は第２の流路を規定し、第２の流路を流れる空気流に第２のガス供給手段からの燃焼用ガスが噴出され、これによって一次ノズル手段の希薄混合ガスよりもガス濃度の低い希薄混合ガスが生成される。このようなバーナ装置では、一次ノズル手段の混合ガスのガス濃度が二次ノズル手段の混合ガスのガス濃度よりも高いので、一次ノズル手段の混合ガスが安定して燃焼し、そしてこの一次ノズル手段の燃焼ガスを利用して二次ノズル手段の混合ガスが燃焼される。燃焼用ガスをこのように燃焼することによって、希薄燃焼が可能となり、また燃焼ガスの燃焼温度を低くすることができ、これによって酸化窒素（ＮＯｘ）の発生を抑えた高効率な燃焼が可能となる。
【０００４】
しかしながら、上述したバーナ装置では、次のとおりの解決すべき問題が存在する。第１のノズル手段を流れる希薄混合ガスのガス濃度は第２のノズル手段の希薄混合ガスのガス濃度よりも濃いので、その燃焼ガスの燃焼温度は高く、一方第２のノズル手段を流れる希薄混合ガスの燃焼温度は第１のノズル手段の燃焼ガスの燃焼温度よりも低くなる傾向にある。一般的に、バーナ装置からの燃焼ガスをガスタービンに送給する場合、送給される燃焼ガスの最高温度がガスタービンの耐熱温度を超えないようにする必要がある。それ故に、上述したバーナ装置においては、燃焼ガスの中心付近の最高温度をガスタービンの耐熱温度、たとえば１２００℃以下に設定する必要があり、このようにしたとき、中心付近から離れた部位の燃焼ガスの燃焼温度が低くなる。その結果、ガスタービンに送給される燃焼ガスの平均温度が低くなり、バーナ装置を含むシステムの熱効率が悪くなる。
【０００５】
これを解決するために、第１のノズル手段を有する第１の流路を第１の円筒状に形成し、これよりも外側に同心に、第２のノズル手段を有する第２の流路を第２の円筒状に配置し第２の流路から第１の流路に、連続したリング状の混合ガス導入口を設けたバーナ装置が考えられる。このバーナ装置は前記バーナ装置よりも燃焼の片寄りが少なくなるが、まだ混合ガス導入口から導入された混合ガスが充分に第１の流路の混合ガスと混合しない。
【０００６】
【発明が解決しようとする課題】
本発明の目的は、バーナ装置における燃焼の片寄りを防止し、燃焼ガスの燃焼温度を均一にして、これによって燃焼ガスの平均温度を高めることができるとともに、安定して燃焼を継続できるバーナ装置を提供することである。
【０００７】
【課題を解決するための手段】
本発明は、第１の円筒状部材から構成され、第１の流路を規定する第１のノズル手段と、
前記第１の円筒状部材の外側に同心状に配置される第２の円筒状部材から構成され、第２の流路を規定する第２のノズル手段と、
前記第１の流路に燃焼用ガスを供給するための第１のガス供給手段と、
前記第２の流路に燃焼用ガスを供給するための第２のガス供給手段と、
前記第１および第２の流路に空気を供給するための空気流路とを備え、
前記第１のガス供給手段からの燃焼用ガスは前記空気流路から前記第１の流路を通して流れる空気流に向けて噴出され、これによって安定に燃焼できる希薄混合ガスが第１の流路で生成され、
前記第２のガス供給手段からの燃焼用ガスは前記空気流路から前記第２の流路を通して流れる空気流に向けて噴出され、これによって前記第１の流路の希薄混合ガスよりもさらにガス濃度の低い希薄混合ガスが第２の流路で生成され、
前記第１の流路と前記第２の流路との間には、さらに、前記第２の流路の希薄混合ガスの一部を前記第１の流路に導くための断続したリング状の混合ガス導入口が設けられていることを特徴とするバーナ装置である。
【０００８】
本発明者らは、混合ガス導入口の形状を種々実験で検討した結果、断続したリング状にすれば、混合ガス導入口から導入された混合ガスが第１の流路の混合ガスと充分に混合することを確認し、本発明を完成するに至った。
【０００９】
本発明に従えば、第１の円筒状部材から構成される第１の流路を流れる空気流には第１のガス供給手段からの燃焼用ガスが噴出され、これによって安定して燃焼する希薄混合ガスが生成される。また、第１の円筒状部材の外側に同心状に配置される第２の円筒状部材から構成される第２の流路を流れる空気流には第２のガス供給手段からの燃焼用ガスが噴出され、これによって第１のノズル手段の混合ガスよりもガス濃度の薄い希薄混合ガスが生成される。さらに、第１の流路と第２の流路との間には断続したリング状の混合ガス導入口が設けられているので、第２の流路にて生成された混合ガスの一部が第１の流路に導入され、これによって第１の流路の混合ガスと第１の流路に導入された第２の流路の混合ガスとの混合が充分に行われ、ガス濃度が均一化して燃焼状態の片寄りが非常に少なくなる。その結果、第１のノズル手段からの燃焼ガスの燃焼温度と第２のノズル手段からの燃焼ガスの燃焼温度がほぼ等しくなり、燃焼ガスをガスタービンに送給する場合、燃焼ガスの平均温度をガスタービンの耐熱温度に近づけることができ、バーナ装置を含むシステムの効率を高めることができる。
【００１０】
また本発明は、前記第２の流路を流れる空気流の流速は、前記第１の流路を流れる空気流の流速よりも速いことを特徴とする。
【００１１】
本発明に従えば、第２の流路を流れる空気流の流速は第１の流路を流れる空気流の流速よりも速いので、第２の流路の希薄な混合ガスの一部が混合ガス導入手段を介して第１の流路に導入され、第１の流路を流れる混合ガスの濃度が薄められ、これにより高温となる混合ガスが減少する。
【００１２】
また本発明は、前記第２の流路の半径方向断面積Ｓ２と前記第１の流路の半径方向断面積Ｓ１との比（Ｓ２／Ｓ１）は２．０〜１０．０であり、前記混合ガス導入口は３〜１６個の等面積の開口部と閉口部とを有する断続したリング状であり、前記第２の流路の半径方向断面積Ｓ２と前記混合ガス導入口の開口部の半径方向断面積Ｓ３との比（Ｓ２／Ｓ３）は１．０〜３０．０であることを特徴とする。
【００１３】
本発明に従えば、第２の流路の断面積Ｓ２と第１の流路の断面積Ｓ１との比（Ｓ２／Ｓ１）が２．０〜１０．０である。前記断面積比が２．０未満では、第１の流路の中央部における燃焼ガスの燃焼温度は部分的に高温となり、排出ガス中のＮＯｘ値を減少させることができない。またこれが１０．０を超えると、第２の流路のガスが吹き消されるおそれがある。第２の流路の混合ガスは、それのみでは安定して燃焼できない程度に希薄な混合ガスであり、第１の流路の混合ガスはそれのみで安定して燃焼できる混合ガスであり、第２の流路の混合ガスは第１の流路の混合ガスによってその燃焼が助けられる。すなわち第２の流路の混合ガスは、第１の流路の混合ガスによって保炎されている。したがって前記断面積比が大きくなる程、保炎効果が少なくなり、これが１０．０を超えると、安定して燃焼を継続できなくなるおそれがある。この断面積比（Ｓ２／Ｓ１）の範囲は、次に述べる断面積比（Ｓ２／Ｓ３）の範囲とともに本発明者が実験的に求めたものである。
【００１４】
また本発明に従えば、第２の流路の断面積Ｓ２と混合ガス導入手段の導入開口の断面積Ｓ３との比（Ｓ２／Ｓ３）が１．０〜３０．０である。前記断面積比が１．０未満では、第２の流路の混合ガスが導入手段を介して大量に第１の流路に流れ、第２の流路の混合ガスの量が減少し、燃焼が第１の流路で主として生じ、燃焼器出口の温度が不均一になる。またこれが３０．０を超えると、第２の流路の混合ガスがほとんど第１の流路に導入されず、第１の流路の燃焼ガスが高温となり、排出ガス中のＮＯｘ値を減少させることができない。
【００１５】
さらに本発明に従えば、混合ガス導入口は、３〜１６個の等面積の開口部と閉口部とを有する断続したリング状である。開口部と閉口部との個数を各２以下にすると、先に述べた連続したリング状に近い構造となり、混合ガス導入口から導入された混合ガスが充分に第１の流路の混合ガスと混合しない。開口部と閉口部との個数は多くする程、導入口から導入された混合ガスがよく第１の流路の混合ガスと混合されるが、この個数を１７個以上に増加しても、混合状態は大きく改善されない上に、製作に手間がかかる。
【００１６】
また本発明は、前記第１の円筒状部材は、円筒状のノズル本体と先端ノズルとから構成され、前記先端ノズルは、内径が大きい大径部と、前記大径部よりも内径が小さい小径部と、前記大径部と前記小径部とを接続するテーパ部とを有し、前記先端ノズルの前記大径部が前記ノズル本体の先端部に装着され、前記混合ガス導入口の前記開口部は、前記ノズル本体と前記先端ノズルの前記大径部との間に断続して形成され、前記先端ノズルの前記テーパ部は、前記大径部から半径方向内方に延び、前記テーパ部の前記先端ノズルとのテーパ角度が２０〜１２０度に設定されていることを特徴とする。
【００１７】
本発明に従えば、第１のノズル手段はノズル本体と先端ノズルから構成され、ノズル本体と先端ノズルの大径部との間に混合ガス導入開口が規定されているので、第２の流路を流れる混合ガスはこの混合ガス導入開口を通して第１の流路に所要のとおりに導入される。また、先端ノズルにはテーパ角度が２０〜１２０度であるテーパ部が設けられているので、混合ガス導入開口を通して導入された混合ガスはこのテーパ部に案内されて半径方向内方に案内され、これによって第２の流路から導入された混合ガスは半径方向内方に流れて第１の流路を流れる混合ガスに実質上均一に混合される。このテーパ角度が２０度未満では、テーパ部の長さが長くなり好ましくない。また１２０度を超えると、混合ガス導入開口を通して導入される混合ガス流に抵抗を生じ、円滑に導入されない。このテーパ角度の範囲は、本発明者が実験的に求めたものである。
【００１８】
さらに本発明は、前記第１の流路を流れる希薄混合ガスを点火するための点火手段が設けられ、前記混合ガス導入手段の前記導入開口は前記点火手段の配設部位よりも下流側に設けられていることを特徴とする。
【００１９】
本発明に従えば、混合ガス導入手段は点火手段の配設部位の下流側に配設されているので、点火手段には第１の流路を通して流れる混合ガス、すなわち第２の流路からの混合ガスが含まれていない安定して燃焼できる混合ガスが送給され、したがって点火手段によって第１の流路の混合ガスを確実に点火することができる。
【００２０】
【発明の実施の形態】
以下、添付図面を参照して、本発明に従うバーナ装置の一実施形態について説明する。図１は、本発明に従うバーナ装置の一実施形態を簡略的に示す断面図であり、図２は、図１に示すバーナ装置の一部を拡大して示す断面図であり、図３は、図２におけるＩＩＩ−ＩＩＩ線による断面図である。
【００２１】
図１を参照して、図示のバーナ装置は、番号２で示すバーナテスト用ケースのディフューザ部を備え、このディフューザ部２に円筒状のテストケース４が装着され、テストケース４は図１において右方に延びている。テストケース４内には燃焼ケース６が配設されている。燃焼ケース６は円筒状で、テストケース４に同心状に配設されている。燃焼ケース６の一端部（図１において左端部）はディフューザ部２に装着され、その他端部は図１において右方に延びている。ディフューザ部２には、また、空気流路８が形成され、この空気流路８を通して燃焼用空気が燃焼ケース６の一端部に供給される。この燃焼用空気は、たとえば、コンプレッサ（図示せず）によって圧縮された状態にて送給される。
【００２２】
この実施形態では、燃焼ケース６の一端部内に第１のノズル手段１０、第２のノズル手段１２および燃焼筒１４が配設されている。図２をも参照して、ディフューザ部２の一部には取付支持ブロック１６が装着され、この取付支持ブロック１６に外ガス送給管１８の一端部が装着され、この外ガス送給管１８の他端部に噴射ノズル体２０が装着されている。噴射ノズル体２０は内部に空間２２が形成され、この内部空間２２を軸線方向に貫通して仕切スリーブ２４が装着され、この仕切スリーブ２４によって上記内部空間２２が内側の第１空間２２ａとこの第１空間２２ａの外側の第２空間２２ｂとに仕切られている。外ガス送給管１８の他端部は、噴射ノズル体２０の第２空間２２ｂに連通されている。また、外ガス送給管１８の内側には内ガス送給管２６が同心状に配設され、その一端部が取付支持ブロック１６に装着され、その他端部が噴射ノズル体２０に装着されている。この内ガス送給管２６は、噴射ノズル体２０の第１空間２２ａに連通されている。
【００２３】
内ガス送給管２６には、これに燃焼用ガスを供給するための第１のガス供給手段が接続されている。第１のガス供給手段は、燃焼用ガスが蓄えられたガス供給源（図示せず）、ガス供給源から燃焼用ガスを導くガス送給管２８およびガス送給管２８を通して送給されるガスの流量を制御する流量制御手段、たとえば流量制御弁（図示せず）を含み、ガス送給管２８が内ガス送給管２６に連通されている。また、外ガス送給管１８には、これに燃焼用ガスを供給するための第２のガス供給手段が接続されている。第２のガス供給手段は、燃焼用ガスが蓄えられたガス供給源（図示せず）、ガス供給源から燃焼用ガスを導くガス送給管３０およびガス送給管３０を通して送給されるガスの流量を制御する流量制御手段、たとえば流量制御弁（図示せず）を含み、ガス送給管３０が外ガス送給管１８に連通されている。なお、燃焼用ガスとしては、たとえば、都市ガスを好都合に用いることができる。
【００２４】
第１のノズル手段１０は、噴射ノズル体２０の外側に装着されている。図示の第１のノズル手段１０は第１の円筒状部材３２から構成され、この第１の円筒状部材３２の一端部には周方向に間隔を置いて半径方向内方に突出する内突起３４が一体的に設けられ、複数個の内突起３４を介して第１の円筒状部材３２が噴射ノズル体２０に同心状に支持されている。このように構成されているので、第１の円筒状部材３２と噴射ノズル体２０との間には、周方向のほぼ全域に渡って環状の間隙が存在し、空気流路８からの空気はかかる間隙を通して第１の円筒状部材３２内に導かれる。
【００２５】
噴射ノズル体２０の先端部と第１の円筒状部材３２の一端部との間には、第１のスワラ３６が配設されている。第１のスワラ３６は、周方向に間隔を置いて配設された複数個のフィンから構成され、噴射ノズル体２０と第１の円筒状部材３２との間隙を通して流れる空気は、かかる第１のスワラ３６によって旋回流となり、旋回流の状態で第１の円筒状部材３２内を図１および図２において右方に流れる。第１のスワラ３６は第１の円筒状部材３２と一体的に形成してもよく、また別体に形成して両者の間に介在させてもよい。
【００２６】
第２のノズル手段１２は、第１のノズル手段１０の外側に装着されている。図示の第２のノズル手段１２は第２の円筒状部材３８から構成され、この第２の円筒状部材３８の一端部が第２のスワラ４０を介して第１の円筒状部材３２の外側にこれに同心状に装着されている。第２のスワラ４０は、周方向に間隔を置いて配設された複数個のフィンから構成され、第１の円筒状部材３２と第２の円筒状部材３８との間に導かれる空気は、かかる第２のスワラ４０の作用によって旋回流となり、旋回流の状態で第２の円筒状部材３８内を図１および図２において右方に流れる。この第２のスワラ４０は、第２の円筒状部材３８と一体的に形成してもよく、また別体に形成して第１および第２の円筒状部材３２，３８の間に介在させてもよい。
【００２７】
第２の円筒状部材３８の一端部には半径方向外方に突出する環状フランジ４２が一体的に設けられ、この環状フランジ４２の先端部に燃焼筒１４の一端部が取付ねじ４４によって取付けられている。燃焼筒１４は円筒状部材から構成され、第１および第２の円筒状部材３２，３８に同心状に配設され、この燃焼筒１４と燃焼ケース６との間にも環状の外空間が存在する。
【００２８】
この実施形態では、噴射ノズル体２０先端部には周方向に間隔を置いて複数個の第１噴出孔４６が形成され、これら第１噴出孔４６が噴射ノズル体２０の第１空間２２ａに連通している。また、噴射ノズル体２０の中間部には半径方向に延びる第２噴出孔４８が周方向に間隔を置いて形成され、これら第２噴出孔４８が噴射ノズル体２０の第２空間２２ｂに連通している。さらに、第１円筒状部材３２の内突起３４には貫通孔５０が形成され、かかる貫通孔５０が対応する第２噴出孔４８に接続されている。
【００２９】
このように構成されているので、ガス送給管２８を通して供給される燃焼用ガスは、内ガス送給管２６を通して噴射ノズル体２０の第１空間２２ａに送給され、第１噴出孔４６を通して噴出される。第１のノズル手段１０は、図１および図２に示すとおり、第１の円筒状部材３２によって第１の流路４５を規定し、空気流路８を流れる空気の一部は噴射ノズル体２０と第１の円筒状部材３２との間を通して第１の流路４５に導かれ、第１噴出孔４６から噴出される燃焼用ガスは、第１のスワラ３６によって旋回流となって流れる空気流に向けて噴出され、旋回流の作用によって実質上均一に混合されて混合ガス（燃焼用ガスと空気との希薄混合ガス）となる。この第１の流路４５の混合ガスの空気比は、たとえば１．４〜１．９程度の安定して燃焼する範囲に設定される。なお、第１のガス供給手段の流量制御手段（図示せず）を操作することによって、第１噴出孔４６から噴出される燃焼用ガスの噴出量を制御することができる。また、ガス送給管３０を通して供給される燃焼用ガスは、外ガス送給管１８を通して噴射ノズル体２０の第２空間２２ｂに送給され、第２噴出孔４８および第１の円筒状部材３２の貫通孔５０を通して第１の円筒状部材３２の外側に噴出される。第２のノズル手段１２は、図１および図２に示すとおり、第１の円筒状部材３２の外側に第２の円筒状部材３８によって環状の第２の流路４７を規定し、空気流路８を流れる空気の残りの一部は第１の円筒状部材３２と第２の円筒状部材３８との間を通して第２の流路４７に導かれ、第２噴出孔４８から貫通孔５０を通して噴出される燃焼用ガスは、第２のスワラ４０によって旋回流となって流れる空気流に向けて噴出され、旋回流の作用によって実質上均一に混合されて混合ガス（燃焼用ガスと空気との希薄混合ガス）となる。この第２の流路４７の混合ガスの空気比は、たとえば２．０程度に設定される。なお、第２のガス供給手段の流量制御手段（図示せず）を操作することによって、第２噴出孔４８から噴出される燃焼用混合ガスの噴出量を制御することができる。
【００３０】
空気流路８を通して流れる空気の残部は燃焼筒１４と燃焼ケース６との間の空間５１を通して流れる。この実施形態では、燃焼筒１４には周方向および軸線方向に間隔を置いて複数個の空気孔５２が形成されており、空間５１を通して流れる空気はこれら空気孔５２を通して燃焼筒１４内に導入される。空気孔５２を通して導入される空気は燃焼筒１４の内周面に沿って流れる空気層を生成し、かかる空気層によって燃焼筒１４が冷却される。これら空気孔５２は、燃焼筒１４の一部を半径方向外方に折曲することによって形成することができる。また、後述する如くして燃焼して燃焼筒１４内を流れる燃焼ガスの温度が異常に上昇しないように、必要に応じて、燃焼筒１４に希釈孔（図示せず）を設けることができ、このように希釈孔を設けた場合、空間５１を流れる空気が希釈孔を通して燃焼筒１４内に導入され、導入した空気によって燃焼ガスの温度が低下される。なお、燃焼筒１４が異常高温に上昇しない場合、空気孔５２を省略することもできる。
【００３１】
この実施形態では、図１に示すとおり、第１のノズル手段１０の先端部、すなわち第１の円筒状部材３２の他端部と、第２のノズル手段１２の先端部、すなわち第２の円筒状部材３８の他端部とは、実質上同じ位置またはほぼ同じ位置まで延びており、また燃焼筒１４の先端部は第１および第２のノズル手段１０，１２を越えてさらに図１において右方に延びている。したがって、第１の流路４５の混合ガスによる燃焼火炎は第１の円筒状部材３２の内部もしくは先端部から図１において右方に生成され、また第２の流路４７の混合ガスによる燃焼火炎は第２の円筒状部材３８の先端部から図１において右方に発生し、これら燃焼火炎は燃焼筒１４内にて所要のとおりに燃焼される。
【００３２】
この実施形態では、第１の流路４５を流れる希薄混合ガスのガス濃度は第２の流路４７を流れる希薄混合ガスのガス濃度よりも濃くなるように設定されている。そして、このことに関連して、混合ガスを点火するための点火手段５６の点火部が第１の流路４５内に突出している。点火手段５６は細長い点火部材５８を備え、その基部がテストケース４に装着され、その先端部が燃焼ケース６、燃焼筒１４、第２の円筒状部材３８および第１の円筒状部材３２を貫通して第１の流路４５に突出している。点火部材５８の先端点火部は、第１の流路４５を流れる混合ガスに向けて火花を発生し、かかる火花によって第１の流路４５の安定して燃焼できる混合ガスが点火燃焼される。そして、第１の流路４５にて発生した燃焼ガスの火炎が第２の流路４７を流れる混合ガスに伝播され、かかる火炎の伝播によって第２の流路４７の混合ガスが燃焼される。なお、第１および第２のノズル手段１０，１２として流量制御を行うことができるものを採用する場合、この点火手段５６を第１および第２の流路４５，４７からの混合ガスが混合される領域の下流側に設けることができる。
【００３３】
また、噴射ノズル体２０と第１の円筒状部材３２との間隙は、第１の円筒状部材３２と第２の円筒状部材３８との間隙よりも小さく設定されており、したがって第１の流路４５に流入する空気は、第１の流路４５の入口部において絞られ、その後下流側において第１の流路の断面積が大きく増大するので、この第１の流路４５を流れる空気流の流速は比較的遅く、これに対して、第２の流路４７を流れる空気流の流速は比較的速くなる。
【００３４】
燃焼筒１４の先端部には、さらに筒状の導出筒６０が設けられている。導出筒６０は、図１において右方に延び、その先端部は先細に形成されており、燃焼筒１４から導出筒６０の一端部に導かれた燃焼ガスはこの導出筒６０内を流れてその先細先端部に集められて下流側に流れる。導出筒６０の先端側にはガスタービン６２が配設され、燃焼筒１４内で燃焼された燃焼ガスは導出筒６０を通してガスタービン６２に送給され、ガスタービン６２はバーナ装置からの燃焼ガスによって回転駆動される。なお、導出筒６０の先端部は、燃焼ケース６の先端部に装着された支持プレート６４によって支持されている。
【００３５】
この実施形態では、第２の流路４７の希薄混合ガスの一部が第１の流路４５の希薄混合ガスに混合されるように構成されている。図１および図２ともに図３を参照してさらに説明すると、この実施形態では、第１のノズル手段１０の第１の円筒状部材３２に混合ガス導入手段が設けられている。図示の第１の円筒状部材３２は、円筒状のノズル本体７２とこのノズル本体７２の先端部に装着される先端ノズル７４から構成され、ノズル本体７２の一端部（図１および図２において左端部）が噴射ノズル体２０に装着されている。ノズル体７２は一端部近傍から他端部まで実質上同じ内径であり、その一端部は半径方向外方に幾分湾曲されており、これによって空気流路８を流れる空気は、かかる湾曲一端部に案内されて噴射ノズル体２０とノズル本体７２との間隙に導かれる。先端ノズル７４は、内径が大きい大径部７６と、内径が小さい小径部７８と、大径部７６および小径部７８を接続するテーパ部８０とから構成され、テーパ部８０は半径方向内方に向けてテーパ状に延びている。本実施の形態では、小径部７８の内径はノズル本体７２の内径と実質上等しく、大径部７６の内径は小径部７８およびノズル本体７２の内径よりも大きく設定されている。
【００３６】
本実施形態では、ノズル本体７２の他端部に先端ノズル７４の大径部７６が６個の等面積の開口部８２と閉口部８４とを介して装着されている。このように先端ノズル７４が装着されているので、図３に示すとおり、ノズル本体７２の他端部外周面と先端ノズル７４の大径部７６の内周面との間に扇形の６個の開口部８２が形成され、この開口部８２が混合ガス導入口として機能する。このように導入開口が設けられているので、第２の流路４７を流れる希薄混合ガスはこの導入口を通して第１の流路４５に導入され、第１の流路４５を流れる希薄混合ガスに充分混合される。したがって、第２の流路４７からの混合ガスによって第１の流路４５の混合ガスのガス濃度が薄められ、これによって第１の流路４５の混合ガスと第２の流路４７の混合ガスとのガス濃度の均一化が図られる。また、第２の流路４７からの混合ガスは６個の開口部８２と６個の閉口部８４とが交互に設けられた断続したリング状の導入口を通して第１の流路４５に導入されるので、第１の流路４５の実質上全周に渡って第２の流路４７からの混合ガスを導入することができ、導入混合ガスの片寄りを防止することができる。
【００３７】
このような先端ノズル７４を用いた場合、テーパ部８０の先端ノズル７４とのテーパ角度θ（図２）、すなわちテーパ部８０の半径方向内方への傾斜角度を２０〜１２０度に設定するのが望ましい。このように設定することによって、導入口を通して導入された混合ガスは先端ノズル７４のテーパ部８０に案内されて半径方向内方に流れ、第１の流路４５を流れる混合ガスに一層均一に混合されるようになる。なお、この実施形態では、ノズル本体７２と先端ノズル７４とを閉口部８４で塞ぎ溶接によって固着している。また、この実施形態では、テーパ部８０は直線状に延びているが、必ずしも直線状である必要はなく、所定形状の曲線状に形成することができる。
【００３８】
このようなバーナ装置では、図３に示すように、６個の開口部８２および６個の閉口部８４を含む図２のＩＩＩ−ＩＩＩ線における断面において、第２の流路４７の半径方向断面積Ｓ２と第１の流路４５の半径方向断面積Ｓ１との比（Ｓ２／Ｓ１）を２．０〜１０．０に設定するのが望ましい。このように設定することによって、第２の流路４７の断面積Ｓ２が第１の流路４５の断面積Ｓ１より２倍以上大きくなり、これによって第１の流路４５を通して流れる混合ガス（この混合ガスのガ濃度は、第２の流路４７を流れる混合ガスのガス濃度よりも濃い）の流量が少なくなり、燃焼筒１４の中央部、換言すると第１の流路４５に対応する燃焼領域の燃焼ガスの燃焼温度が抑えられ、ＮＯｘの発生を少なくすることができる。また、第２の流路４７の断面積Ｓ２が第１の流路４５の断面積Ｓ１の１０倍以下とされ、これによって第１の流路４５を通して流れる混合ガスの流量が第２の流路４７を通して流れる混合ガスの量に対し過小とならず、安定して燃焼する第１の流路４５を流れるガスによって、さらに希薄な第２の流路４７を流れるガスの燃焼を助け、全体として安定した燃焼が継続できる。
【００３９】
図２において、第２の流路４７の半径方向断面積Ｓ２と導入口の半径方向断面積（６個の開口部８２の合計断面積）Ｓ３との比（Ｓ２／Ｓ３）を１．０〜３０．０に設定するのが望ましい。このように設定することによって、第２の流路４７の断面積Ｓ２が導入口の断面積Ｓ３よりも大きくなり、これによって第２の流路４７から導入口を通して第１の流路４５に導入される混合ガスの導入量が過剰に多くなることがなく、第１の流路４７を流れる混合ガスのガス濃度が薄くなることを防止することができる。また、第２の流路４７の断面積Ｓ２が導入口の断面積Ｓ３よりも３０倍を超えて大きくならず、これによって第２の流路４７から導入口を通して第１の流路４５に導入される混合ガスの導入量が過小にならず、第１の流路４５に第２の流路４７のガスを混合する効果を損なわない。
【００４０】
この実施形態では、また、点火手段５６の点火部材５８は、第１のノズル手段１０のノズル本体７２の他端部近傍、具体的には混合ガスの流れ方向に見て導入開口８４の上流側に配設される。このように構成することによって、第１の流路４５を流れる混合ガス、すなわち第２の流路４７からの混合ガスが導入される前の安定して燃焼するガス濃度の混合ガスが点火部材５８に送給されるようになり、点火手段５６による点火性能が低下することが回避できる。
【００４１】
このようなバーナ装置では、第１の流路４５を流れる混合ガスに第２の流路４７を流れる混合ガスの一部が送給され、これによって点火手段５６の下流側にて第１の流路４５の混合ガスが第２の流路４７からの混合ガスによって薄められ、第１の流路４５と第２の流路４７の混合ガスのガス濃度をほぼ均一化し、燃焼ガスの燃焼温度を燃焼筒１４の半径方向断面のほぼ全域において実質上均一にすることができる。このように燃焼ガスの燃焼温度を平均化することによって、燃焼ガスをガスタービン６２に送給する場合、燃焼温度の平均値をガスタービン６２の耐熱温度により近づけることができ、バーナ装置を含むガスタービンシステムの効率の向上を図ることができる。
【００４２】
〔実施例および比較例〕
本発明のバーナ装置の効果を確認するために、実施例として、図１〜図３に示す実施形態のバーナ装置を用いて燃焼ガスの燃焼実験を行った。用いたバーナ装置における各部材の寸法などは、次のとおりであった。噴射ノズル体については、直径１．３ｍｍの第１噴出孔を周方向に実質上等間隔を置いて８個設け、また直径２．６ｍｍの第２噴出孔を周方向に実質上等間隔をおいて８個設けた。また、第１のノズル手段については、内径３６ｍｍ、長さ１０２ｍｍのノズル本体と、内径４６ｍｍ、長さ１１ｍｍの大径部、内径３６ｍｍ、長さ１６ｍｍの小径部およびこれら両者を接続する長さ５ｍｍのテーパ部を有し、テーパ部のテーパ角度が４５度である先端ノズルとを用い、先端ノズルの大径部を８個の閉口部によってノズル本体に取付けて第１の円筒状部材を構成した。また、第２のノズル手段については、内径７０ｍｍ、長さ１００ｍｍの第２の円筒状部材を用いた。このような第１および第２の円筒状部材を用いることによって、それらの肉厚を考慮し、第１の流路の半径方向断面積を１０１８ｍｍ²に、第２の流路の半径方向断面積を２０３８ｍｍ²に、また導入口の半径方向断面積を２０２ｍｍ²に設定した。さらに、燃焼筒１４として内径１４３ｍｍ、長さ３５８ｍｍの円筒状部材を用いた。この円筒状部材には、口元部（図１および図２において左端部）に周方向に実質上等間隔を置いて直径６ｍｍの空気孔を８個設け、またこの口元部より先端側に、周方向に実質上等間隔を置いて直径１．２ｍｍの空気孔を３６個設けた空気孔組を長手方向に８組設けた。
【００４３】
このようなバーナ装置を用い、燃焼実験において、空気流路を通して温度３５０℃の空気を流量７００Ｎｍ³／Ｈの割合で送給した。送給された空気は、その約４％が第１の流路を通して、その約５５％が第２の流路を通して、またその約４１％が燃焼筒の外側を通して流れ、この燃焼筒の外側を流れる空気は、燃焼筒の空気孔を通して燃焼筒内に流入した。燃焼用ガスとしてメタンを用い、１．０Ｎｍ³／Ｈの割合で噴射ノズル体の第１噴出孔を通して第１の流路に噴出させるとともに、２４．７Ｎｍ³／Ｈの割合で噴射ノズル体の第２噴出孔を通して第２の流路に噴出させた。送給した空気およびメタンを混合して混合ガスとし、点火部材で点火させて混合ガスを燃焼させて燃焼ガスを生成した。
【００４４】
そして、このように混合ガスを燃焼して燃焼筒の先端における燃焼ガスの温度を測定したところ平均燃焼温度が１０３７℃であり、このときの燃焼温度の温度差が±２６℃であった。また酸素濃度０％に換算した排出ＮＯｘ濃度は１５ｐｐｍであった。この結果から、燃焼筒のほぼ全域における燃焼温度がほぼ均一であることが確認できた。なお、燃焼温度の測定個所は、燃焼筒の先端にて直径方向に実質上等間隔を置いて７個の温度センサを設けて各測定個所の燃焼温度を測定した。またＮＯｘ濃度は温度センサを外した状態で各測定箇所から燃焼排ガスを混合採取し、その混合ガスのを分析して求めた。
【００４５】
この実施例において、さらに、第２の流路に送給される燃焼ガスの送給量を制御してその送給量を絞ったところ、送給量を１０％まで絞ったところでバーナ装置の燃焼が消え、ターンダウンレシオ（送給量１００％を基準にして、燃焼ガスの送給量をどこまで絞れるかを示す割合）は１：１０であった。
【００４６】
比較例として、図２における切断線ＩＩＩ−ＩＩＩによる断面図が図４の構成のバーナ装置を用い、また空気および燃焼ガスの送給条件も実施例と同様にして燃焼実験を行い、燃焼ガスの温度を実施例と同様にして測定した。なお、先端ノズル７４９の形状は、実施例と同じであるが、先端ノズルの大径部を４個のピン８６によってノズル本体７２に溶接した。導入口８２ａは、リング状に形成され、その断面積は４０５ｍｍ²であった。このときの平均燃焼温度は、１０４０℃、燃焼温度の温度差は±４０℃、酸素濃度０％に換算したＮＯｘ濃度は３５ｐｐｍであった。また実施例と同一の方法で測定したターンダウンレシオは１：４であった。
【００４７】
【発明の効果】
本発明の請求項１記載のバーナ装置によれば、第１の円筒状部材から構成される第１のノズル手段の第１の流路を流れる空気流には第１のガス供給手段からの燃焼用ガスが噴出され、これによって安定して燃焼できる希薄混合ガスが生成される。また、第１の円筒状部材の外側に同心状に配置される第２の円筒状部材から構成される第２のノズル手段の第２の流路を流れる空気流には第２のガス供給手段からの燃焼用ガスが噴出され、これによって第１のノズル手段の混合ガスよりもガス濃度の薄い希薄混合ガスが生成される。さらに、第１の流路と第２の流路との間には断続したリング状の混合ガス導入口が設けられているので、第２の流路にて生成された混合ガスの一部が第１の流路に導入され、これによって第１の流路の混合ガスと第２の流路の混合ガスのガス濃度が均一化して燃焼状態の片寄りが非常に少なくなる。その結果、第１のノズル手段からの燃焼ガスの燃焼温度と第２のノズル手段からの燃焼ガスの燃焼温度がほぼ等しくなり、燃焼ガスをガスタービンに送給する場合、燃焼ガスの平均温度をガスタービンの耐熱温度に近づけることができ、バーナ装置を含むシステムの効率を高めることができる。
【００４８】
また本発明の請求項２記載のバーナ装置によれば、第２の流路を流れる空気流の流速は第１の流路を流れる空気流の流速よりも速いので、第２の流路の希薄な混合ガスの一部が混合ガス導入手段を介して第１の流路に導入され、第１の流路を流れる混合ガスの濃度が薄められ、これにより高温となる混合ガスが減少する。
【００４９】
また本発明の請求項３記載のバーナ装置によれば、第２の流路の断面積Ｓ２と第１の流路の断面積Ｓ１との比が２．０〜１０．０であるので、第１の流路の中央部における燃焼ガスの燃焼温度が部分的に高くなることを抑えること、および第２流路の希薄混合ガスを安定して燃焼させることができる。また、第２の流路の断面積と混合ガス導入口の断面積との比が１．０〜３０．０であるので、第２の流路の混合ガスが適量第１の流路に導入され、第１の流路の混合ガスのガス濃度が最適に保持され、燃焼器出口の温度分布を均一にできる。さらに前記混合ガス導入口は、３〜１６個の等面積の開口部と閉口部とを有し、これによって第２の流路から導入された混合ガスは第１の流路の混合ガスと均一に混合される。
【００５０】
また本発明の請求項４記載のバーナ装置によれば、第１のノズル手段はノズル本体と先端ノズルから構成され、ノズル本体と先端ノズルの大径部との間に混合ガス導入開口が規定されているので、第２の流路を流れる混合ガスはこの混合ガス導入開口を通して第１の流路に所要のとおりに導入される。また、先端ノズルにはテーパ角度が２０〜１２０度であるテーパ部が設けられているので、混合ガス導入開口を通して導入された混合ガスはこのテーパ部に案内されて半径方向内方に案内され、これによって第２の流路から導入された混合ガスは半径方向内方に流れて第１の流路を流れる混合ガスに実質上均一に混合される。
【００５１】
さらに本発明の請求項５記載のバーナ装置によれば、混合ガス導入手段は点火手段の配設部位の下流側に配設されているので、点火手段には第１の流路を通して流れる混合ガス、すなわち第２の流路からの混合ガスが含まれていない混合ガスが送給され、したがって点火手段によって安定に燃焼できる第１の流路の混合ガスを確実に点火することができる。
【図面の簡単な説明】
【図１】本発明に従うバーナ装置の一実施形態を簡略的に示す断面図である。
【図２】図１のバーナ装置の要部を簡略的に示す拡大断面図である。
【図３】図２におけるＩＩＩ−ＩＩＩ線による断面図である。
【図４】従来技術における図３に相当する断面図である。
【符号の説明】
２ディフューザ部
４テストケース
６バーナケース
８空気流路
１０第１のノズル手段
１２第２のノズル手段
１４燃焼筒
１８外ガス送給管
２０噴射ノズル体
２６内ガス送給管
３２第１の円筒状部材
３８第２の円筒状部材
４５第１の流路
４６第１噴出孔
４７第２の流路
４８第２噴出孔
５６点火手段
６２ガスタービン
７２ノズル本体
７４先端ノズル
７６大径部８４
７８小径部
８０テーパ部
８２開口部
８４閉口部[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a burner device for burning combustion gas.
[0002]
[Prior art]
Various cogeneration systems have been proposed and put into practical use in order to perform local power generation and district heating. One typical system of such a cogeneration system includes a burner device for combusting combustion gas, and a gas turbine that is rotationally driven by the combustion gas burned by the burner device. Power is generated using
[0003]
The burner device used in such a gas turbine includes a primary nozzle means to which combustion gas is supplied from a first gas supply means, and a secondary nozzle to which combustion gas is supplied from a second gas supply means. Means. The primary nozzle means defines a first flow path, and a combustion gas from the first gas supply means is jetted into the air flow flowing through the first flow path, thereby generating a lean mixed gas that stably burns. Is done. The secondary nozzle means defines a second flow path, and the combustion gas from the second gas supply means is jetted into the air flow flowing through the second flow path, whereby the lean mixed gas of the primary nozzle means A lean mixed gas having a lower gas concentration is produced. In such a burner device, since the gas concentration of the mixed gas of the primary nozzle means is higher than the gas concentration of the mixed gas of the secondary nozzle means, the mixed gas of the primary nozzle means burns stably, and this primary nozzle means The mixed gas of the secondary nozzle means is burned using the combustion gas. By burning the combustion gas in this way, lean combustion is possible, and the combustion temperature of the combustion gas can be lowered, thereby enabling highly efficient combustion with reduced generation of nitrogen oxide (NOx). Become.
[0004]
However, the burner apparatus described above has the following problems to be solved. Since the gas concentration of the lean mixed gas flowing through the first nozzle means is higher than the gas concentration of the lean mixed gas of the second nozzle means, the combustion temperature of the combustion gas is high, while the lean mixture flowing through the second nozzle means The combustion temperature of the gas tends to be lower than the combustion temperature of the combustion gas of the first nozzle means. Generally, when the combustion gas from the burner device is supplied to the gas turbine, it is necessary to prevent the maximum temperature of the supplied combustion gas from exceeding the heat resistant temperature of the gas turbine. Therefore, in the burner apparatus described above, it is necessary to set the maximum temperature near the center of the combustion gas to the heat resistant temperature of the gas turbine, for example, 1200 ° C. or less. Gas combustion temperature is lowered. As a result, the average temperature of the combustion gas supplied to the gas turbine is lowered, and the thermal efficiency of the system including the burner device is deteriorated.
[0005]
In order to solve this, the first flow path having the first nozzle means is formed in a first cylindrical shape, and the second flow path having the second nozzle means is formed concentrically outside the first flow path. A burner apparatus in which a continuous ring-shaped mixed gas inlet is provided from the second flow path to the first flow path in a second cylindrical shape is conceivable. This burner device is less displaced than the burner device, but the mixed gas introduced from the mixed gas introduction port is not sufficiently mixed with the mixed gas in the first flow path.
[0006]
[Problems to be solved by the invention]
An object of the present invention is to prevent a deviation of combustion in a burner device, to make the combustion temperature of the combustion gas uniform, thereby increasing the average temperature of the combustion gas, and capable of continuing the combustion stably. Is to provide.
[0007]
[Means for Solving the Problems]
The present invention comprises a first nozzle means comprising a first cylindrical member and defining a first flow path;
A second nozzle means comprising a second cylindrical member disposed concentrically outside the first cylindrical member, and defining a second flow path;
First gas supply means for supplying combustion gas to the first flow path;
Second gas supply means for supplying combustion gas to the second flow path;
An air flow path for supplying air to the first and second flow paths,
Combustion gas from the first gas supply means is ejected from the air flow path toward the air flow flowing through the first flow path, and a lean mixed gas that can be stably burned by this is flown in the first flow path. Generated
Combustion gas from the second gas supply means is ejected from the air flow channel toward the air flow flowing through the second flow channel, thereby further gas than the lean mixed gas in the first flow channel. A lean mixed gas having a low concentration is generated in the second flow path,
Between the first flow path and the second flow path, an intermittent ring-like shape for guiding a part of the lean mixed gas of the second flow path to the first flow path is further provided. A burner apparatus characterized in that a mixed gas inlet is provided.
[0008]
As a result of studying the shape of the mixed gas introduction port through various experiments, the inventors of the present invention have found that the mixed gas introduced from the mixed gas introduction port is sufficiently combined with the mixed gas in the first flow path if the ring shape is intermittent. It was confirmed that they were mixed, and the present invention was completed.
[0009]
According to the present invention, the combustion gas from the first gas supply means is jetted into the air flow flowing through the first flow path constituted by the first cylindrical member, and thereby the lean gas is stably burned. A mixed gas is produced. In addition, combustion gas from the second gas supply means is contained in the air flow flowing through the second flow path constituted by the second cylindrical member arranged concentrically outside the first cylindrical member. As a result, a lean mixed gas having a gas concentration lower than that of the mixed gas of the first nozzle means is generated. Furthermore, since an intermittent ring-shaped mixed gas inlet is provided between the first flow path and the second flow path, a part of the mixed gas generated in the second flow path is Introduced into the first flow path, the mixed gas of the first flow path and the mixed gas of the second flow path introduced into the first flow path are sufficiently mixed, and the gas concentration is uniform. And the deviation of the combustion state becomes very small. As a result, the combustion temperature of the combustion gas from the first nozzle means becomes substantially equal to the combustion temperature of the combustion gas from the second nozzle means, and when the combustion gas is fed to the gas turbine, the average temperature of the combustion gas is The heat resistance temperature of the gas turbine can be approached, and the efficiency of the system including the burner device can be increased.
[0010]
Further, the present invention is characterized in that the flow velocity of the air flow flowing through the second flow path is faster than the flow velocity of the air flow flowing through the first flow path.
[0011]
According to the present invention, since the flow velocity of the air flow through the second flow path is faster than the flow velocity of the air flow through the first flow path, a part of the lean mixed gas in the second flow path is mixed gas. The concentration of the mixed gas that is introduced into the first flow path through the introducing means and flows through the first flow path is reduced, and thereby the mixed gas that becomes high temperature is reduced.
[0012]
In the present invention, the ratio (S2 / S1) between the radial cross-sectional area S2 of the second flow path and the radial cross-sectional area S1 of the first flow path is 2.0 to 10.0, The mixed gas introduction port is an intermittent ring shape having 3 to 16 equal-area openings and closing portions, and the radial cross-sectional area S2 of the second flow path and the opening of the mixed gas introduction port The ratio (S2 / S3) to the radial sectional area S3 is 1.0 to 30.0.
[0013]
According to the present invention, the ratio (S2 / S1) between the cross-sectional area S2 of the second flow path and the cross-sectional area S1 of the first flow path is 2.0 to 10.0. When the cross-sectional area ratio is less than 2.0, the combustion temperature of the combustion gas in the central portion of the first flow path becomes partially high, and the NOx value in the exhaust gas cannot be reduced. Moreover, when this exceeds 10.0, there exists a possibility that the gas of a 2nd flow path may be blown off. The mixed gas in the second flow path is a gas mixture that is so thin that it cannot be stably burned by itself, and the mixed gas in the first flow path is a mixed gas that can be burned stably by itself, Combustion of the mixed gas in the two flow paths is aided by the mixed gas in the first flow path. In other words, the mixed gas in the second flow path is held by the mixed gas in the first flow path. Therefore, as the cross-sectional area ratio increases, the flame holding effect decreases, and if it exceeds 10.0, combustion may not be continued stably. The range of the cross-sectional area ratio (S2 / S1) is experimentally determined by the present inventor together with the range of the cross-sectional area ratio (S2 / S3) described below.
[0014]
According to the invention, the ratio (S2 / S3) between the cross-sectional area S2 of the second flow path and the cross-sectional area S3 of the introduction opening of the mixed gas introducing means is 1.0 to 30.0. If the cross-sectional area ratio is less than 1.0, the mixed gas in the second flow path flows in a large amount to the first flow path through the introducing means, and the amount of the mixed gas in the second flow path is reduced and combustion occurs. Mainly occurs in the first flow path, and the temperature of the combustor outlet becomes non-uniform. If this exceeds 30.0, almost no mixed gas in the second flow path is introduced into the first flow path, the combustion gas in the first flow path becomes high temperature, and the NOx value in the exhaust gas is reduced. I can't.
[0015]
Furthermore, according to the present invention, the mixed gas introduction port is an intermittent ring shape having 3 to 16 equal-area openings and closed portions. When the number of openings and closing portions is 2 or less, the structure is similar to the continuous ring shape described above, and the mixed gas introduced from the mixed gas introduction port is sufficiently mixed with the mixed gas in the first flow path. Do not mix. The larger the number of openings and closing parts, the better the mixed gas introduced from the inlet is mixed with the mixed gas in the first flow path, but even if this number is increased to 17 or more, the mixed gas is mixed. The condition is not greatly improved, and it takes time to make.
[0016]
In the present invention, the first cylindrical member includes a cylindrical nozzle body and a tip nozzle, and the tip nozzle has a large diameter portion having a large inner diameter and a small diameter having a smaller inner diameter than the large diameter portion. And a tapered portion connecting the large diameter portion and the small diameter portion, the large diameter portion of the tip nozzle is mounted on the tip portion of the nozzle body, and the opening portion of the mixed gas inlet Is formed intermittently between the nozzle body and the large-diameter portion of the tip nozzle, and the tapered portion of the tip nozzle extends radially inward from the large-diameter portion, and the taper portion The taper angle with the tip nozzle is set to 20 to 120 degrees.
[0017]
According to the present invention, the first nozzle means is composed of the nozzle body and the tip nozzle, and the mixed gas introduction opening is defined between the nozzle body and the large-diameter portion of the tip nozzle. The mixed gas flowing through the gas is introduced into the first flow path as required through the mixed gas introduction opening. Further, since the tip nozzle is provided with a taper portion having a taper angle of 20 to 120 degrees, the mixed gas introduced through the mixed gas introduction opening is guided to the taper portion and guided inward in the radial direction, As a result, the mixed gas introduced from the second flow path flows radially inward and is substantially uniformly mixed with the mixed gas flowing through the first flow path. When the taper angle is less than 20 degrees, the length of the taper portion becomes long, which is not preferable. On the other hand, if it exceeds 120 degrees, resistance is generated in the mixed gas flow introduced through the mixed gas introduction opening, and the mixed gas flow is not smoothly introduced. The range of the taper angle is obtained experimentally by the inventor.
[0018]
Further, the present invention is provided with an ignition means for igniting the lean mixed gas flowing through the first flow path, and the introduction opening of the mixed gas introduction means is provided on the downstream side of the site where the ignition means is provided. It is characterized by being.
[0019]
According to the present invention, since the mixed gas introducing means is disposed downstream of the portion where the ignition means is disposed, the mixed gas flowing through the first flow path to the ignition means, that is, from the second flow path. A mixed gas that does not contain the mixed gas and can be combusted stably is fed, and therefore, the mixed gas in the first flow path can be reliably ignited by the ignition means.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a burner device according to the present invention will be described with reference to the accompanying drawings. FIG. 1 is a cross-sectional view schematically showing an embodiment of a burner device according to the present invention, FIG. 2 is a cross-sectional view showing an enlarged part of the burner device shown in FIG. 1, and FIG. It is sectional drawing by the III-III line in FIG.
[0021]
Referring to FIG. 1, the burner device shown includes a diffuser portion of a burner test case denoted by reference numeral 2, and a cylindrical test case 4 is attached to the diffuser portion 2, and the test case 4 is shown on the right side in FIG. It extends towards. A combustion case 6 is disposed in the test case 4. The combustion case 6 is cylindrical and is disposed concentrically with the test case 4. One end portion (left end portion in FIG. 1) of the combustion case 6 is attached to the diffuser portion 2, and the other end portion extends rightward in FIG. An air flow path 8 is also formed in the diffuser portion 2, and combustion air is supplied to one end portion of the combustion case 6 through the air flow path 8. The combustion air is supplied in a state compressed by a compressor (not shown), for example.
[0022]
In this embodiment, the first nozzle means 10, the second nozzle means 12, and the combustion cylinder 14 are disposed in one end portion of the combustion case 6. Referring also to FIG. 2, a mounting support block 16 is attached to a part of the diffuser portion 2, and one end portion of the external gas supply pipe 18 is attached to the mounting support block 16, and the external gas supply pipe 18 is attached. An injection nozzle body 20 is attached to the other end of the nozzle. The injection nozzle body 20 has a space 22 formed therein, and a partition sleeve 24 is mounted through the internal space 22 in the axial direction. The partition sleeve 24 allows the internal space 22 to be connected to the inner first space 22a and the first space 22a. It is partitioned into a second space 22b outside the first space 22a. The other end of the outer gas supply pipe 18 communicates with the second space 22 b of the injection nozzle body 20. An inner gas feed pipe 26 is concentrically disposed inside the outer gas feed pipe 18, one end of which is attached to the mounting support block 16, and the other end is attached to the injection nozzle body 20. Yes. The inner gas supply pipe 26 communicates with the first space 22 a of the injection nozzle body 20.
[0023]
The internal gas feed pipe 26 is connected to a first gas supply means for supplying combustion gas thereto. The first gas supply means includes a gas supply source (not shown) in which combustion gas is stored, a gas supply pipe 28 that leads the combustion gas from the gas supply source, and a gas supplied through the gas supply pipe 28. The gas supply pipe 28 is communicated with the internal gas supply pipe 26. The flow control means includes a flow control valve (not shown), for example. The outer gas supply pipe 18 is connected to second gas supply means for supplying combustion gas thereto. The second gas supply means includes a gas supply source (not shown) in which combustion gas is stored, a gas supply pipe 30 that guides the combustion gas from the gas supply source, and a gas supplied through the gas supply pipe 30 The gas supply pipe 30 is communicated with the external gas supply pipe 18. The gas supply pipe 30 includes a flow control means for controlling the flow rate of the gas, for example, a flow control valve (not shown). For example, city gas can be conveniently used as the combustion gas.
[0024]
The first nozzle means 10 is attached to the outside of the injection nozzle body 20. The illustrated first nozzle means 10 is composed of a first cylindrical member 32, and an inner protrusion 34 projecting radially inwardly at one end of the first cylindrical member 32 at a circumferential interval. Are integrally provided, and the first cylindrical member 32 is concentrically supported by the injection nozzle body 20 via a plurality of inner protrusions 34. Since it is configured in this way, an annular gap exists between the first cylindrical member 32 and the injection nozzle body 20 in almost the entire circumferential direction, and the air from the air flow path 8 is It is guided into the first cylindrical member 32 through the gap.
[0025]
A first swirler 36 is disposed between the tip of the injection nozzle body 20 and one end of the first cylindrical member 32. The first swirler 36 is composed of a plurality of fins arranged at intervals in the circumferential direction, and the air flowing through the gap between the injection nozzle body 20 and the first cylindrical member 32 is the first swirler 36. A swirl flow is generated by the swirler 36 and flows in the first cylindrical member 32 to the right in FIGS. 1 and 2 in the swirl flow state. The first swirler 36 may be formed integrally with the first cylindrical member 32, or may be formed separately and interposed between the two.
[0026]
The second nozzle means 12 is mounted on the outside of the first nozzle means 10. The illustrated second nozzle means 12 is composed of a second cylindrical member 38, and one end of the second cylindrical member 38 is located outside the first cylindrical member 32 via a second swirler 40. It is mounted concentrically on this. The second swirler 40 is composed of a plurality of fins arranged at intervals in the circumferential direction, and the air guided between the first cylindrical member 32 and the second cylindrical member 38 is: A swirl flow is generated by the action of the second swirler 40 and flows in the second cylindrical member 38 to the right in FIG. 1 and FIG. 2 in the swirl state. The second swirler 40 may be formed integrally with the second cylindrical member 38, or may be formed separately and interposed between the first and second cylindrical members 32, 38. Also good.
[0027]
An annular flange 42 projecting radially outward is integrally provided at one end portion of the second cylindrical member 38, and one end portion of the combustion cylinder 14 is attached to the distal end portion of the annular flange 42 by a mounting screw 44. ing. The combustion cylinder 14 is formed of a cylindrical member, and is disposed concentrically with the first and second cylindrical members 32 and 38, and an annular outer space exists between the combustion cylinder 14 and the combustion case 6. To do.
[0028]
In this embodiment, a plurality of first ejection holes 46 are formed at the distal end portion of the ejection nozzle body 20 at intervals in the circumferential direction, and these first ejection holes 46 communicate with the first space 22 a of the ejection nozzle body 20. is doing. In addition, second ejection holes 48 extending in the radial direction are formed in the middle portion of the ejection nozzle body 20 at intervals in the circumferential direction, and the second ejection holes 48 communicate with the second space 22 b of the ejection nozzle body 20. ing. Furthermore, a through hole 50 is formed in the inner protrusion 34 of the first cylindrical member 32, and the through hole 50 is connected to the corresponding second ejection hole 48.
[0029]
With this configuration, the combustion gas supplied through the gas supply pipe 28 is supplied to the first space 22 a of the injection nozzle body 20 through the inner gas supply pipe 26 and through the first injection hole 46. Erupted. As shown in FIGS. 1 and 2, the first nozzle means 10 defines the first flow path 45 by the first cylindrical member 32, and a part of the air flowing through the air flow path 8 is the injection nozzle body 20. And the first cylindrical member 32 are introduced into the first flow path 45 and the combustion gas ejected from the first ejection holes 46 flows as a swirl flow by the first swirler 36. And mixed substantially uniformly by the action of the swirling flow to become a mixed gas (a lean mixed gas of combustion gas and air). The air ratio of the mixed gas in the first flow path 45 is set to a range in which stable combustion is performed, for example, about 1.4 to 1.9. Note that the amount of combustion gas ejected from the first ejection hole 46 can be controlled by operating a flow rate control means (not shown) of the first gas supply means. The combustion gas supplied through the gas supply pipe 30 is supplied to the second space 22b of the injection nozzle body 20 through the outer gas supply pipe 18, and the second injection hole 48 and the first cylindrical member 32 are supplied. Are ejected to the outside of the first cylindrical member 32 through the through hole 50. As shown in FIGS. 1 and 2, the second nozzle means 12 defines an annular second flow path 47 by a second cylindrical member 38 outside the first cylindrical member 32, and an air flow path. The remaining part of the air flowing through 8 is guided to the second flow path 47 through the space between the first cylindrical member 32 and the second cylindrical member 38, and is ejected from the second ejection hole 48 through the through hole 50. The combustion gas is ejected toward the air flow that flows as a swirl flow by the second swirler 40, and is substantially uniformly mixed by the action of the swirl flow to be mixed gas (a lean mixture of combustion gas and air). Mixed gas). The air ratio of the mixed gas in the second flow path 47 is set to about 2.0, for example. Note that by operating a flow rate control means (not shown) of the second gas supply means, it is possible to control the ejection amount of the combustion mixed gas ejected from the second ejection holes 48.
[0030]
The remainder of the air flowing through the air flow path 8 flows through the space 51 between the combustion cylinder 14 and the combustion case 6. In this embodiment, a plurality of air holes 52 are formed in the combustion cylinder 14 at intervals in the circumferential direction and the axial direction, and air flowing through the space 51 is introduced into the combustion cylinder 14 through these air holes 52. The The air introduced through the air holes 52 generates an air layer that flows along the inner peripheral surface of the combustion cylinder 14, and the combustion cylinder 14 is cooled by the air layer. These air holes 52 can be formed by bending a part of the combustion cylinder 14 outward in the radial direction. In addition, a dilution hole (not shown) can be provided in the combustion cylinder 14 as necessary so that the temperature of the combustion gas that burns and flows in the combustion cylinder 14 as described later does not rise abnormally. When the dilution hole is provided in this way, the air flowing through the space 51 is introduced into the combustion cylinder 14 through the dilution hole, and the temperature of the combustion gas is lowered by the introduced air. If the combustion cylinder 14 does not rise to an abnormally high temperature, the air holes 52 can be omitted.
[0031]
In this embodiment, as shown in FIG. 1, the tip of the first nozzle means 10, that is, the other end of the first cylindrical member 32, and the tip of the second nozzle means 12, that is, the second cylinder. The other end of the member 38 extends to substantially the same position or substantially the same position, and the tip of the combustion cylinder 14 extends beyond the first and second nozzle means 10 and 12 and further to the right in FIG. It extends toward. Therefore, the combustion flame by the mixed gas in the first flow path 45 is generated rightward in FIG. 1 from the inside or the front end portion of the first cylindrical member 32, and the combustion flame by the mixed gas in the second flow path 47. Is generated to the right in FIG. 1 from the tip of the second cylindrical member 38, and these combustion flames are burned in the combustion cylinder 14 as required.
[0032]
In this embodiment, the gas concentration of the lean mixed gas flowing through the first flow path 45 is set to be higher than the gas concentration of the lean mixed gas flowing through the second flow path 47. In relation to this, the ignition part of the ignition means 56 for igniting the mixed gas protrudes into the first flow path 45. The ignition means 56 includes an elongated ignition member 58, the base of which is attached to the test case 4, and the tip of the ignition means 56 passes through the combustion case 6, the combustion cylinder 14, the second cylindrical member 38, and the first cylindrical member 32. And protrudes into the first flow path 45. The front ignition part of the ignition member 58 generates a spark toward the mixed gas flowing through the first flow path 45, and the mixed gas that can be stably burned in the first flow path 45 is ignited and burned by the spark. The flame of the combustion gas generated in the first flow path 45 is propagated to the mixed gas flowing in the second flow path 47, and the mixed gas in the second flow path 47 is combusted by the propagation of the flame. When the first and second nozzle means 10 and 12 are capable of controlling the flow rate, the ignition means 56 is mixed with the mixed gas from the first and second flow paths 45 and 47. It can be provided downstream of the area.
[0033]
Further, the gap between the injection nozzle body 20 and the first cylindrical member 32 is set to be smaller than the gap between the first cylindrical member 32 and the second cylindrical member 38. The air flowing into the channel 45 is throttled at the inlet of the first channel 45, and then the cross-sectional area of the first channel greatly increases on the downstream side. Therefore, the air flow flowing through the first channel 45 On the other hand, the flow velocity of the air flow through the second flow path 47 is relatively high.
[0034]
A cylindrical lead-out cylinder 60 is further provided at the tip of the combustion cylinder 14. The lead-out cylinder 60 extends to the right in FIG. 1 and has a tapered tip. Combustion gas introduced from the combustion cylinder 14 to one end of the lead-out cylinder 60 flows through the lead-out cylinder 60 and is It collects at the tapered tip and flows downstream. A gas turbine 62 is disposed on the leading end side of the lead-out cylinder 60, and the combustion gas burned in the combustion cylinder 14 is supplied to the gas turbine 62 through the lead-out cylinder 60. The gas turbine 62 is driven by the combustion gas from the burner device. Driven by rotation. Note that the leading end of the lead-out cylinder 60 is supported by a support plate 64 attached to the leading end of the combustion case 6.
[0035]
In this embodiment, a part of the lean mixed gas in the second flow path 47 is configured to be mixed with the lean mixed gas in the first flow path 45. 1 and FIG. 2 will be further described with reference to FIG. 3. In this embodiment, the first cylindrical member 32 of the first nozzle means 10 is provided with a mixed gas introducing means. The illustrated first cylindrical member 32 includes a cylindrical nozzle body 72 and a tip nozzle 74 attached to the tip of the nozzle body 72. One end of the nozzle body 72 (the left end in FIGS. 1 and 2). Part) is mounted on the injection nozzle body 20. The nozzle body 72 has substantially the same inner diameter from the vicinity of one end portion to the other end portion, and one end portion thereof is somewhat curved outward in the radial direction, whereby the air flowing through the air flow path 8 is To the gap between the injection nozzle body 20 and the nozzle body 72. The tip nozzle 74 includes a large-diameter portion 76 having a large inner diameter, a small-diameter portion 78 having a small inner diameter, and a tapered portion 80 that connects the large-diameter portion 76 and the small-diameter portion 78, and the tapered portion 80 is radially inward. It extends in a tapered shape. In the present embodiment, the inner diameter of the small diameter portion 78 is substantially equal to the inner diameter of the nozzle body 72, and the inner diameter of the large diameter portion 76 is set larger than the inner diameters of the small diameter portion 78 and the nozzle body 72.
[0036]
In the present embodiment, the large-diameter portion 76 of the tip nozzle 74 is attached to the other end portion of the nozzle body 72 through six equal-area openings 82 and closing portions 84. Since the tip nozzle 74 is mounted in this manner, as shown in FIG. 3, there are six fan-shaped spaces between the outer peripheral surface of the other end portion of the nozzle body 72 and the inner peripheral surface of the large-diameter portion 76 of the tip nozzle 74. An opening 82 is formed, and this opening 82 functions as a mixed gas inlet. Since the introduction opening is provided in this way, the lean mixed gas flowing through the second flow path 47 is introduced into the first flow path 45 through the introduction port, and the diluted mixed gas flowing through the first flow path 45 is converted into the lean mixed gas flowing through the first flow path 45. Mix thoroughly. Therefore, the gas concentration of the mixed gas in the first flow path 45 is diluted by the mixed gas from the second flow path 47, and thereby, the mixed gas in the first flow path 45 and the mixed gas in the second flow path 47. The gas concentration is made uniform. The mixed gas from the second flow path 47 is introduced into the first flow path 45 through an intermittent ring-shaped inlet having six openings 82 and six closing portions 84 provided alternately. Therefore, the mixed gas from the second flow path 47 can be introduced over substantially the entire circumference of the first flow path 45, and the deviation of the introduced mixed gas can be prevented.
[0037]
When such a tip nozzle 74 is used, the taper angle θ between the taper portion 80 and the tip nozzle 74 (FIG. 2), that is, the inclination angle of the taper portion 80 inward in the radial direction is set to 20 to 120 degrees. Is desirable. By setting in this way, the mixed gas introduced through the inlet port is guided by the tapered portion 80 of the tip nozzle 74 and flows inward in the radial direction, and is further uniformly mixed with the mixed gas flowing through the first flow path 45. Will come to be. In this embodiment, the nozzle body 72 and the tip nozzle 74 are closed by the closing portion 84 and fixed by welding. Further, in this embodiment, the tapered portion 80 extends linearly, but does not necessarily need to be linear, and can be formed in a curved shape having a predetermined shape.
[0038]
In such a burner apparatus, as shown in FIG. 3, the second channel 47 is cut in the radial direction in the section taken along the line III-III of FIG. 2 including six openings 82 and six closing portions 84. It is desirable to set the ratio (S2 / S1) between the area S2 and the radial sectional area S1 of the first flow path 45 to 2.0 to 10.0. By setting in this way, the cross-sectional area S2 of the second flow path 47 is more than twice as large as the cross-sectional area S1 of the first flow path 45, and thereby the mixed gas flowing through the first flow path 45 (this The gas concentration of the mixed gas is higher than the gas concentration of the mixed gas flowing through the second flow path 47), and the combustion region corresponding to the central portion of the combustion cylinder 14, in other words, the first flow path 45. The combustion temperature of the combustion gas can be suppressed, and the generation of NOx can be reduced. Further, the cross-sectional area S2 of the second flow path 47 is set to be 10 times or less the cross-sectional area S1 of the first flow path 45, whereby the flow rate of the mixed gas flowing through the first flow path 45 is the second flow path. The gas flowing through the first flow path 45 that does not become excessively small relative to the amount of the mixed gas flowing through the 47 and stably burns helps the combustion of the gas that flows through the more dilute second flow path 47 and is stable as a whole. Combustion can continue.
[0039]
In FIG. 2, the ratio (S2 / S3) of the radial cross-sectional area S2 of the second flow path 47 and the radial cross-sectional area of the inlet (total cross-sectional area of the six openings 82) S3 is 1.0 to It is desirable to set it to 30.0. By setting in this way, the cross-sectional area S2 of the second flow path 47 is larger than the cross-sectional area S3 of the introduction port, whereby the second flow path 47 is introduced into the first flow path 45 through the introduction port. The amount of the mixed gas introduced does not increase excessively, and the gas concentration of the mixed gas flowing through the first flow path 47 can be prevented from becoming thin. Further, the cross-sectional area S2 of the second flow channel 47 does not exceed 30 times the cross-sectional area S3 of the introduction port, whereby the second flow channel 47 is introduced into the first flow channel 45 through the introduction port. The amount of the mixed gas introduced is not excessively small, and the effect of mixing the gas in the second channel 47 with the first channel 45 is not impaired.
[0040]
In this embodiment, the ignition member 58 of the ignition means 56 is located near the other end of the nozzle body 72 of the first nozzle means 10, specifically, upstream of the introduction opening 84 when viewed in the flow direction of the mixed gas. It is arranged. With this configuration, the mixed gas flowing through the first flow path 45, that is, the mixed gas having a gas concentration that stably burns before the mixed gas from the second flow path 47 is introduced, is ignited by the ignition member 58. It is possible to avoid the ignition performance of the ignition means 56 from being lowered.
[0041]
In such a burner device, a part of the mixed gas flowing in the second flow path 47 is fed to the mixed gas flowing in the first flow path 45, whereby the first flow is made downstream of the ignition means 56. The mixed gas in the passage 45 is diluted by the mixed gas from the second flow path 47, the gas concentration of the mixed gas in the first flow path 45 and the second flow path 47 is made substantially uniform, and the combustion temperature of the combustion gas is increased. It can be made substantially uniform over substantially the entire radial cross section of the combustion cylinder 14. When the combustion gas is supplied to the gas turbine 62 by averaging the combustion temperature of the combustion gas in this way, the average value of the combustion temperature can be made closer to the heat resistant temperature of the gas turbine 62, and the gas including the burner device. The efficiency of the turbine system can be improved.
[0042]
[Examples and Comparative Examples]
In order to confirm the effect of the burner device of the present invention, combustion experiments of combustion gas were performed using the burner device of the embodiment shown in FIGS. 1 to 3 as an example. The dimensions and the like of each member in the burner device used were as follows. For the injection nozzle body, eight first ejection holes having a diameter of 1.3 mm are provided at substantially equal intervals in the circumferential direction, and second ejection holes having a diameter of 2.6 mm are provided at substantially equal intervals in the circumferential direction. 8 were provided. The first nozzle means has a nozzle body having an inner diameter of 36 mm and a length of 102 mm, a large diameter portion having an inner diameter of 46 mm and a length of 11 mm, an inner diameter of 36 mm and a small diameter portion having a length of 16 mm, and a length of 5 mm for connecting them. The first cylindrical member is configured by attaching a large diameter portion of the tip nozzle to the nozzle body with eight closed portions using a tip nozzle having a taper portion of 45 degrees and a taper angle of the taper portion of 45 degrees. . For the second nozzle means, a second cylindrical member having an inner diameter of 70 mm and a length of 100 mm was used. By using such first and second cylindrical members, the radial cross-sectional area of the first flow path is set to 1018 mm ² in consideration of the thickness thereof, and the radial cross-sectional area of the second flow path is set to 1018 mm ^2. Was set to 2038 mm ² , and the radial cross-sectional area of the inlet was set to 202 mm ² . Further, a cylindrical member having an inner diameter of 143 mm and a length of 358 mm was used as the combustion cylinder 14. The cylindrical member is provided with eight air holes having a diameter of 6 mm at substantially equal intervals in the circumferential direction in the mouth portion (left end portion in FIGS. 1 and 2), and the peripheral edge is provided on the tip side from the mouth portion. Eight air hole groups having 36 air holes with a diameter of 1.2 mm were provided in the longitudinal direction at substantially equal intervals in the direction.
[0043]
Using such a burner device, in a combustion experiment, air having a temperature of 350 ° C. was supplied through the air flow path at a rate of 700 Nm ³ / H. About 4% of the supplied air flows through the first flow path, about 55% through the second flow path, and about 41% through the outside of the combustion cylinder. The flowing air flowed into the combustion cylinder through the air holes of the combustion cylinder. Using methane as the combustion gas, together with the jetting a first flow path through the first ejection hole of the injection nozzle body at a rate of 1.0 Nm ³ / H, the injection nozzle body at a rate of 24.7Nm ³ / H It ejected to the 2nd flow path through 2 ejection holes. The supplied air and methane were mixed to form a mixed gas, and ignited by an ignition member to burn the mixed gas to generate a combustion gas.
[0044]
And when the temperature of the combustion gas in the front-end | tip of a combustion cylinder was measured by burning a mixed gas in this way, the average combustion temperature was 1037 degreeC and the temperature difference of the combustion temperature at this time was +/- 26 degreeC. The exhausted NOx concentration converted to an oxygen concentration of 0% was 15 ppm. From this result, it was confirmed that the combustion temperature in almost the entire region of the combustion cylinder was substantially uniform. The measurement points of the combustion temperature were measured at the measurement temperature by providing seven temperature sensors at substantially equal intervals in the diameter direction at the tip of the combustion cylinder. The NOx concentration was determined by mixing and collecting combustion exhaust gas from each measurement location with the temperature sensor removed, and analyzing the mixed gas.
[0045]
In this embodiment, further, the amount of combustion gas fed to the second flow path is controlled to reduce the amount of combustion. When the amount of feed is reduced to 10%, the combustion of the burner device is performed. Disappeared, and the turn-down ratio (ratio indicating how far the amount of combustion gas supply can be reduced based on the amount of supply 100%) was 1:10.
[0046]
As a comparative example, a burner apparatus having a cross-sectional view taken along the line III-III in FIG. 2 is configured as shown in FIG. 4, and the air and combustion gas supply conditions are the same as in the embodiment. The temperature was measured as in the example. The shape of the tip nozzle 749 is the same as that of the example, but the large diameter portion of the tip nozzle was welded to the nozzle body 72 with four pins 86. The introduction port 82a was formed in a ring shape, and its cross-sectional area was 405 mm ² . The average combustion temperature at this time was 1040 ° C., the temperature difference between the combustion temperatures was ± 40 ° C., and the NOx concentration converted to an oxygen concentration of 0% was 35 ppm. The turndown ratio measured by the same method as in Example was 1: 4.
[0047]
【The invention's effect】
According to the burner device of the first aspect of the present invention, the air flow flowing through the first flow path of the first nozzle means composed of the first cylindrical member is combusted from the first gas supply means. The working gas is ejected, thereby generating a lean mixed gas that can be stably burned. In addition, the second gas supply means is used for the air flow flowing through the second flow path of the second nozzle means constituted by the second cylindrical member arranged concentrically outside the first cylindrical member. The combustion gas from is ejected, thereby producing a lean mixed gas having a lower gas concentration than the mixed gas of the first nozzle means. Furthermore, since an intermittent ring-shaped mixed gas inlet is provided between the first flow path and the second flow path, a part of the mixed gas generated in the second flow path is The gas is introduced into the first flow path, whereby the gas concentrations of the mixed gas in the first flow path and the mixed gas in the second flow path are made uniform, and the deviation of the combustion state becomes very small. As a result, the combustion temperature of the combustion gas from the first nozzle means becomes substantially equal to the combustion temperature of the combustion gas from the second nozzle means, and when the combustion gas is fed to the gas turbine, the average temperature of the combustion gas is The heat resistance temperature of the gas turbine can be approached, and the efficiency of the system including the burner device can be increased.
[0048]
According to the burner device of the second aspect of the present invention, since the flow velocity of the air flow flowing through the second flow path is faster than the flow velocity of the air flow flowing through the first flow path, A part of the mixed gas is introduced into the first flow path through the mixed gas introducing means, and the concentration of the mixed gas flowing through the first flow path is reduced, thereby reducing the mixed gas that reaches a high temperature.
[0049]
According to the burner device of the third aspect of the present invention, the ratio of the cross-sectional area S2 of the second flow path to the cross-sectional area S1 of the first flow path is 2.0 to 10.0. It is possible to suppress a partial increase in the combustion temperature of the combustion gas in the central portion of the first flow path, and to stably burn the lean mixed gas in the second flow path. Further, since the ratio of the cross-sectional area of the second flow path to the cross-sectional area of the mixed gas introduction port is 1.0 to 30.0, an appropriate amount of the mixed gas of the second flow path is introduced into the first flow path. In addition, the gas concentration of the mixed gas in the first flow path is optimally maintained, and the temperature distribution at the combustor outlet can be made uniform. Further, the mixed gas inlet has 3 to 16 equal-area openings and closed portions, whereby the mixed gas introduced from the second flow path is uniform with the mixed gas in the first flow path. To be mixed.
[0050]
According to the burner device of claim 4 of the present invention, the first nozzle means comprises a nozzle body and a tip nozzle, and a mixed gas introduction opening is defined between the nozzle body and the large diameter portion of the tip nozzle. Therefore, the mixed gas flowing through the second flow path is introduced into the first flow path as required through the mixed gas introduction opening. Further, since the tip nozzle is provided with a taper portion having a taper angle of 20 to 120 degrees, the mixed gas introduced through the mixed gas introduction opening is guided to the taper portion and guided inward in the radial direction, As a result, the mixed gas introduced from the second flow path flows radially inward and is substantially uniformly mixed with the mixed gas flowing through the first flow path.
[0051]
Further, according to the burner device of the fifth aspect of the present invention, since the mixed gas introducing means is disposed downstream of the portion where the ignition means is disposed, the mixed gas flowing through the first flow path to the ignition means. That is, the mixed gas not containing the mixed gas from the second flow path is supplied, and therefore, the mixed gas in the first flow path that can be stably burned by the ignition means can be reliably ignited.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view schematically showing an embodiment of a burner device according to the present invention.
FIG. 2 is an enlarged cross-sectional view schematically showing a main part of the burner device of FIG. 1;
FIG. 3 is a cross-sectional view taken along line III-III in FIG.
4 is a cross-sectional view corresponding to FIG. 3 in the prior art.
[Explanation of symbols]
2 Diffuser section 4 Test case 6 Burner case 8 Air flow path 10 First nozzle means 12 Second nozzle means 14 Combustion cylinder 18 Outer gas supply pipe 20 Injection nozzle body 26 Inner gas supply pipe 32 First cylindrical shape Member 38 second cylindrical member 45 first flow path 46 first ejection hole 47 second flow path 48 second ejection hole 56 ignition means 62 gas turbine 72 nozzle body 74 tip nozzle 76 large diameter portion 84
78 Small diameter portion 80 Taper portion 82 Opening portion 84 Closure portion

Claims

A first nozzle means composed of a first cylindrical member and defining a first flow path;
A second nozzle means comprising a second cylindrical member disposed concentrically outside the first cylindrical member, and defining a second flow path;
First gas supply means for supplying combustion gas to the first flow path;
Second gas supply means for supplying combustion gas to the second flow path;
An air flow path for supplying air to the first and second flow paths,
Combustion gas from the first gas supply means is ejected from the air flow path toward the air flow flowing through the first flow path, and a lean mixed gas that can be stably burned by this is flown in the first flow path. Generated
Combustion gas from the second gas supply means is ejected from the air flow channel toward the air flow flowing through the second flow channel, thereby further gas than the lean mixed gas in the first flow channel. A lean mixed gas having a low concentration is generated in the second flow path,
Between the first flow path and the second flow path, an intermittent ring-like shape for guiding a part of the lean mixed gas of the second flow path to the first flow path is further provided. A burner apparatus characterized in that a mixed gas inlet is provided.

2. The burner device according to claim 1, wherein the flow velocity of the air flow flowing through the second flow path is faster than the flow velocity of the air flow flowing through the first flow path.

The ratio (S2 / S1) between the radial cross-sectional area S2 of the second flow path and the radial cross-sectional area S1 of the first flow path is 2.0 to 10.0, and the mixed gas inlet is It is an intermittent ring shape having 3 to 16 equal-area openings and closed portions, and the radial cross-sectional area S2 of the second flow path and the radial cross-sectional area S3 of the opening of the mixed gas inlet The burner apparatus according to claim 1 or 2, wherein the ratio (S2 / S3) to the range is 1.0 to 30.0.

The first cylindrical member includes a cylindrical nozzle body and a tip nozzle, and the tip nozzle includes a large diameter portion having a large inner diameter, a small diameter portion having an inner diameter smaller than the large diameter portion, and the large nozzle. A tapered portion connecting the diameter portion and the small diameter portion, the large diameter portion of the tip nozzle is attached to the tip portion of the nozzle body, and the opening portion of the mixed gas inlet is the nozzle body And the taper portion of the tip nozzle extends radially inward from the large diameter portion, and the taper portion is tapered with the tip nozzle. The burner apparatus according to claim 3, wherein the angle is set to 20 to 120 degrees.

An ignition means for igniting the lean mixed gas flowing in the first flow path is provided, and the introduction opening of the mixed gas introduction means is provided downstream of the site where the ignition means is provided. The burner device according to claim 3 or 4, characterized by the above.