JP2002089365A - Heat source recycling system - Google Patents
Heat source recycling systemInfo
- Publication number
- JP2002089365A JP2002089365A JP2001203378A JP2001203378A JP2002089365A JP 2002089365 A JP2002089365 A JP 2002089365A JP 2001203378 A JP2001203378 A JP 2001203378A JP 2001203378 A JP2001203378 A JP 2001203378A JP 2002089365 A JP2002089365 A JP 2002089365A
- Authority
- JP
- Japan
- Prior art keywords
- exhaust gas
- combustor
- heat source
- air
- fresh air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
- Air Supply (AREA)
- Combustion Of Fluid Fuel (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、例えば自立分散型
電源設備における発電機の駆動源として用いられている
エンジンやガスタービンなどの熱機関からの排ガスが含
んでいる熱エネルギを再利用するための熱源再利用シス
テムに関し、特に熱機関の内部圧力が低い場合に好適で
ある熱源再利用システムに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for reusing heat energy contained in exhaust gas from a heat engine such as an engine or a gas turbine used as a drive source of a generator in a self-contained distributed power supply system. More particularly, the present invention relates to a heat source recycling system that is suitable when the internal pressure of a heat engine is low.
【０００２】[0002]
【従来の技術】熱機関からの排ガスに含まれる熱エネル
ギを再利用する熱源再利用システムないしコージェネレ
ーションシステムについては、排ガスの熱エネルギを直
接的に利用する方式と間接的に利用する方式がある。後
者の間接利用方式は、排ガスの熱エネルギを燃料燃焼用
空気の昇温に利用する排気再燃式であり、直接利用方式
に比べて再利用の効率を２倍近いものにすることができ
る。このことから最近は排気再燃式が主流になってい
る。2. Description of the Related Art As a heat source recycling system or a cogeneration system for reusing heat energy contained in exhaust gas from a heat engine, there are a system for directly using the heat energy of the exhaust gas and a system for indirectly using the heat energy of the exhaust gas. . The latter indirect use method is an exhaust gas reburning method in which the heat energy of exhaust gas is used to raise the temperature of fuel combustion air, and the efficiency of reuse can be nearly doubled compared to the direct use method. For this reason, the exhaust-gas reburning type has become mainstream recently.
【０００３】排気再燃式については、例えば「大阪ガス
TECHNICAL REPORT 排ガス再燃バーナ」や特開平１０−
１９６９３３号公報あるいは特開平９−２３６２０１号
公報などに開示の例が知られている。また特開平１０−
４７０７８号、特開平９−２８７４１５号、特開２００
０−４５７１０号などの各公報に開示の例も知られてい
る。特に特開平１０−１９６９３３号公報における図２
の例や特開平９−２３６２０１号公報における図２の例
は従来の排気再燃式における一つの典型的な構造であ
る。[0003] Regarding the exhaust gas reburning type, for example, "Osaka Gas
TECHNICAL REPORT Exhaust gas reburning burner ”
Examples disclosed in 196933 and JP-A-9-236201 are known. In addition, Japanese Patent Application Laid-Open
47078, JP-A-9-287415, JP-A-200
Examples disclosed in respective gazettes such as 0-45710 are also known. In particular, FIG. 2 in JP-A-10-196933.
The example shown in FIG. 2 and the example shown in FIG.
【０００４】すなわち従来の排気再燃式熱源再利用シス
テムでは、燃焼器を排ガス利用のために備えており、発
電機などの駆動源として用いられている熱機関からの排
ガスを燃焼器における燃焼用空気の昇温に利用すること
で排ガスに含まれている熱エネルギを再利用できるよう
にしている。このような排ガスの利用形態においては、
排ガスの酸素含有量が例えば１３〜１５％程度と通常の
空気よりも低いことから、排ガスとともに新鮮な空気も
燃焼器に送り込んでやる必要がある。この排ガスと新鮮
空気の混合供給のための従来における一般的な構造は、
特開平１０−１９６９３３号公報や特開平９−２３６２
０１号公報、特願２０００−２０７７５１号公報にも記
載されているように、押込通風機により新鮮空気を昇圧
し、この昇圧された新鮮空気を排ガスと混合させて燃焼
器に送り込むようになっている。That is, in the conventional exhaust gas reburning type heat source recycling system, a combustor is provided for utilizing exhaust gas, and exhaust gas from a heat engine used as a driving source such as a generator is used for combustion air in the combustor. The thermal energy contained in the exhaust gas can be reused by utilizing the temperature of the exhaust gas. In the use form of such exhaust gas,
Since the oxygen content of the exhaust gas is lower than ordinary air, for example, about 13 to 15%, it is necessary to send fresh air to the combustor together with the exhaust gas. The conventional general structure for the mixed supply of the exhaust gas and the fresh air is as follows.
JP-A-10-196933 and JP-A-9-2362
No. 01, Japanese Patent Application No. 2000-207751, as described in Japanese Patent Application No. 2000-207751, pressurized fresh air is pressurized, and the pressurized fresh air is mixed with exhaust gas and sent to a combustor. I have.
【０００５】[0005]
【発明が解決しようとする課題】前記のような従来の排
気再燃式熱源再利用システムにおいては、押込通風機に
よる昇圧で排ガス源である熱機関の背圧が上昇するとい
う問題がある。この押込通風機による背圧の上昇は熱機
関の内部圧力が十分に大きい場合であればそれほど悪影
響をもたらすことがないといえる。しかし比較的小型の
自家用発電設備などにおいて今後ますます多用されると
考えられる、例えば３００ｋｗ以下といった出力レベル
のガスタービンであり、一般的にマイクロガスタービン
と呼ばれる熱機関などの場合には、その内部圧力が通常
の押込通風機の昇圧能に比べて、非常に低い。このため
押込通風機による背圧の上昇によって熱機関はその効率
に大きく悪影響を受けるおそれがある。In the conventional exhaust gas reburning type heat source recycling system as described above, there is a problem that the back pressure of the heat engine, which is the exhaust gas source, increases due to the pressure increase by the forced ventilation. If the internal pressure of the heat engine is sufficiently large, it can be said that the increase in the back pressure caused by the forced draft fan does not cause much adverse effect. However, it is a gas turbine with an output level of, for example, 300 kW or less, which is considered to be used more and more in relatively small private power generation facilities and the like. The pressure is very low compared to the boosting capacity of a normal forced draft fan. For this reason, the efficiency of the heat engine may be greatly adversely affected by the increase of the back pressure by the forced draft fan.
【０００６】前記特開平１０−１９６９３３号公報に
は、熱機関からの排ガスを圧送するファンを設けること
が記載されている。この圧送ファンは、排ガス利用後の
排気のために従来のシステムで設けられていた誘引通風
機を不要とすることを目的としているものであるが、結
果的に熱機関の背圧上昇を防止することにも機能してい
る。しかしこの技術では、排ガスを圧送ファンで圧送し
た後に新鮮空気と混合させる構成としているため、圧送
ファンは熱機関からの排ガスが伴っている数百°Ｃいっ
た非常な高温に直接的に曝されることになる。このこと
は圧送ファンの材質選択や設計などに際して大きな負担
となり、ひいてはシステムの安定作動を損なう原因とな
ったり、またシステムのコストアップにつながることに
もなる。[0006] Japanese Patent Application Laid-Open No. 10-196933 describes that a fan for feeding exhaust gas from a heat engine under pressure is provided. The purpose of this pumping fan is to eliminate the need for an induction ventilator provided in a conventional system for exhausting after exhaust gas is used, but as a result, to prevent a rise in back pressure of the heat engine. It also works. However, in this technology, since the exhaust gas is pumped by a pumping fan and then mixed with fresh air, the pumping fan is directly exposed to an extremely high temperature of several hundred degrees Celsius accompanied by exhaust gas from a heat engine. Will be. This imposes a heavy burden on the selection and design of the material of the pressure-feeding fan, which in turn leads to impairment of the stable operation of the system and increases the cost of the system.
【０００７】また前記特願２０００−２０７７５１号公
報では、熱機関からの排ガスと新鮮空気とを混合させな
がら吸引し、かつ混合した気体を昇圧して燃焼器へ供給
する昇圧手段の設けられた熱源再利用システムが記載さ
れている。しかしこのシステムの場合、排ガス全量に新
鮮空気を加えて吸引昇圧するため、大型の吸気ファンを
必要としてシステムのコストアップにつながると共に、
熱機関からの排ガス量と熱源再利用システムの燃焼器の
容量が固定されてしまうため、コージェネレションシス
テムの熱電比率が固定されてしまうなどの制約がある。[0007] Also, Japanese Patent Application No. 2000-207751 discloses a heat source provided with a pressure increasing means for sucking exhaust gas from a heat engine and fresh air while mixing the gas, and for increasing the pressure of the mixed gas to supply the gas to a combustor. A reuse system is described. However, in the case of this system, fresh air is added to the entire amount of exhaust gas to increase the suction pressure, so a large intake fan is required, leading to an increase in system cost and
Since the amount of exhaust gas from the heat engine and the capacity of the combustor of the heat source reuse system are fixed, there is a limitation that the thermoelectric ratio of the cogeneration system is fixed.
【０００８】本発明は、以上のような従来の事情を背景
になされたものであり、排ガスと新鮮空気との混合供給
を排ガス源である熱機関に対する背圧の上昇を伴うこと
なく行なえ、しかも熱機関からの排ガスにおける高温の
影響を直接的に受けることなくこれを行なえるようにし
た排気再燃式熱源再利用システムの提供を目的としてい
る。The present invention has been made in view of the above-mentioned conventional circumstances, and enables the mixed supply of exhaust gas and fresh air to be performed without increasing the back pressure on the heat engine as the exhaust gas source. It is an object of the present invention to provide an exhaust gas recirculation type heat source recycling system capable of performing this without being directly affected by high temperature in exhaust gas from a heat engine.
【０００９】[0009]
【課題を解決するための手段】前記目的を達成するため
本発明の排気再燃式熱源再利用システムは、熱機関から
の排ガスを燃焼用空気の昇温に利用する燃焼器を備えた
熱源再利用システムにおいて、熱機関からの排ガスを新
鮮空気と混合させながら吸引すると共に、排ガスと前記
新鮮空気との混合気体を昇圧して燃焼器に供給する吸引
昇圧手段が設けられていることを特徴としている。In order to achieve the above object, an exhaust gas reburning type heat source recycling system according to the present invention has a combustor for utilizing exhaust gas from a heat engine to raise the temperature of combustion air. In the system, exhaust gas from the heat engine is sucked while being mixed with fresh air, and suction pressure increasing means for increasing the mixed gas of the exhaust gas and the fresh air and supplying the mixed gas to the combustor is provided. .
【００１０】前記目的を達成するため本発明の排気再燃
式熱源再利用システムは、熱機関からの排ガスを燃焼用
空気の昇温に利用する燃焼器を備えた熱源再利用システ
ムにおいて、前記熱機関からの排ガスの一部を吸引し
て、燃焼用空気の昇温に利用し、残りの排ガスは直接前
記燃焼器の燃焼室で再燃焼させることを特徴としてい
る。In order to achieve the above object, an exhaust gas reburning type heat source recycling system according to the present invention is directed to a heat source recycling system including a combustor for using exhaust gas from a heat engine to raise the temperature of combustion air. A part of the exhaust gas is sucked and used for raising the temperature of combustion air, and the remaining exhaust gas is directly recombusted in the combustion chamber of the combustor.
【００１１】前記目的を達成するため本発明の排気再燃
式熱源再利用システムは、排ガスと新鮮空気との混合割
合を調節するための調節用ダンパーが設けられている。In order to achieve the above object, the exhaust gas reburning type heat source recycling system of the present invention is provided with an adjusting damper for adjusting a mixing ratio of exhaust gas and fresh air.
【００１２】前記目的を達成するため本発明の排気再燃
式熱源再利用システムは、吸引昇圧手段が燃焼器に近接
させて設けられている。[0012] In order to achieve the above object, in the exhaust gas reburning type heat source recycling system of the present invention, the suction pressure increasing means is provided close to the combustor.
【００１３】前記目的を達成するため本発明の排気再燃
式熱源再利用システムは、燃焼器の燃焼用空気として、
熱機関からの排ガスの代わりに新鮮空気を吸引する補助
外気導入口が設けられている。In order to achieve the above object, an exhaust gas reburning type heat source recycling system according to the present invention comprises:
An auxiliary outside air inlet for sucking fresh air instead of exhaust gas from the heat engine is provided.
【００１４】[0014]
【発明の実施の形態】以下、本発明の実施の形態につい
て説明する。図１は第１の実施形態による熱源再利用シ
ステムのフロー図である。本実施形態による熱源再利用
システムは、例えば自家用発電設備などとして用いられ
る自立分散型電源設備からの排ガスを再利用する例であ
る。排ガス源（排熱源）となる発電設備は、図外の発電
機と、これを駆動する熱機関であるガスタービン１とを
備えている。Embodiments of the present invention will be described below. FIG. 1 is a flowchart of the heat source reuse system according to the first embodiment. The heat source reuse system according to the present embodiment is an example of reusing exhaust gas from a self-contained distributed power supply facility used as a private power generation facility, for example. The power generation equipment serving as an exhaust gas source (exhaust heat source) includes a power generator (not shown) and a gas turbine 1 serving as a heat engine for driving the power generator.
【００１５】一方、熱源再利用システムの本体部分は、
ガスタービン１に接続する第１の排気ダクト２、排気ダ
クト２に一端を接続する第１の導気路３、第１の導気路
３の他端に接続する吸引昇圧手段である吸気ファン４、
吸気ファン４に一端を接続する第２の導気路５、第２の
導気路５に接続する燃焼器６、燃焼器６に接続する熱交
換器であるボイラ７、およびボイラ７に接続する第２の
排気ダクト８を備えている。On the other hand, the main part of the heat source recycling system
A first exhaust duct 2 connected to the gas turbine 1, a first air duct 3 having one end connected to the exhaust duct 2, and an intake fan 4 serving as a suction pressure increasing means connected to the other end of the first air duct 3. ,
A second air passage 5 having one end connected to the intake fan 4, a combustor 6 connected to the second air passage 5, a boiler 7 as a heat exchanger connected to the combustor 6, and a connection to the boiler 7 A second exhaust duct 8 is provided.
【００１６】第１の排気ダクト２を介して排出されるガ
スタービン１からの排ガスＧｅは、吸気ファン４の吸引
力により第１の導気路３に導かれる。その際に、第１の
排気ダクト２の大気側への開放端から新鮮空気Ｇｆも吸
引・給気されて排ガスＧｅと混合する。この場合に、ガ
スタービン１が大気圧よりも高い内部圧力を有している
ことから、まず排ガスＧｅが優先的に吸引され、吸気フ
ァン４の吸引量がガスタービン１からの排気量を超えた
範囲について新鮮空気Ｇｆが一定量で吸引される。Exhaust gas Ge from the gas turbine 1 discharged through the first exhaust duct 2 is guided to the first air guide path 3 by the suction force of the intake fan 4. At this time, fresh air Gf is also sucked and supplied from the open end of the first exhaust duct 2 to the atmosphere side, and is mixed with the exhaust gas Ge. In this case, since the gas turbine 1 has an internal pressure higher than the atmospheric pressure, the exhaust gas Ge is first sucked preferentially, and the suction amount of the intake fan 4 exceeds the exhaust amount from the gas turbine 1. Fresh air Gf is sucked in a fixed amount for the range.
【００１７】従って排ガスＧｅと新鮮空気Ｇｆの混合割
合は、吸気ファン４の吸引容量に応じて定まる。吸気フ
ァン４の吸引容量は、吸気ファン４に近接させて第１の
導気路３に設けてある流量制御ダンパー９の開度を変え
ることで調節可能であるし、また吸気ファン４における
羽根車の回転速度を変えることでも調節可能であるが、
通常は流量制御ダンパー９で調節する。ただ吸気ファン
４で実際に必要とする吸引容量は、燃焼器６で必要とす
る空気量により決まるものである。従って通常は燃焼器
６の仕様に応じて要求される空気量（酸素量）を供給で
きるように、吸気ファン４の吸引容量を固定的に設定す
る。このため排ガスＧｅと新鮮空気Ｇｆの混合割合も固
定的なものとなる。Therefore, the mixing ratio of the exhaust gas Ge and the fresh air Gf is determined according to the suction capacity of the intake fan 4. The suction capacity of the intake fan 4 can be adjusted by changing the opening degree of the flow control damper 9 provided in the first air guide passage 3 close to the intake fan 4, and the impeller of the intake fan 4 It can be adjusted by changing the rotation speed of
Usually, it is adjusted by the flow control damper 9. However, the suction capacity actually required by the intake fan 4 is determined by the amount of air required by the combustor 6. Therefore, normally, the suction capacity of the intake fan 4 is fixedly set so that an air amount (oxygen amount) required according to the specifications of the combustor 6 can be supplied. Therefore, the mixing ratio between the exhaust gas Ge and the fresh air Gf is also fixed.
【００１８】排ガスＧｅと新鮮空気Ｇｆの混合気体は、
吸気ファン４により所定の圧力以上に昇圧され、第２の
導気路５を介して燃焼器６に供給される。ここで前記所
定の圧力は燃焼器６の仕様により定まるものである。燃
焼器６には燃料供給管１１を介してガスや油などの燃料
Ｆが供給され、この燃料Ｆが前記のようにして供給され
る混合気体の下で燃焼する。燃焼器６からの排ガスは第
２の排気ダクト８から最終的に大気中に放出される。The mixed gas of the exhaust gas Ge and the fresh air Gf is
The pressure is raised to a predetermined pressure or higher by the intake fan 4 and supplied to the combustor 6 through the second air guide path 5. Here, the predetermined pressure is determined by the specifications of the combustor 6. Fuel F such as gas or oil is supplied to the combustor 6 through a fuel supply pipe 11, and the fuel F burns under the mixed gas supplied as described above. Exhaust gas from the combustor 6 is finally discharged from the second exhaust duct 8 to the atmosphere.
【００１９】この燃焼で発生する熱エネルギはボイラ７
の熱源として利用される。ボイラ７は熱エネルギの利用
目的に応じた形態をとることになる。例えば蒸気や温水
を得るために熱エネルギを利用する場合であれば、蒸気
や温水を発生させるための形態となり、例えば吸収式冷
温水器の冷媒再生用として熱エネルギを利用する場合で
あれば、吸収式冷温水器の高温再生器の形態をとること
になる。The heat energy generated by this combustion is supplied to the boiler 7
Is used as a heat source. The boiler 7 takes a form according to the purpose of utilizing heat energy. For example, if heat energy is used to obtain steam or hot water, a mode for generating steam or hot water is used.For example, if heat energy is used for refrigerant regeneration of an absorption-type water heater / warmer, It will take the form of a high temperature regenerator for an absorption chiller / warmer.
【００２０】本発明による熱源再利用システムは、以上
のように吸気ファン４によりガスタービン１からの排ガ
スを吸引・昇圧して燃焼器６に供給するようにしてい
る。このため燃焼器６に混合気体を昇圧させて供給する
に際してガスタービン１の背圧上昇を招くことがない。
したがってガスタービン１が例えば３００ｋｗ以下とい
った出力レベルのいわゆるマイクロガスタービンであ
り、その内部圧力がきわめて低い場合であっても、ガス
タービン１の効率を低下させることなく排熱利用を図る
ことが可能となる。In the heat source recycling system according to the present invention, the exhaust gas from the gas turbine 1 is sucked and pressurized by the intake fan 4 and supplied to the combustor 6 as described above. Therefore, the back pressure of the gas turbine 1 does not increase when the gas mixture is supplied to the combustor 6 at a high pressure.
Therefore, even when the gas turbine 1 is a so-called micro gas turbine having an output level of, for example, 300 kW or less and the internal pressure is extremely low, it is possible to use the exhaust heat without lowering the efficiency of the gas turbine 1. Become.
【００２１】また本発明では、排ガスを新鮮空気と混合
させた後に吸気ファン４で吸引・昇圧するようにしてい
る。このため吸気ファン４を通過する気体の温度は大気
中から取り込んだ新鮮空気が排ガスに混合させられる比
率に応じて低下していることになる。例えば通常そうで
あるように、新鮮空気の混合比率を５０％以上にする
と、排ガスの温度が例えば３００℃程度であっても、吸
気ファン４を通過する混合気体の温度は１５０℃以下に
することができる。Further, in the present invention, the exhaust gas is mixed with fresh air and then suctioned and pressurized by the intake fan 4. Therefore, the temperature of the gas passing through the intake fan 4 decreases in accordance with the ratio of fresh air taken in from the atmosphere to the exhaust gas. For example, if the mixing ratio of fresh air is 50% or more, as is usually the case, the temperature of the mixed gas passing through the intake fan 4 should be 150 ° C. or less even if the temperature of the exhaust gas is, for example, about 300 ° C. Can be.
【００２２】このことは、前記の特開平１０−１９６９
３３号公報におけるように排ガスだけをファンで吸引
し、そのために３００℃といった非常に高温な気体がそ
のままファンを通過する構成に比べ、実用上できわめて
有意である利点をもたらす。具体的には、吸気ファン４
の各部材を比較的低レベルの耐熱材で構成することが可
能となり、また吸気ファン４の設計に関してもそれほど
高い耐熱設計を要求せずに済ませることができ、したが
って低コスト化を図ることができる。This is because the above-mentioned Japanese Patent Application Laid-Open No. 10-1969
As compared with the configuration in which only exhaust gas is sucked by a fan as in JP-A No. 33, and a very high temperature gas such as 300 ° C. passes through the fan as it is, there is an advantage that is extremely significant in practical use. Specifically, the intake fan 4
Can be made of a relatively low-level heat-resistant material, and the design of the intake fan 4 does not need to require a very high heat-resistant design, so that the cost can be reduced. .
【００２３】図２は第２の実施形態による熱源再利用シ
ステムのフロー図である。本実施形態は、第１の排気ダ
クト２に外気吸入量調整ダンパー２１を設けているこ
と、第１の導気路３に遮断用ダンパー２２を設けている
こと、および第１の導気路３に外気吸入量調整ダンパー
２３付きの補助外気導入口２４を接続してあることを除
いて、基本的には第１の実施形態と同様である。第１の
排気ダクト２に外気吸入量調整ダンパー２１を設けてあ
る本実施形態の場合には、排ガスＧｅと新鮮空気Ｇｆの
混合割合を外気吸入量調整ダンパー２１により調節する
ことが可能である。FIG. 2 is a flow chart of the heat source recycling system according to the second embodiment. In the present embodiment, the first exhaust duct 2 is provided with an outside air intake amount adjusting damper 21, the first air guide path 3 is provided with a blocking damper 22, and the first air guide path 3 Is basically the same as that of the first embodiment except that an auxiliary outside air introduction port 24 with an outside air intake amount adjustment damper 23 is connected to the first embodiment. In the case of the present embodiment in which the first exhaust duct 2 is provided with the outside air intake amount adjustment damper 21, the mixing ratio of the exhaust gas Ge and the fresh air Gf can be adjusted by the outside air intake amount adjustment damper 21.
【００２４】具体的には、外気吸入量調整ダンパー２１
を制御することにより、新鮮空気Ｇｆの吸入抵抗を調節
し、このことで新鮮空気Ｇｆの吸入量を変えることがで
き、これによって排ガスＧｅと新鮮空気Ｇｆの混合割合
を変えることができる。外気吸入量調整ダンパー２１の
制御は、ガスタービン１からの排ガスＧｅの状態に応じ
てなす。More specifically, the outside air intake amount adjustment damper 21
, The suction resistance of the fresh air Gf can be adjusted, whereby the suction amount of the fresh air Gf can be changed, whereby the mixing ratio of the exhaust gas Ge and the fresh air Gf can be changed. The control of the outside air intake amount adjustment damper 21 is performed according to the state of the exhaust gas Ge from the gas turbine 1.
【００２５】排ガスＧｅの状態に関する情報はガスター
ビン１の制御装置から得ることが可能であるし、必要な
らば専用の排ガス監視手段を設けるようにしてもよい。
このような調節機能は、ガスタービン１の運転状態が変
化しても安定的に燃焼器６を稼働させることに役立ち、
またガスタービン１からの排ガスＧｅに含まれる酸素量
に応じて新鮮空気Ｇｆの混合量を必要最小限にすること
で、排ガスの利用効率を高めることなどにも役立つ。Information on the state of the exhaust gas Ge can be obtained from the control device of the gas turbine 1, and if necessary, a dedicated exhaust gas monitoring means may be provided.
Such an adjustment function is useful for stably operating the combustor 6 even when the operation state of the gas turbine 1 changes,
Further, by minimizing the necessary amount of fresh air Gf in accordance with the amount of oxygen contained in the exhaust gas Ge from the gas turbine 1, it is also useful to increase the utilization efficiency of the exhaust gas.
【００２６】遮断用ダンパー２２は、何らかの理由で排
ガスＧｅの吸引を停止する必要のある場合に用いる。そ
して排ガスＧｅの吸引を停止した状態で燃焼器６を稼働
させる場合には、補助外気導入口２４から新鮮空気Ｇｆ
だけを吸引して燃焼器６に供給する。この場合の新鮮空
気Ｇｆの吸入量は燃焼器６での要求に応じて外気吸入量
調整ダンパー２３で調節する。このような機能もガスタ
ービン１の運転状態の変動に対する熱源再利用システム
本体部分の安定性を高めるのに役立つ。The shut-off damper 22 is used when it is necessary to stop exhaust gas Ge suction for some reason. When the combustor 6 is operated in a state in which the suction of the exhaust gas Ge is stopped, the fresh air Gf
Is sucked and supplied to the combustor 6. In this case, the intake amount of the fresh air Gf is adjusted by the outside air intake amount adjustment damper 23 according to a request from the combustor 6. Such a function is also useful for improving the stability of the heat source recycling system main body with respect to fluctuations in the operation state of the gas turbine 1.
【００２７】図３は第３の実施形態による熱源再利用シ
ステムのフロー図である。本実施形態は、吸気ファン４
を燃焼器６に直結している点を除いて第２の実施形態と
同様である。つまり本実施形態では第１の実施形態や第
２の実施形態における第２の導気路５を省略している。
このような構成とすることにより、システム全体の小型
化を図ることができる。FIG. 3 is a flow chart of the heat source recycling system according to the third embodiment. In this embodiment, the intake fan 4
Is similar to that of the second embodiment except that is directly connected to the combustor 6. That is, in the present embodiment, the second air passage 5 in the first embodiment or the second embodiment is omitted.
With such a configuration, the size of the entire system can be reduced.
【００２８】図４は第４の実施形態による熱源再利用シ
ステムのフロー図である。本実施形態は、第２の排気ダ
クト２に外気吸入量調整ダンパー２１を設けているこ
と、第１の導気路３と並列に第２の導気路１５を設けて
いること、第１の導気路３の入口に遮断用ダンパー２２
を設けていること、および第１の導気路３と第２の導気
路１５の分岐点より下流側の第１の導気路３に外気吸入
量調整ダンパー２３付きの補助外気導入口２４を接続し
てあることを除いて、基本的には第３の実施形態と同様
であり、第２の導気路１５の下流側は燃焼器６に直接接
続してある。FIG. 4 is a flowchart of the heat source recycling system according to the fourth embodiment. In the present embodiment, the second exhaust duct 2 is provided with an outside air intake amount adjustment damper 21, the second air guide 15 is provided in parallel with the first air guide 3, Shut-off damper 22 at the entrance of air guide path 3
And an auxiliary outside air inlet 24 with an outside air suction amount adjustment damper 23 in the first air guide path 3 downstream of the branch point of the first air guide path 3 and the second air guide path 15. Is basically the same as that of the third embodiment except that the downstream side of the second air passage 15 is directly connected to the combustor 6.
【００２９】排熱再利用時には、第１の導気路３に設け
た遮断用ダンパー２２が開、第１の導気路３に設けた外
気吸入量調整ダンパー２１が閉となり、第１の排気ダク
ト２を介して排出されるガスタービン１からの排ガスＧ
ｅは、第１の導気路３と第２の導気路１５に分岐され
る。一方燃焼器６には、燃料供給配管１１を介してガス
や油などの燃料Ｆが供給され、この燃料の燃焼に必要と
する空気量が遮断用ダンパー２２で調整されて燃焼器６
に供給される。When the exhaust heat is reused, the shut-off damper 22 provided in the first air passage 3 is opened, the outside air suction amount adjustment damper 21 provided in the first air passage 3 is closed, and the first exhaust gas is exhausted. Exhaust gas G from the gas turbine 1 discharged through the duct 2
e is branched into a first air passage 3 and a second air passage 15. On the other hand, a fuel F such as gas or oil is supplied to the combustor 6 via a fuel supply pipe 11, and the amount of air required for combustion of the fuel is adjusted by a damper 22 for shutting off the combustor 6.
Supplied to
【００３０】従って、第１の導気路３で吸引される排ガ
ス量は、燃焼器６で必要とする空気量により決定し、残
りの排ガスは第２の導気路１５から燃焼器６の燃焼室に
導かれて燃焼され、燃焼火炎により加熱・再燃焼され
る。そして燃焼器６からの排ガスは、第２の排気ダクト
８から最終的に大気中に放出されるが、この燃焼で発生
する熱エネルギはボイラ７の熱源に利用される。ボイラ
７は熱エネルギの利用目的に応じた形態をとることにな
る。例えば蒸気や温水を得るために熱エネルギを利用す
る場合であれば、蒸気や温水を発生させるための形態と
なり、例えば吸収式冷温水機の冷媒再生用として熱エネ
ルギを利用する場合であれば、吸収式冷温水機の高温再
生器の形態をとることとなる。Therefore, the amount of exhaust gas sucked in the first air guide path 3 is determined by the amount of air required in the combustor 6, and the remaining exhaust gas flows from the second air guide path 15 into the combustion chamber 6. It is guided into the chamber and burned, and is heated and reburned by the combustion flame. Then, the exhaust gas from the combustor 6 is finally released into the atmosphere from the second exhaust duct 8, and the heat energy generated by this combustion is used as a heat source of the boiler 7. The boiler 7 takes a form according to the purpose of utilizing heat energy. For example, if heat energy is used to obtain steam or hot water, a form for generating steam or hot water is used.For example, if heat energy is used for refrigerant regeneration of an absorption type chiller / heater, It will take the form of a high temperature regenerator for an absorption chiller / heater.
【００３１】第１の導気路３には外気吸込量調整ダンパ
ー２３付きの補助外気導入口２４が設けてあり、ガスタ
ービン１からの排ガスの酸素含有量や吸気ファン４の耐
熱仕様に応じて、吸気ファン４に吸引される排ガスと新
鮮空気の混合割合を外気吸込量調整ダンパー２３を制御
することにより調節可能である。The first air guide path 3 is provided with an auxiliary outside air inlet 24 provided with an outside air suction amount adjusting damper 23, depending on the oxygen content of the exhaust gas from the gas turbine 1 and the heat resistance of the intake fan 4. The mixing ratio of the exhaust gas and the fresh air sucked by the intake fan 4 can be adjusted by controlling the outside air suction amount adjustment damper 23.
【００３２】一方何らかの理由で、ガスタービン１から
排出される排ガスの排熱を利用せずに熱源再利用システ
ムの単独運転を行う場合には、第１の導気路３の入口に
設けてある遮断用ダンパー２２が閉、外気吸入量調整ダ
ンパー２１が開となり、第１の導気路３および第２の導
気路１５への排ガスＧｅ流入が遮断される。ガスタービ
ン１からの排ガスの吸引を遮断した状態で燃焼器６を稼
動させると、吸気ファン４は補助外気導入口２４から新
鮮空気Ｇｆを吸引して燃焼器６に供給するが、このとき
の新鮮空気Ｇｆの吸込量は、燃焼器６での要求に応じて
外気吸入量調整ダンパー２３で調整された新鮮空気Ｇｆ
が燃焼器６に供給される。このような単独運転機能もガ
スタービン１の運転状態の変動に対する熱源再利用シス
テムやコージェネレーションシステム全体の安定性を高
めるのに役立つ。On the other hand, when the heat source recycling system is operated independently without using the exhaust heat of the exhaust gas discharged from the gas turbine 1 for some reason, the heat source recycling system is provided at the inlet of the first air guide path 3. The shutoff damper 22 is closed and the outside air suction amount adjustment damper 21 is opened, and the flow of exhaust gas Ge into the first air guide path 3 and the second air guide path 15 is shut off. When the combustor 6 is operated in a state where the exhaust gas from the gas turbine 1 is not sucked, the intake fan 4 sucks fresh air Gf from the auxiliary outside air inlet 24 and supplies the fresh air Gf to the combustor 6. The intake amount of the air Gf is adjusted according to the demand of the combustor 6 by the fresh air Gf adjusted by the outside air intake amount adjustment damper 23.
Is supplied to the combustor 6. Such an independent operation function is also useful for improving the stability of the heat source reuse system and the cogeneration system as a whole against fluctuations in the operation state of the gas turbine 1.
【００３３】ガスタービン１で発電のみを行い、排ガス
排熱の再利用を行わない場合には、第１の導気路３の入
口に設けてある遮断用ダンパー２２が閉、外気吸入量調
整ダンパー２１が開となり、ガスタービン１からの排ガ
スＧｅは第１の排気ダクト２から外気吸入量調整ダンパ
ー２１を介して大気に放出される。このとき遮断用ダン
パー２２が全閉位置にあっても、隙間からの排ガスが少
量リークしてボイラ７の異常加熱や、伝熱面への結露に
よる腐食の原因となるのを防止するため、ガスタービン
１の運転中は吸気ファン４は常時運転され、補助外気導
入口２４から新鮮空気Ｇｆを吸引してボイラ７内に供給
することで、内部の空気を常に外気で置換し温度上昇と
結露を防止する。When only the power generation is performed by the gas turbine 1 and the exhaust heat is not reused, the shut-off damper 22 provided at the inlet of the first air guide path 3 is closed, and the outside air intake amount adjusting damper is closed. 21 is opened, and the exhaust gas Ge from the gas turbine 1 is discharged from the first exhaust duct 2 to the atmosphere via the outside air intake amount adjusting damper 21. At this time, even if the shut-off damper 22 is in the fully closed position, the gas is prevented in order to prevent a small amount of exhaust gas leaking from the gap to cause abnormal heating of the boiler 7 and cause corrosion due to dew condensation on the heat transfer surface. During the operation of the turbine 1, the intake fan 4 is always operated, and the fresh air Gf is sucked from the auxiliary outside air inlet 24 and supplied to the boiler 7, so that the inside air is always replaced with outside air to increase the temperature and dew condensation. To prevent.
【００３４】[0034]
【発明の効果】以上説明しように本発明によれば、熱機
関からの排ガスを新鮮空気と混合させながら吸引して昇
圧する吸引昇圧手段を設けるようにしているので、排ガ
スと新鮮空気との混合供給を、排ガス源である熱機関に
対する背圧の上昇を伴うことなく、しかも熱機関からの
高温な排ガスの影響を吸引昇圧手段に直接的に与えるこ
となく行なうことができる。このため内部圧力の低い熱
機関、例えばいわゆるマイクロガスタービンと呼ばれる
熱機関についてもその効率を低下させることなく排ガス
を高い効率で再利用することが可能となる。As described above, according to the present invention, the suction / pressurizing means for sucking and increasing the pressure of the exhaust gas from the heat engine while mixing it with the fresh air is provided. The supply can be performed without increasing the back pressure on the heat engine which is the exhaust gas source, and without directly applying the influence of the high-temperature exhaust gas from the heat engine to the suction pressure increasing means. For this reason, it is possible to reuse the exhaust gas with high efficiency without lowering the efficiency of a heat engine having a low internal pressure, for example, a heat engine called a so-called micro gas turbine.
【００３５】また熱機関からの排ガスの一部を吸引し
て、燃焼用空気の昇温に利用し、残りの排ガスは直接前
記燃焼器の燃焼室で再燃焼させるようにしたことから、
排ガスの全量を吸引するものに比べて小型の吸気ファン
が使用できる上、排熱を利用するボイラなどの必要容量
に応じて燃焼器の容量が自由に選定できるため、システ
ム全体のコストダウンが図れる。Further, a part of the exhaust gas from the heat engine is sucked and used for raising the temperature of the combustion air, and the remaining exhaust gas is directly re-burned in the combustion chamber of the combustor.
Smaller intake fans can be used than those that suck in the entire amount of exhaust gas, and the capacity of the combustor can be freely selected according to the required capacity of a boiler or the like that uses exhaust heat, thereby reducing the cost of the entire system. .
【００３６】しかも燃焼器の燃焼用空気として、熱機関
からの排ガスの代わりに新鮮空気を吸引する補助外気導
入口を設けたことから、熱機関の運転中は吸気ファンに
より排ガスを吸引することにより、排気圧力損失の削減
が図れると共に、何等かの理由で熱機関が停止した場合
でも、吸気ファンにより外気を燃焼器へ供給することに
より、熱源再利用システムの単独運転が可能となる。In addition, since the auxiliary outside air inlet for sucking fresh air instead of exhaust gas from the heat engine is provided as combustion air for the combustor, exhaust gas is sucked by the intake fan during operation of the heat engine. In addition, the exhaust pressure loss can be reduced, and even when the heat engine is stopped for any reason, the independent operation of the heat source recycling system becomes possible by supplying outside air to the combustor by the intake fan.
【図１】本発明の第１の実施形態による熱源再利用シス
テムのフロー図である。FIG. 1 is a flowchart of a heat source reuse system according to a first embodiment of the present invention.
【図２】本発明の第２の実施形態による熱源再利用シス
テムのフロー図である。FIG. 2 is a flowchart of a heat source reuse system according to a second embodiment of the present invention.
【図３】本発明の第３の実施形態による熱源再利用シス
テムのフロー図である。FIG. 3 is a flowchart of a heat source reuse system according to a third embodiment of the present invention.
【図４】本発明の第４の実施形態による熱源再利用シス
テムのフロー図である。FIG. 4 is a flowchart of a heat source reuse system according to a fourth embodiment of the present invention.
１ ガスタービン（熱機関） ４ 吸気ファン（吸引昇圧手段） ６ 燃焼器 ２１ 外気吸入量調整ダンパー（調節用ダンパー） ２４ 補助外気導入口 Ｇｅ 排ガス Ｇｆ 新鮮空気 DESCRIPTION OF SYMBOLS 1 Gas turbine (heat engine) 4 Intake fan (suction boosting means) 6 Combustor 21 Outside air intake amount adjustment damper (adjustment damper) 24 Auxiliary outside air inlet Ge Exhaust gas Gf Fresh air
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ０２Ｃ 6/18 Ｆ０２Ｃ 6/18 Ａ Ｚ Ｆ２３Ｌ 15/00 Ｆ２３Ｌ 15/00 Ａ 17/00 ６０１ 17/00 ６０１Ｎ // Ｆ２３Ｃ 6/04 ３０３ Ｆ２３Ｃ 6/04 ３０３ (72)発明者 浅沼 俊浩 茨城県土浦市神立町603番地 株式会社日 立製作所産業機械システム事業部内 (72)発明者 藤田 陽一 茨城県土浦市神立町603番地 株式会社日 立製作所産業機械システム事業部内 (72)発明者 用松 康秀 東京都千代田区神田錦町一丁目６番地 株 式会社日立ビルシステム内 Ｆターム(参考） 3G081 BA02 BA11 BC07 BD00 DA03 DA14 3K023 QB09 QB18 QB20 QC08 3K091 DD02 FB35 FB68 ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 7 Identification symbol FI Theme coat ゛ (Reference) F02C 6/18 F02C 6/18 AZ F23L 15/00 F23L 15/00 A 17/00 601 17/00 601N // F23C 6/04 303 F23C 6/04 303 (72) Inventor Toshihiro Asanuma 603, Katemachi, Tsuchiura-shi, Ibaraki Pref. Industrial Machinery Systems Division, Hitachi Engineering Co., Ltd. 603 Industrial Machinery Systems Division, Hitachi, Ltd. (72) Inventor Yasuhide Yonematsu 1-6-6 Kanda Nishikicho, Chiyoda-ku, Tokyo F-term in Hitachi Building Systems Co., Ltd. 3G081 BA02 BA11 BC07 BD00 DA03 DA14 3K023 QB09 QB18 QB20 QC08 3K091 DD02 FB35 FB68
Claims (5)
に利用する燃焼器を備えた熱源再利用システムにおい
て、前記熱機関からの前記排ガスを新鮮空気と混合させ
ながら吸引すると共に、前記排ガスと前記新鮮空気との
混合気体を昇圧して前記燃焼器に供給する吸引昇圧手段
が設けられていることを特徴とする熱源再利用システ
ム。1. A heat source recycling system comprising a combustor for utilizing exhaust gas from a heat engine to raise the temperature of combustion air, wherein the exhaust gas from the heat engine is sucked while being mixed with fresh air, and A heat source reusing system, comprising: a suction pressure increasing means for increasing the pressure of a mixed gas of exhaust gas and the fresh air and supplying the gas to the combustor.
に利用する燃焼器を備えた熱源再利用システムにおい
て、前記熱機関からの排ガスの一部を吸引して、燃焼用
空気の昇温に利用し、残りの排ガスは直接前記燃焼器の
燃焼室で再燃焼させることを特徴とする熱源再利用シス
テム。2. A heat source recycling system comprising a combustor for utilizing exhaust gas from a heat engine to raise the temperature of combustion air, wherein a part of the exhaust gas from the heat engine is sucked to raise the combustion air. A heat source recycling system, wherein the system is used for temperature and the remaining exhaust gas is directly reburned in a combustion chamber of the combustor.
を調節するための調節用ダンパーが設けられている請求
項１または２に記載の熱源再利用システム。3. The heat source recycling system according to claim 1, further comprising an adjusting damper for adjusting a mixing ratio of the exhaust gas and the fresh air.
せて設けられている請求項１ないし３のいずれか１項に
記載の熱源再利用システム。4. The heat source recycling system according to claim 1, wherein said suction pressure increasing means is provided close to said combustor.
機関からの排ガスの代わりに新鮮空気を吸引する補助外
気導入口が設けられている請求項２に記載の熱源再利用
システム。5. The heat source recycling system according to claim 2, wherein an auxiliary outside air inlet for sucking fresh air instead of exhaust gas from the heat engine is provided as combustion air for the combustor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001203378A JP3713221B2 (en) | 2000-07-10 | 2001-07-04 | Heat source reuse system |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000207751 | 2000-07-10 | ||
| JP2000-207751 | 2000-07-10 | ||
| JP2001203378A JP3713221B2 (en) | 2000-07-10 | 2001-07-04 | Heat source reuse system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002089365A true JP2002089365A (en) | 2002-03-27 |
| JP3713221B2 JP3713221B2 (en) | 2005-11-09 |
Family
ID=26595660
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001203378A Expired - Lifetime JP3713221B2 (en) | 2000-07-10 | 2001-07-04 | Heat source reuse system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3713221B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010065695A (en) * | 2008-09-11 | 2010-03-25 | General Electric Co <Ge> | Low btu fuel flow rate ratio duct burner for heating and heat recovery system |
| CN105649693A (en) * | 2016-01-19 | 2016-06-08 | 上海汉钟精机股份有限公司 | Gas-steam organic three-level cycle power generation heating and refrigerating cogeneration system |
-
2001
- 2001-07-04 JP JP2001203378A patent/JP3713221B2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010065695A (en) * | 2008-09-11 | 2010-03-25 | General Electric Co <Ge> | Low btu fuel flow rate ratio duct burner for heating and heat recovery system |
| DE102009043864B4 (en) | 2008-09-11 | 2024-01-04 | General Electric Co. | Duct burner for low calorific value fuel for heating systems and heat recovery systems |
| CN105649693A (en) * | 2016-01-19 | 2016-06-08 | 上海汉钟精机股份有限公司 | Gas-steam organic three-level cycle power generation heating and refrigerating cogeneration system |
| CN105649693B (en) * | 2016-01-19 | 2024-04-19 | 上海汉钟精机股份有限公司 | Gas-steam organic three-stage circulation power generation heating and refrigeration co-production system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3713221B2 (en) | 2005-11-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR102319093B1 (en) | Pressurized air supply system, fuel cell system comprising the pressurized air supply system, and starting method of the pressurized air supply system | |
| JP4538077B2 (en) | Lean fuel intake gas turbine | |
| JP3795951B2 (en) | Low NOx burner and exhaust gas recirculation control method | |
| US20040148942A1 (en) | Method for catalytic combustion in a gas- turbine engine, and applications thereof | |
| US20110239650A1 (en) | Power plant comprising a turbine unit and a generator | |
| US20060272334A1 (en) | Practical method for improving the efficiency of cogeneration system | |
| CN104675521A (en) | Novel gas-steam combined cycle cooling, heating and power generation system | |
| KR20020005972A (en) | System for recycling waste heat | |
| JP2000130108A (en) | Starting method for combined cycle power plant | |
| JP2899247B2 (en) | Gas turbine inlet heating and cooling system | |
| JP2002089365A (en) | Heat source recycling system | |
| JP4859512B2 (en) | Combustion boiler control method | |
| JP2001020755A (en) | Exhaust re-circulation type gas turbine system and combined cycle generator facility with the gas turbine system | |
| KR20020027055A (en) | Combusion air supplying method of Turbo-burner used high efficiency and low NOx boiler, Turbo-burner used high efficiency and low NOx boiler | |
| CN105423289A (en) | Condensation-resistant system and method of flue gas outer circulation combustion equipment | |
| JP2002005412A (en) | Waste gas re-combustion type combustion device | |
| CN218912983U (en) | Combined cycle system | |
| KR102258738B1 (en) | Combustion System Combined with Pressurized Oxygen Combustion and Pulverized Coal Fuel Combustion | |
| JP4550677B2 (en) | High humidity gas turbine equipment and operation method thereof | |
| JP2566129Y2 (en) | Mill fire prevention equipment | |
| JPH0547921Y2 (en) | ||
| JPS58145808A (en) | Method for lowering nox at time when boiler is started | |
| JP2024044230A (en) | Combustion device and method for operating the combustion device | |
| KR100725340B1 (en) | Cogenaration system for furnace | |
| JP2002339803A (en) | Internal combustion engine cogeneration system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20050729 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20050816 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20050819 |
|
| R150 | Certificate of patent or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 Ref document number: 3713221 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080826 Year of fee payment: 3 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080826 Year of fee payment: 3 |
|
| R371 | Transfer withdrawn |
Free format text: JAPANESE INTERMEDIATE CODE: R371 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080826 Year of fee payment: 3 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080826 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090826 Year of fee payment: 4 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100826 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100826 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110826 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120826 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130826 Year of fee payment: 8 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
| R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
| R371 | Transfer withdrawn |
Free format text: JAPANESE INTERMEDIATE CODE: R371 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| EXPY | Cancellation because of completion of term |