JPH0763303A - System for utilizing combustion exhaust gas of boiler - Google Patents
System for utilizing combustion exhaust gas of boilerInfo
- Publication number
- JPH0763303A JPH0763303A JP21315993A JP21315993A JPH0763303A JP H0763303 A JPH0763303 A JP H0763303A JP 21315993 A JP21315993 A JP 21315993A JP 21315993 A JP21315993 A JP 21315993A JP H0763303 A JPH0763303 A JP H0763303A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- pressure boiler
- boiler
- exhaust gas
- water
- 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.)
- Pending
Links
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は例えば原油、重油、石炭
などを燃料とする大型の高圧ボイラーにおいて、高温の
燃焼排気ガスから熱エネルギーを回収し、この熱エネル
ギーを前記高圧ボイラーにおける給水予熱などの熱源に
利用するボイラーの燃焼排気ガス利用システムに関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention collects thermal energy from high-temperature combustion exhaust gas in a large-sized high-pressure boiler that uses crude oil, heavy oil, coal, etc. as a fuel, and supplies this thermal energy to water supply preheating in the high-pressure boiler. The present invention relates to a combustion exhaust gas utilization system of a boiler used as a heat source of a vehicle.
【０００２】[0002]
【従来の技術】従来、原油・重油又は石炭を燃料とする
大型の高圧ボイラーは、例えば発電所の蒸気原動機に用
いられているが、この高圧ボイラーは、そのボイラー自
体及びその関連機器の硫酸腐食を回避するための工夫が
なされている。2. Description of the Related Art Conventionally, large-sized high-pressure boilers that use crude oil, heavy oil, or coal as fuel have been used, for example, in steam power plants of power plants, but this high-pressure boiler is subject to sulfuric acid corrosion of the boiler itself and its related equipment. The device is made to avoid.
【０００３】図２は、前記高圧ボイラーを用いた蒸気原
動機のシステム図であって、大型の高圧ボイラー１０１
と蒸気原動機１０２とを高圧蒸気管１０３と低圧蒸気管
１０４及び給水管１０５とにより結んでおり、前記ボイ
ラー１０１の燃料供給管１０６には燃料加熱器１０７が
介装され、また、燃焼空気を供給する空気管１０８には
空気予熱器１０９を介装している。FIG. 2 is a system diagram of a steam engine using the high-pressure boiler, which is a large-sized high-pressure boiler 101.
The high-pressure steam pipe 103, the low-pressure steam pipe 104, and the water supply pipe 105 are connected to the steam engine 102, and a fuel heater 107 is installed in the fuel supply pipe 106 of the boiler 101, and combustion air is supplied. An air preheater 109 is interposed in the air pipe 108 to operate.
【０００４】また、前記ボイラー１０１の燃焼室周りに
は蒸発管１１０が配設される共に、この蒸発管１１０と
接続するボイラードラム１１１を設け、このドラム１１
１の蒸気域には、前記燃焼室に内装する過熱器１１２が
接続され、この過熱器１１２に前記高圧蒸気管１０３が
接続されている。An evaporation pipe 110 is arranged around the combustion chamber of the boiler 101, and a boiler drum 111 connected to the evaporation pipe 110 is provided.
A superheater 112 installed inside the combustion chamber is connected to the steam region 1 and the high-pressure steam pipe 103 is connected to the superheater 112.
【０００５】そして、前記ドラム１１１の液域には、前
記燃焼室に内装する給水加熱器１１３が接続され、この
給水加熱器１１３に前記給水管１０５が接続されてい
る。尚、図２において１１４は前記給水管１０５の蒸気
原動機１０２側に介装する復水器、１１５は復水ポンプ
であり、１１６，１１７は前記給水管１０５に設ける給
水予熱器であり、１１８は給水ポンプである。The feed water heater 113 installed in the combustion chamber is connected to the liquid region of the drum 111, and the feed water pipe 105 is connected to the feed water heater 113. In FIG. 2, 114 is a condenser installed on the steam engine 102 side of the water supply pipe 105, 115 is a condensate pump, 116 and 117 are water supply preheaters provided in the water supply pipe 105, and 118 is a water supply preheater. It is a water supply pump.
【０００６】しかして、以上の構成において、燃料は燃
料加熱器１０７で加熱され、燃料空気は空気予熱器１０
９で予熱されて混合され、前記ボイラー１０１の燃焼室
内で燃焼して燃焼ガスとなる。In the above structure, the fuel is heated by the fuel heater 107, and the fuel air is heated by the air preheater 10.
9 is preheated and mixed, and burned in the combustion chamber of the boiler 101 to form combustion gas.
【０００７】この燃焼ガスは、蒸発管１１０を加熱する
と共に過熱器１１２及び給水加熱器１１３を加熱し、６
００℃前後の排気ガスとして煙道１１９から大気に排出
される。The combustion gas heats the evaporation pipe 110 and heats the superheater 112 and the feed water heater 113,
Exhaust gas around 00 ° C. is exhausted from the flue 119 to the atmosphere.
【０００８】そして、前記蒸気原動機１０２の作動流体
となる蒸気は、復水器１１４で復水し、復水ポンプ１１
５で予圧されると共に、給水予熱器１１６，１１７で予
熱され、給水ポンプ１１８でボイラー圧力まで昇圧さ
れ、また、給水加熱器１１３で加熱され前記ボイラー１
０１のボイラードラム１１１に給水されるのであり、前
記蒸発管１１０で発生した高圧蒸気は、前記ボイラード
ラム１１１から過熱器１１２に至り、この過熱器１１２
で加熱されて過熱蒸気となり、前記蒸気原動機１０２に
入り、この蒸気原動機１０２を駆動する。The steam, which is the working fluid of the steam engine 102, is condensed in the condenser 114, and the condensate pump 11
5 is pre-pressurized, and is pre-heated by the feed water pre-heaters 116 and 117, boosted to the boiler pressure by the feed water pump 118, and heated by the feed water heater 113.
No. 01 boiler drum 111 is supplied with water, and the high-pressure steam generated in the evaporation pipe 110 reaches the superheater 112 from the boiler drum 111, and the superheater 112 is heated.
Is heated to become superheated steam, enters the steam engine 102, and drives the steam engine 102.
【０００９】また、前記蒸気原動機１０２から部分膨
張、減圧した蒸気を一部抽出して、この減圧蒸気を前記
燃料加熱器１０７、空気予熱器１０９及び給水予熱器１
１６，１１７に供給して、燃料加熱、空気加熱及び給水
予熱を行っている。また、大部分の高圧蒸気は前記蒸気
原動機１０２を駆動し、完全膨張して復水器１１４に戻
るサイクルを繰り返すのである。Further, a part of the steam that has been partially expanded and depressurized is extracted from the steam engine 102, and this depressurized steam is used for the fuel heater 107, the air preheater 109 and the feed water preheater 1.
16 and 117 to perform fuel heating, air heating, and feed water preheating. Further, most of the high-pressure steam drives the steam engine 102, completes expansion, and returns to the condenser 114 to repeat the cycle.
【００１０】[0010]
【発明が解決しようとする課題】図２に示した蒸気原動
機システムにおいて、前記燃焼室で燃焼ガスと熱交換す
る過熱器１１２及び給水加熱器１１３の熱交換面の温度
は亜硫酸ガスの露点温度（１６０℃）より高くなり硫酸
腐食を回避できるのであるが、排気ガス煙道１１９から
大気に排出される排気ガスは６００℃前後の高温であっ
て、高温のまゝ大気に排出されているから燃料消費量が
多くなり、また、前記した燃料加熱、空気予熱及び給水
予熱は、蒸気原動機１０２を駆動する蒸気の一部を、そ
の途中から抽出して行っているため、蒸気原動機１０２
の効力を減少させることになっている。In the steam engine system shown in FIG. 2, the temperature of the heat exchange surfaces of the superheater 112 and the feed water heater 113 for exchanging heat with the combustion gas in the combustion chamber is the dew point temperature of sulfurous acid gas ( 160 ° C), sulfuric acid corrosion can be avoided, but the exhaust gas discharged from the exhaust gas flue 119 to the atmosphere has a high temperature of around 600 ° C and is discharged to the atmosphere at a high temperature. Since the consumption amount becomes large, and the fuel heating, the air preheating, and the feed water preheating are performed by extracting a part of the steam that drives the steam engine 102 from the middle thereof, the steam engine 102 is used.
Is to reduce the potency of.
【００１１】本発明の目的は、燃焼排気ガスの熱回収を
硫酸腐食なく、かつ十分行え、燃料消費量を少なくして
省エネルギが可能で、しかも蒸気原動力の動力を減少さ
せることのないボイラーの燃焼排気ガス利用システムを
提供することにある。An object of the present invention is to provide a boiler that can sufficiently recover the heat of combustion exhaust gas without sulfuric acid corrosion, can reduce energy consumption by reducing fuel consumption, and does not reduce steam motive power. It is to provide a combustion exhaust gas utilization system.
【００１２】[0012]
【課題を解決するための手段】本発明は以上の目的を達
成するため燃焼室２と燃焼排気ガス煙道３とをもつ高圧
ボイラー１において、前記煙道３に設けられ、燃焼排気
ガスと熱交換する蒸気発生器４と、前記高圧ボイラー１
とは別に設ける低圧ボイラー５と、この低圧ボイラー５
と前記蒸気発生器４との間に設けられ、前記低圧ボイラ
ー５から缶水を、前記蒸気発生器４に循環させて蒸気を
発生させ、前記低圧ボイラー５に戻す循環ポンプ６をも
った缶水循環路７とを備え、前記低圧ボイラー５の蒸気
域に、前記蒸気発生器４で発生した蒸気を取出し、前記
高圧ボイラー１における給水予熱などの熱源に利用する
熱回収蒸気管１２を接続したのである。In order to achieve the above object, the present invention provides a high-pressure boiler 1 having a combustion chamber 2 and a combustion exhaust gas flue 3, which is provided in the flue 3 and is provided with combustion exhaust gas and heat. The steam generator 4 to be replaced and the high pressure boiler 1
And a low-pressure boiler 5 provided separately from the low-pressure boiler 5
Water circulation with a circulation pump 6 provided between the low pressure boiler 5 and the steam generator 4 to circulate can water from the low pressure boiler 5 to the steam generator 4 to generate steam and return it to the low pressure boiler 5. The heat recovery steam pipe 12 is provided in the steam region of the low-pressure boiler 5 for taking out the steam generated by the steam generator 4 and using it as a heat source for preheating the feed water in the high-pressure boiler 1. .
【００１３】[0013]
【作用】循環ポンプ６の駆動で低圧ボイラー５の缶水部
から缶水が取出され、高圧ボイラー１の排気ガス煙道３
に設置した蒸気発生器４に送入され、送入された缶水が
排気ガス煙道３から大気に排気される高温（６００℃前
後）の燃焼排気ガスと熱交換され、蒸気として低圧ボイ
ラー５に戻され、この低圧ボイラー５の熱回収蒸気管１
２から燃料加熱器、空気予熱器、給水予熱器、燃料タン
ク等の蒸気系統に送られ、これら燃料加熱、空気予熱や
給水予熱の熱源に利用できるのである。Operation: The circulating pump 6 drives the canned water from the canned water portion of the low-pressure boiler 5, and the exhaust gas flue 3 of the high-pressure boiler 1
Is sent to the steam generator 4 installed in the steam generator 4, and the sent can water is heat-exchanged with the high-temperature (about 600 ° C.) combustion exhaust gas exhausted from the exhaust gas flue 3 to the atmosphere, and the low-pressure boiler 5 is used as steam. Returned to the heat recovery steam pipe 1 of this low-pressure boiler 5
It is sent from 2 to a steam system such as a fuel heater, an air preheater, a feed water preheater, and a fuel tank, and can be used as a heat source for fuel heating, air preheating, and feed water preheating.
【００１４】また、蒸気発生器４には低圧ボイラー５の
缶水を送りこの缶水を高圧ボイラー１の排気ガスと熱交
換して熱回収するのであるから、単位面積当たりの熱貫
流率は、伝熱管を通しての蒸気と排気ガス又は空気と排
気ガスとの熱交換に比較して約２倍になり、同一伝熱面
積で同一温度差では熱回収が大きくなる。Further, since the canned water of the low-pressure boiler 5 is sent to the steam generator 4 and the canned water is heat-exchanged with the exhaust gas of the high-pressure boiler 1 to recover heat, the heat transmission coefficient per unit area is The heat exchange between the steam and the exhaust gas or the air and the exhaust gas through the heat transfer tube is approximately doubled, and the heat recovery becomes large with the same heat transfer area and the same temperature difference.
【００１５】また、蒸気発生器４に送られる缶水は、低
圧ボイラー５の缶水部から取出すのであって、起動時に
は、低圧ボイラー５の燃焼により加熱され、また、運転
中は低圧ボイラー５の燃焼がなくとも、前記循環ポンプ
６で缶水部から取出される缶水は、使用圧力の飽和水温
度、即ち使用圧力５Kg/cm 2Gでは１５８℃、１０Kg/cm
2 G では１８３℃の飽和水温度を保有している。Further, the canned water sent to the steam generator 4 is taken out from the canned water portion of the low-pressure boiler 5, and is heated by the combustion of the low-pressure boiler 5 at the time of start-up, and the low-pressure boiler 5 is operated during operation. Even if there is no combustion, the canned water taken out of the canned water portion by the circulation pump 6 has a saturated water temperature of the working pressure, that is, at a working pressure of 5 Kg / cm 2 G, it is 158 ° C.
In 2 G owns saturated water temperature of 183 ° C..
【００１６】従って、蒸気発生器４において排気ガスと
熱交換する熱交換面の温度は、亜硫酸ガスの露点温度
（１６０℃）以上となり、硫酸腐食を回避できるのであ
る。Therefore, the temperature of the heat exchange surface for exchanging heat with the exhaust gas in the steam generator 4 becomes equal to or higher than the dew point temperature (160 ° C.) of the sulfurous acid gas, and sulfuric acid corrosion can be avoided.
【００１７】また、硫酸腐食を回避するために図２に示
した従来例のように蒸気原動機の中圧段、低圧段より部
分膨張、減圧した蒸気を一部抽気し、燃料加熱器、空気
予熱器、給水予熱器に加熱蒸気を送気するために、蒸気
原動機の出力が減少する不具合もなくなる。Further, in order to avoid sulfuric acid corrosion, as in the prior art example shown in FIG. 2, the steam partially expanded and decompressed from the middle and low pressure stages of the steam engine is partially extracted, and the fuel heater and the air preheater are used. Since heated steam is sent to the preheater and the feedwater preheater, the problem that the output of the steam engine is reduced also disappears.
【００１８】[0018]
【実施例】図１に示した実施例は、図２に示した蒸気原
動機システムをベースとして、高圧ボイラー１の燃焼排
気ガス煙道３に、燃焼排気ガスと熱交換する蒸気発生器
４を設けると共に、前記高圧ボイラー１とは別に低圧ボ
イラー５を設け、この低圧ボイラー５と蒸気発生器４と
の間に、循環ポンプ６をもち、前記低圧ボイラー５の缶
水部５ａから取出す缶水を、前記蒸気発生器４に循環さ
せて蒸気を発生させ、前記低圧ボイラー５に戻す缶水循
環路７を設け、前記低圧ボイラー５の蒸気域に、前記蒸
気発生器４で発生した蒸気を取出して、燃料加熱器８、
空気予熱器９及び給水予熱器１０，１１の熱源として利
用する熱回収蒸気管１２を接続したものである。The embodiment shown in FIG. 1 is based on the steam engine system shown in FIG. 2 and a steam generator 4 for exchanging heat with the combustion exhaust gas is provided in the combustion exhaust gas flue 3 of the high-pressure boiler 1. At the same time, a low-pressure boiler 5 is provided separately from the high-pressure boiler 1, and a circulation pump 6 is provided between the low-pressure boiler 5 and the steam generator 4, and can water extracted from the can water portion 5a of the low-pressure boiler 5 is A can water circulation passage 7 is provided to circulate the steam in the steam generator 4 and return the steam to the low pressure boiler 5. The steam generated in the steam generator 4 is taken out in the steam region of the low pressure boiler 5 to remove the fuel. Heater 8,
A heat recovery steam pipe 12 used as a heat source for the air preheater 9 and the feed water preheaters 10 and 11 is connected.
【００１９】更に詳記すると、前記高圧ボイラー１は、
原油、重油、石炭を燃料とするバーナー（図示せず）を
もった燃焼室２とこの燃焼室２に連通する燃焼排気ガス
煙道３とをもち、前記燃焼室２の周りには蒸気管１３を
配設すると共に、この蒸気管１３と接続するボイラード
ラム１４を設け、このドラム１４の蒸気域には前記燃焼
室２に内装する過熱器１５を接続しており、また、前記
ドラム１４の液域には前記燃焼室２に内装する給水加熱
器１６を接続している。More specifically, the high-pressure boiler 1 is
It has a combustion chamber 2 having a burner (not shown) that uses crude oil, heavy oil, and coal as fuel, and a combustion exhaust gas flue 3 communicating with the combustion chamber 2, and a steam pipe 13 around the combustion chamber 2. And a boiler drum 14 connected to the steam pipe 13 is provided, and a superheater 15 installed in the combustion chamber 2 is connected to the steam region of the drum 14, and the liquid of the drum 14 is A feed water heater 16 installed in the combustion chamber 2 is connected to the area.
【００２０】また、前記高圧ボイラー１の燃料供給管１
７には前記燃料加熱器８を、また、燃焼空気を供給する
空気管１８には、前記空気予熱器９を介装すると共に、
給水管１９には、前記給水予熱器１０，１１を介装して
いる。Further, the fuel supply pipe 1 of the high-pressure boiler 1
7, the fuel heater 8 is provided, and the air pipe 18 for supplying combustion air is provided with the air preheater 9,
The water supply pipe 19 is provided with the water supply preheaters 10 and 11.
【００２１】また前記低圧ボイラー５はバーナー（図示
せず）をもった燃焼室２０及び煙道２１を備え、缶水部
５ａの底部には、給水予熱器２２及び給水ポンプ２３を
もち、前記燃料加熱器８、空気予熱器９及び給水予熱器
１０，１１のドレンタンク（図示せず）に連通され６０
℃になるドレンを前記缶水部５ａに供給する給水管２４
を接続しており、また、この低圧ボイラー５のバーナー
は高圧ボイラー１の起動時には点火して缶水部５ａの缶
水を加熱するが、前記高圧ボイラー１の起動後における
運転中には、不足蒸気を補うために運転するだけでよい
ようにしている。The low-pressure boiler 5 is provided with a combustion chamber 20 having a burner (not shown) and a flue 21, and has a feed water preheater 22 and a feed pump 23 at the bottom of the can water portion 5a. 60 is connected to the drain tank (not shown) of the heater 8, the air preheater 9, and the feedwater preheaters 10 and 11.
A water supply pipe 24 for supplying a drainage of ℃ to the can water portion 5a
The burner of the low-pressure boiler 5 is ignited when the high-pressure boiler 1 is started to heat the can water in the can water portion 5a, but the burner of the high-pressure boiler 1 is insufficient during operation after the start. It only requires driving to supplement the steam.
【００２２】また、前記過熱器１５の出口側には蒸気原
動機２５が高圧蒸気管２６を介して接続されると共に、
前記蒸気原動機２５の出口側に接続する低圧蒸気管２７
には復水器２８が接続され、復水ポンプ２９を介して前
記給水器１９に連通しており、この給水管１９が給水ポ
ンプ３０を介して前記給水加熱器１６に接続されてい
る。A steam engine 25 is connected to the outlet side of the superheater 15 via a high-pressure steam pipe 26, and
Low-pressure steam pipe 27 connected to the outlet side of the steam engine 25
A condenser 28 is connected to the water supply device 28, communicates with the water supply device 19 via a condensate pump 29, and the water supply pipe 19 is connected to the water supply heater 16 via a water supply pump 30.
【００２３】更に、前記低圧ボイラー５の蒸気域に接続
する前記熱回収蒸気管１２は、複数の分岐管３１，３
２，３３，３４を設けて、第１分岐管３１を前記燃料加
熱器８に、第２分岐管３２を前記空気予熱器９に、ま
た、第３分岐管３３を前記給水予熱器１１にそれぞれ接
続し、更に第４分岐管３４を前記低圧ボイラー５の給水
管２４に介装する給水予熱器２２に接続しており、ま
た、前記燃料加熱器８及び空気予熱器９における蒸気系
出口を前記高圧ボイラー１への給水管１９で前記給水予
熱器１１の一次側に介装するもう一つの給水予熱器１０
に接続している。Further, the heat recovery steam pipe 12 connected to the steam region of the low-pressure boiler 5 has a plurality of branch pipes 31, 3.
2, 33, 34 are provided, the first branch pipe 31 is used for the fuel heater 8, the second branch pipe 32 is used for the air preheater 9, and the third branch pipe 33 is used for the water supply preheater 11. Further, the fourth branch pipe 34 is connected to the feed water preheater 22 which is interposed in the feed water pipe 24 of the low pressure boiler 5, and the steam system outlets of the fuel heater 8 and the air preheater 9 are connected to the above. Another water supply preheater 10 which is provided on the primary side of the water supply preheater 11 by a water supply pipe 19 to the high-pressure boiler 1.
Connected to.
【００２４】しかして以上の構成において、前記高圧ボ
イラー１の運転による前記蒸気原動機２５の駆動時、前
記高圧ボイラー１の燃焼排気ガス煙道３に設けた蒸気発
生器４には、前記低圧ボイラー５の缶水部５ａから取出
された缶水が循環ポンプ６の駆動で供給されるのであ
り、この缶水が前記高圧ボイラー１の燃焼排気ガスと熱
交換して蒸気となり、前記循環路７を介して前記低圧ボ
イラー５に戻り、その蒸気域から熱回収蒸気管１２に取
出される蒸気は、前記各分岐管３１〜３４を経て前記燃
料加熱器８、空気予熱器９、給水予熱器１０，１１及び
低圧ボイラー５の給水予熱器２２に、低圧ボイラー蒸気
として供給され、燃料加熱、空気予熱及び給水予熱の熱
源として熱回収利用がなされるのである。With the above structure, when the steam engine 25 is driven by operating the high-pressure boiler 1, the low-pressure boiler 5 is connected to the steam generator 4 provided in the combustion exhaust gas flue 3 of the high-pressure boiler 1. The canned water taken out from the canned water portion 5a of the above is supplied by the drive of the circulation pump 6, and this canned water exchanges heat with the combustion exhaust gas of the high-pressure boiler 1 into steam, and passes through the circulation path 7. Returning to the low-pressure boiler 5, and the steam extracted from the steam region to the heat recovery steam pipe 12 passes through the branch pipes 31 to 34 and the fuel heater 8, the air preheater 9, and the feed water preheaters 10 and 11. And is supplied to the feedwater preheater 22 of the low-pressure boiler 5 as low-pressure boiler steam, and is used for heat recovery as a heat source for fuel heating, air preheating, and feedwater preheating.
【００２５】従って、高圧ボイラー１から排出される高
温の燃焼排気ガスから缶水を介して熱回収されるから、
その熱回収が十分に行えると共にこの熱回収は、硫酸腐
食なく行えるのであって、硫酸腐食なく熱回収が有効に
できて燃料消費量を少なくし、省エネルギーが得られる
のであり、しかも従来例のように蒸気原動機の動力を減
少させることの不具合もないのである。Therefore, heat is recovered from the high-temperature combustion exhaust gas discharged from the high-pressure boiler 1 through the can water,
The heat recovery can be sufficiently performed and this heat recovery can be performed without sulfuric acid corrosion. Therefore, the heat recovery can be effectively performed without sulfuric acid corrosion, the fuel consumption can be reduced, and the energy saving can be obtained. There is also no problem with reducing the power of the steam engine.
【００２６】次に下記要目で高圧ボイラー１及び低圧ボ
イラー５を運転する場合の省エネルギー効果を説明す
る。Next, the energy saving effect when operating the high-pressure boiler 1 and the low-pressure boiler 5 will be described below.
【００２７】 高圧ボイラー要目 常用圧力 ４９．０Kg/cm2G 蒸気温度 ４００℃（過熱） 蒸発量 ４０，０００Kg/H 給水温度 １４０℃ 燃料種類 Ｃ重油 必要燃料量 ３９５０Kg/H 排気ガス温度 ６００℃（100%負荷) 低圧ボイラー要目 常用圧力 ５．０Kg/cm2G 蒸気温度 １５８℃（飽和） 蒸発量 １１，０００Kg/H 給水温度 ６０℃ 燃焼方式 押込通風油焚 燃料種類 Ｃ重油 必要燃料量 ９００Kg/H 高圧ボイラー１の燃焼による排気ガス量Ｇｖ（Ｎm3／K
g）は、次の数１及び数２に示す実験式（石谷式）を適
用することにより近似的に求められる。High-pressure boiler Essential pressure Normal pressure 49.0Kg / cm 2 G Steam temperature 400 ° C (overheat) Evaporation amount 40,000Kg / H Water supply temperature 140 ° C Fuel type C heavy oil Required fuel amount 3950Kg / H Exhaust gas temperature 600 ° C ( 100% load) Low-pressure boiler Essential pressure Normal pressure 5.0Kg / cm 2 G Steam temperature 158 ℃ (Saturation) Evaporation amount 11,000Kg / H Water supply temperature 60 ℃ Combustion method Pushed draft oil Fuel type C Heavy oil Required fuel amount 900Kg / H Exhaust gas amount Gv (Nm 3 / K
g) is approximately obtained by applying the empirical formula (Ishitani formula) shown in the following formulas 1 and 2.
【００２８】[0028]
【数１】 Ｇｖ＝Ｇ0 ｖ＋（μ−１）Ｌ0 ｖ Ｇ0 ｖ：液体燃料の燃焼ガス量 Ｌ0 ｖ：液体燃料燃焼時の理論空気量 μ：空気過剰率（空気比）## EQU1 ## Gv = G 0 v + (μ-1) L 0 v G 0 v: combustion gas amount of liquid fuel L 0 v: theoretical air amount during liquid fuel combustion μ: excess air ratio (air ratio)
【００２９】[0029]
【数２】 [Equation 2]
【００３０】しかして、前記高圧ボイラー１でＣ重油を
燃焼させる場合、Ｃ重油１Ｋｇが完全燃焼するときに必
要な空気過剰率μを、実際例から１．２とすると、Ｃ重
油の低位発熱量Ｈｌは９，６００（Kcal/Kg)であるか
ら、数１及び数２から燃焼排気ガス量Ｇｖを求めると、
１２，９９２（Nm3/Kg) となる。When the C heavy oil is burned in the high-pressure boiler 1, if the excess air ratio μ required when 1 kg of the C heavy oil is completely burned is 1.2 from the actual example, the lower heating value of the C heavy oil is obtained. Since Hl is 9,600 (Kcal / Kg), when the combustion exhaust gas amount Gv is obtained from the equations 1 and 2,
It becomes 12,992 (Nm 3 / Kg).
【００３１】従って、１００％負荷で１時間に３，９５
０ＫｇのＣ重油が燃焼したときに発生する時間当たりの
燃焼排気ガス量ＧN （Nm3/H)は、Therefore, at a load of 100%, 3,95 per hour
The combustion exhaust gas amount G N (Nm 3 / H) per hour generated when 0 kg of C heavy oil is burned is
【００３２】[0032]
【数３】 ＧN ＝12,992(Nm3/Kg ) ×３，９５０（Kg
/H) ＝51,318.4 (Nm3 ／Ｈ） となる。[Formula 3] G N = 12,992 (Nm 3 / Kg) × 3,950 (Kg
/ H) = 51,318.4 (Nm 3 / H).
【００３３】所で蒸気発生器４における排気ガスの入口
側温度を６００℃とし、排気ガスの出口側温度を２５０
℃とすると、排気ガスの平均定圧比熱は０．３３（Kcal
/Nm 3 ℃）であるから、蒸気発生器４における蒸発部で
の熱損失を１０％とすると、この蒸気発生器４で得られ
る乾き飽和の蒸気量ｘ（Kg/H) は、The temperature of the exhaust gas inlet side of the steam generator 4 is 600 ° C., and the temperature of the exhaust gas outlet side is 250 ° C.
℃, the average constant pressure specific heat of exhaust gas is 0.33 (Kcal
/ Nm 3 ° C), so if the heat loss in the evaporation part of the steam generator 4 is 10%, the dry saturated steam amount x (Kg / H) obtained by this steam generator 4 is
【００３４】[0034]
【数４】 [Equation 4]
【００３５】一方、前記高圧ボイラー１の給水管１９に
おける給水予熱器１０，１１の給水入口側温度を２０℃
とし、出口側温度を１４０℃とすると、前記給水予熱器
１０，１１に必要とする蒸気量ａ（Kg/H) は、On the other hand, the temperature of the water supply inlet side of the water supply preheaters 10 and 11 in the water supply pipe 19 of the high-pressure boiler 1 is set to 20 ° C.
And the outlet side temperature is 140 ° C., the steam amount a (Kg / H) required for the feedwater preheaters 10 and 11 is
【００３６】[0036]
【数５】 [Equation 5]
【００３７】となり、また、燃料加熱器８における燃料
入口側温度を３０℃とし、出口側温度を９０℃とする
と、この燃料加熱器８に必要する蒸気量ｂ（Kg/H) は、Further, when the fuel inlet side temperature in the fuel heater 8 is 30 ° C. and the outlet side temperature is 90 ° C., the vapor amount b (Kg / H) required for this fuel heater 8 is
【００３８】[0038]
【数６】 [Equation 6]
【００３９】となり、また、空気予熱器９における空気
入口側温度を２０℃とし、出口側温度を１００℃とする
と、この空気予熱器９に必要とする蒸気量ｃ（Kg/H）
は、Further, assuming that the air inlet side temperature in the air preheater 9 is 20 ° C. and the outlet side temperature is 100 ° C., the steam amount c (Kg / H) required for this air preheater 9
Is
【００４０】[0040]
【数７】 [Equation 7]
【００４１】となり、更に前記低圧ボイラー５の給水管
２４における給水予熱器２２の給水入口側温度を６０℃
とし、出口側温度を１５０℃とすると、この給水予熱器
２２に必要とする蒸発量ｄ（Kg/H) は、Further, the temperature of the water supply inlet side of the water supply preheater 22 in the water supply pipe 24 of the low-pressure boiler 5 is set to 60 ° C.
And the outlet side temperature is 150 ° C., the evaporation amount d (Kg / H) required for this feedwater preheater 22 is
【００４２】[0042]
【数８】 [Equation 8]
【００４３】となり、これら給水予熱器１０，１１及び
２２と、燃料加熱器８と空気予熱器９に必要とする蒸気
量（ａ，ｂ，ｃ，ｄ）のトータルは１０，０７０（kg/
H) となる。Therefore, the total amount of steam (a, b, c, d) required for the feed water preheaters 10, 11 and 22, the fuel heater 8 and the air preheater 9 is 10,070 (kg /
H)
【００４４】従って、このトータル蒸気量（ａ〜ｄ）
は、前記蒸気発生器４で得られる蒸気量ｘ（Kg/H) と低
圧ボイラー５の運転とによって賄えるのである。従っ
て、前記蒸気発生器４で得ることのできる蒸気量に相当
する低圧ボイラー５での必要燃料量７３０(Kg/H)に相当
するＣ重油量の価格、即ち、Ｃ重油量価格を２７（円／
Kg) とすると時間当たりの１９，７００円／Ｈのコスト
ダウンが可能となり、図２に示した従来例に比較してそ
れだけ省エネルギーが実現出来るのであり、しかもこの
き、蒸気原動機２５の発生動力を減ずることもないので
ある。Therefore, this total vapor amount (a to d)
Can be covered by the steam amount x (Kg / H) obtained in the steam generator 4 and the operation of the low-pressure boiler 5. Therefore, the price of the amount of C heavy oil corresponding to the required fuel amount 730 (Kg / H) in the low pressure boiler 5 corresponding to the amount of steam that can be obtained by the steam generator 4, that is, the C heavy oil amount price is 27 (yen /
If Kg) is set, the cost per hour can be reduced by 19,700 yen / H, and energy saving can be realized as compared with the conventional example shown in FIG. 2. Moreover, the power generated by the steam engine 25 can be reduced. There is no reduction.
【００４５】また、前記低圧ボイラー５の缶水部５ａか
ら取出される缶水は、使用圧力の５kg/cm2Ｇにおいて１
５８℃の飽和水温度を保有しており、前記蒸気発生器４
において６００℃の排気ガスと熱交換する熱交換面の温
度は亜硫酸ガスの露点温度（１６０℃）より高温とな
り、従って、硫酸腐食も回避できるのである。The canned water taken out from the canned water portion 5a of the low-pressure boiler 5 is 1 at a working pressure of 5 kg / cm 2 G.
Having a saturated water temperature of 58 ° C., the steam generator 4
At 600 ° C., the temperature of the heat exchange surface for exchanging heat with the exhaust gas is higher than the dew point temperature (160 ° C.) of sulfurous acid gas, and therefore sulfuric acid corrosion can be avoided.
【００４６】以上説明した実施例は蒸気原動機システム
に適用した高圧ボイラーについて説明したが、その他暖
房機又は吸収式冷凍機の高圧ボイラーに適用することも
できる。Although the above-described embodiments have been described with respect to the high-pressure boiler applied to the steam engine system, they can also be applied to other high-pressure boilers for heating machines or absorption chillers.
【００４７】[0047]
【発明の効果】以上のように本発明によれば低圧ボイラ
ー５を併用し、高圧ボイラー１の燃焼排気ガス煙道３に
設ける蒸気発生器４により高温の燃焼排気ガスから熱回
収するようにしたから、燃焼排気ガスの熱回収を缶水を
介して行え、従って、その熱回収を硫酸腐食なく、しか
も十分行えるのであって、燃料消費量を少なくして省エ
ネルギーが可能となり、また、従来例のように蒸気原動
機システムに適用する場合においては、この蒸気原動機
の動力を減少させる従来例の不具合も解消できるのであ
る。As described above, according to the present invention, the low pressure boiler 5 is also used, and the heat is recovered from the high temperature combustion exhaust gas by the steam generator 4 provided in the combustion exhaust gas flue 3 of the high pressure boiler 1. Therefore, the heat of the combustion exhaust gas can be recovered through the can water, and therefore, the heat can be recovered sufficiently without sulfuric acid corrosion, and the fuel consumption can be reduced to save energy. When applied to the steam engine system as described above, it is possible to solve the problem of the conventional example in which the power of the steam engine is reduced.
【図１】 本発明システムの一実施例を示す配管系統
図。FIG. 1 is a piping system diagram showing an embodiment of the system of the present invention.
【図２】 従来例を示す配管系統図。FIG. 2 is a piping system diagram showing a conventional example.
１ 高圧ボイラー ２
燃焼室 ３ 煙道 ４
蒸気発生器 ５ 低圧ボイラー ６
循環ポンプ ７ 缶水循環路 ８
燃料加熱器 ９ 空気予熱器 １０，１１
給水予熱器 １２ 熱回収蒸気管1 high pressure boiler 2
Combustion chamber 3 Flue 4
Steam generator 5 Low-pressure boiler 6
Circulation pump 7 Can water circulation path 8
Fuel heater 9 Air preheater 10, 11
Water supply preheater 12 Heat recovery steam pipe
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成５年１０月８日[Submission date] October 8, 1993
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】０００４[Correction target item name] 0004
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【０００４】また、前記ボイラー１０１の燃焼室周りに
は蒸発管１１０が配設されると共に、この蒸発管１１０
と接続するボイラードラム１１１を設け、このドラム１
１１の蒸気域には、前記燃焼室に内装する過熱器１１２
が接続され、この過熱器１１２に前記高圧蒸気管１０３
が接続されている。[0004] Further, around the combustion chamber of the boiler 101 together when the evaporation pipe 110 is disposed, the evaporation tube 110
Boiler drum 111 connected to
In the steam region 11 there is a superheater 112 installed inside the combustion chamber.
Is connected to the superheater 112, and the high-pressure steam pipe 103 is connected to the superheater 112.
Are connected.
【手続補正２】[Procedure Amendment 2]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１１[Correction target item name] 0011
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１１】本発明の目的は、燃焼排気ガスの熱回収を
硫酸腐食なく、かつ十分行え、燃料消費量を少なくして
省エネルギが可能で、しかも蒸気原動機の動力を減少さ
せることのないボイラーの燃焼排気ガス利用システムを
提供することにある。An object of the present invention, no sulfuric acid corrosion of the heat recovery of the combustion exhaust gases, and sufficient can, the fuel consumption decreased to possible energy saving, yet without reducing the power of the steam prime mover boilers To provide a combustion exhaust gas utilization system of
【手続補正３】[Procedure 3]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１９[Correction target item name] 0019
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１９】更に詳記すると、前記高圧ボイラー１は、
原油、重油、石炭を燃料とするバーナー（図示せず）を
もった燃焼室２とこの燃焼室２に連通する燃焼排気ガス
煙道３とをもち、前記燃焼室２の周りには蒸発管１３を
配設すると共に、この蒸発管１３と接続するボイラード
ラム１４を設け、このドラム１４の蒸気域には前記燃焼
室２に内装する過熱器１５を接続しており、また、前記
ドラム１４の液域には前記燃焼室２に内装する給水加熱
器１６を接続している。More specifically, the high-pressure boiler 1 is
Crude, heavy oil, coal has a combustion exhaust gas flue 3 that communicates with the combustion chamber 2 of the combustion chamber 2 Toko with burner (not shown) to fuel, evaporation tubes around the combustion chamber 2 13 while disposed, the boiler drum 14 to be connected to the evaporation pipe 13 provided on the steam zone of the drum 14 connects the superheater 15 to interior into the combustion chamber 2, also the drum 14 A feed water heater 16 installed in the combustion chamber 2 is connected to the liquid region of the above.
【手続補正４】[Procedure amendment 4]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００３０[Name of item to be corrected] 0030
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００３０】しかして、前記高圧ボイラー１でＣ重油を
燃焼させる場合、Ｃ重油１Ｋｇが完全燃焼するときに必
要な空気過剰率μを、実際例から１．２とすると、Ｃ重
油の低位発熱量Ｈｌは９，６００（Kcal/Kg)であるか
ら、数１及び数２から燃焼排気ガス量Ｇｖを求めると、
１２．９９２（Nm3/Kg) となる。When the C heavy oil is burned in the high-pressure boiler 1, if the excess air ratio μ required when 1 kg of the C heavy oil is completely burned is 1.2 from the actual example, the lower heating value of the C heavy oil is obtained. Since Hl is 9,600 (Kcal / Kg), when the combustion exhaust gas amount Gv is obtained from the equations 1 and 2,
It becomes 12.992 (Nm 3 / Kg).
【手続補正５】[Procedure Amendment 5]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００３２[Name of item to be corrected] 0032
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００３２】[0032]
【数３】 ＧN ＝12.992(Nm3/Kg ) ×３，９５０（Kg
/H) ＝51,318.4 (Nm3 ／Ｈ） となる。[Formula 3] G N = 1.992 (Nm 3 / Kg) × 3,950 (Kg
/ H) = 51,318.4 (Nm 3 / H).
【手続補正６】[Procedure correction 6]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００３６[Correction target item name] 0036
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００３６】[0036]
【数５】 [Equation 5]
【手続補正７】[Procedure Amendment 7]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００４１[Correction target item name] 0041
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００４１】となり、更に前記低圧ボイラー５の給水管
２４における給水予熱器２２の給水入口側温度を６０℃
とし、出口側温度を１５０℃とすると、この給水予熱器
２２に必要とする蒸気量ｄ（Kg/H) は、Further, the temperature of the water supply inlet side of the water supply preheater 22 in the water supply pipe 24 of the low-pressure boiler 5 is set to 60 ° C.
And then, if the outlet temperature is 0.99 ° C., vapor amount d in need for this water preheater 22 (Kg / H) is
【手続補正８】[Procedure Amendment 8]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００４４[Correction target item name] 0044
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００４４】従って、このトータル蒸気量（ａ〜ｄ）
は、前記蒸気発生器４で得られる蒸気量ｘ（Kg/H) と低
圧ボイラー５の運転とによって賄えるのである。従っ
て、前記蒸気発生器４で得ることのできる蒸気量に相当
する低圧ボイラー５での必要燃料量９００(Kg/H)に相当
するＣ重油量の価格、即ち、Ｃ重油量価格を２７（円／
Kg) とすると時間当たりの１９，７００円／Ｈのコスト
ダウンが可能となり、図２に示した従来例に比較してそ
れだけ省エネルギーが実現出来るのであり、しかもこの
上、蒸気原動機２５の発生動力を減ずることもないので
ある。Therefore, this total vapor amount (a to d)
Can be covered by the steam amount x (Kg / H) obtained in the steam generator 4 and the operation of the low-pressure boiler 5. Therefore, the price of the amount of C heavy oil corresponding to the required fuel amount 900 (Kg / H) in the low pressure boiler 5 corresponding to the amount of steam that can be obtained by the steam generator 4, that is, the C heavy oil amount price is 27 (yen /
If Kg) is set, the cost per hour can be reduced by 19,700 yen / H, and energy saving can be realized as compared with the conventional example shown in FIG.
Moreover , the power generated by the steam engine 25 is not reduced.
Claims (1)
（３）とをもつ高圧ボイラー（１）の燃焼排気ガス利用
システムであって、 前記煙道（３）に設けられ、燃焼排気ガスと熱交換する
蒸気発生器（４）と、 前記高圧ボイラー（１）とは別に設ける低圧ボイラー
（５）と、 この低圧ボイラー（５）と前記蒸気発生器（４）との間
に設けられ、前記低圧ボイラー（５）から缶水を、前記
蒸気発生器（４）に循環させて蒸気を発生させ、前記低
圧ボイラー（５）に戻す循環ポンプ（６）をもった缶水
循環路（７）とを備え、 前記低圧ボイラー（５）の蒸気域に、前記蒸気発生器
（４）で発生した蒸気を取出し、前記高圧ボイラー
（１）における給水予熱などの熱源に利用する熱回収蒸
気管（１２）を接続していることを特徴とするボイラー
の燃焼排気ガス利用システム。1. A combustion exhaust gas utilization system for a high-pressure boiler (1) having a combustion chamber (2) and a combustion exhaust gas flue (3), the flue (3) being provided with the combustion exhaust gas. A steam generator (4) for exchanging heat with gas; a low pressure boiler (5) provided separately from the high pressure boiler (1); and a low pressure boiler (5) provided between the low pressure boiler (5) and the steam generator (4). A can water circulation path (7) having a circulation pump (6) for circulating can water from the low pressure boiler (5) to the steam generator (4) to generate steam and returning the steam to the low pressure boiler (5). And a heat recovery steam pipe (12) for taking out steam generated in the steam generator (4) into a steam region of the low pressure boiler (5) and utilizing it as a heat source for preheating feed water in the high pressure boiler (1). ) Is connected to the boiler combustion Gas-gas utilization system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21315993A JPH0763303A (en) | 1993-08-27 | 1993-08-27 | System for utilizing combustion exhaust gas of boiler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21315993A JPH0763303A (en) | 1993-08-27 | 1993-08-27 | System for utilizing combustion exhaust gas of boiler |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0763303A true JPH0763303A (en) | 1995-03-07 |
Family
ID=16634549
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21315993A Pending JPH0763303A (en) | 1993-08-27 | 1993-08-27 | System for utilizing combustion exhaust gas of boiler |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0763303A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103542396A (en) * | 2012-07-11 | 2014-01-29 | 三浦工业株式会社 | Boiler for vessel |
| CN104501126A (en) * | 2014-12-12 | 2015-04-08 | 安徽宏宇竹木制品有限公司 | Steam boiler |
| CN104633636A (en) * | 2013-11-15 | 2015-05-20 | 安阳市方快锅炉有限公司 | Saturated steam combined boiler and quick steam manufacturing method |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59113213A (en) * | 1982-12-20 | 1984-06-29 | Hitachi Ltd | Double-pressure type superhigh temperature and high-pressure steam turbine plant |
| JPH0448101A (en) * | 1990-06-15 | 1992-02-18 | Hirakawa Tekkosho:Kk | Combination type boiler |
-
1993
- 1993-08-27 JP JP21315993A patent/JPH0763303A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59113213A (en) * | 1982-12-20 | 1984-06-29 | Hitachi Ltd | Double-pressure type superhigh temperature and high-pressure steam turbine plant |
| JPH0448101A (en) * | 1990-06-15 | 1992-02-18 | Hirakawa Tekkosho:Kk | Combination type boiler |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103542396A (en) * | 2012-07-11 | 2014-01-29 | 三浦工业株式会社 | Boiler for vessel |
| CN103542396B (en) * | 2012-07-11 | 2016-09-07 | 三浦工业株式会社 | Boiler for vessel |
| CN104633636A (en) * | 2013-11-15 | 2015-05-20 | 安阳市方快锅炉有限公司 | Saturated steam combined boiler and quick steam manufacturing method |
| CN104501126A (en) * | 2014-12-12 | 2015-04-08 | 安徽宏宇竹木制品有限公司 | Steam boiler |
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