JPH07167401A - Double pressure type waste heat recovery boiler water supplying apparatus - Google Patents

Double pressure type waste heat recovery boiler water supplying apparatus

Info

Publication number
JPH07167401A
JPH07167401A JP6247861A JP24786194A JPH07167401A JP H07167401 A JPH07167401 A JP H07167401A JP 6247861 A JP6247861 A JP 6247861A JP 24786194 A JP24786194 A JP 24786194A JP H07167401 A JPH07167401 A JP H07167401A
Authority
JP
Japan
Prior art keywords
pressure
economizer
low
water
water supply
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
Application number
JP6247861A
Other languages
Japanese (ja)
Inventor
Naotake Mochida
Masayuki Narita
Kohei Saito
Minoru Yamada
実 山田
正幸 成田
尚毅 持田
浩平 斉藤
Original Assignee
Toshiba Corp
株式会社東芝
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to JP26482293 priority Critical
Priority to JP5-264822 priority
Application filed by Toshiba Corp, 株式会社東芝 filed Critical Toshiba Corp
Priority to JP6247861A priority patent/JPH07167401A/en
Publication of JPH07167401A publication Critical patent/JPH07167401A/en
Pending legal-status Critical Current

Links

Abstract

PURPOSE:To prevent deterioration of a high-pressure water supply pump by reducing a change width of a high-pressure water supply pump inlet supply water temperature as much as possible. CONSTITUTION:A double pressure type waste heat recovery boiler water supplying apparatus comprises a high-pressure drum 16 and a low-pressure drum 17 respectively coupled to a high-pressure vaporizer 12 and a low-pressure vaporizer 14, and a high-pressure economizer 18 and a low-pressure economizer 15 for supplying water to the drums 16 and 17, wherein a high-pressure water supply tube 34 is branched from a low-pressure water supply tube 32 of an upstream side of the economizer 15, and water is fed to the economizer 18 through a high-pressure water supply pump 33 connected to the tube 34.

Description

【発明の詳細な説明】Detailed Description of the Invention
【0001】[0001]
【産業上の利用分野】本発明は排熱回収ボイラの高圧節
炭器へ給水を供給する高圧給水ポンプ入口温度の変化幅
を極力抑える複圧式排熱回収ボイラ給水装置に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-pressure type exhaust heat recovery boiler water supply apparatus for suppressing the variation range of the inlet temperature of a high pressure water supply pump for supplying water to a high pressure economizer of an exhaust heat recovery boiler.
【0002】[0002]
【従来の技術】図4は従来の複圧式排熱回収ボイラ給水
装置の系統図を示す。図4に示すように、複圧式排熱回
収ボイラ1内には、高圧蒸気過熱器11、高圧蒸発器1
2、高圧節炭器13、低圧蒸発器14および低圧節炭器
15が排ガスの下流側に向かって配設される。
2. Description of the Related Art FIG. 4 is a system diagram of a conventional double pressure type exhaust heat recovery boiler water supply system. As shown in FIG. 4, a high pressure steam superheater 11 and a high pressure evaporator 1 are provided in the double pressure type exhaust heat recovery boiler 1.
2, the high-pressure economizer 13, the low-pressure evaporator 14, and the low-pressure economizer 15 are arranged toward the downstream side of the exhaust gas.
【0003】また、高圧蒸発器12は高圧ドラム16
と、低圧蒸発器14は低圧ドラム17とそれぞれ連結さ
れ、低圧給水ポンプ31により昇圧された低圧給水は、
低圧給水管32を経て低圧節炭器15で昇温された後、
低圧給水管32を経て低圧ドラム17へ送水され、さら
に低圧主蒸気管22を介して蒸気タービン23の低圧側
に案内するようになっている。
The high pressure evaporator 12 is a high pressure drum 16
The low-pressure evaporator 14 is connected to the low-pressure drum 17, and the low-pressure water supplied to the low-pressure water supply pump 31 is
After the temperature is raised in the low pressure economizer 15 via the low pressure water supply pipe 32,
Water is sent to the low-pressure drum 17 via the low-pressure water supply pipe 32, and is further guided to the low-pressure side of the steam turbine 23 via the low-pressure main steam pipe 22.
【0004】一方、高圧給水は低圧節炭器15出口で分
岐された高圧給水管34を通り、高圧給水ポンプ33、
および高圧節炭器13を介して高圧ドラム16へ送水さ
れ、さらに高圧蒸発器12で蒸気化された後、高圧蒸気
過熱器11で過熱されて高圧主蒸気管21を介して蒸気
タービン23の高圧側に供給される。
On the other hand, the high-pressure feed water passes through the high-pressure feed pipe 34 branched at the outlet of the low-pressure economizer 15, and the high-pressure feed pump 33,
Water is sent to the high-pressure drum 16 via the high-pressure coal economizer 13, further vaporized in the high-pressure evaporator 12, and then superheated in the high-pressure steam superheater 11 to generate high pressure in the steam turbine 23 via the high-pressure main steam pipe 21. Supplied to the side.
【0005】そして、蒸気タービン23に供給された主
蒸気は、蒸気タービン23を回転駆動することで、発電
機24を駆動させた後、復水器25に案内されて凝縮液
化される。
The main steam supplied to the steam turbine 23 drives the generator 24 by rotating the steam turbine 23, and then is guided to the condenser 25 to be condensed and liquefied.
【0006】また、低圧節炭器15における低温腐食を
防止するため、高圧給水の一部は高圧給水ポンプ33出
口で分岐した給水再循環管35を経て、温度調節弁であ
る給水再循環水調節弁36を介して低温給水管32へ再
循環させる。この際、給水再循環水調節弁36の開度は
温度コントローラ37に基づいて調整されることで、低
圧節炭器15入口における給水の温度を一定に保持して
いる。
Further, in order to prevent low temperature corrosion in the low pressure economizer 15, a part of the high pressure feed water passes through a feed water recirculation pipe 35 branched at the outlet of the high pressure feed pump 33, and a feed water recirculation water control which is a temperature control valve. Recirculate to the cold water supply pipe 32 via valve 36. At this time, the opening degree of the feed water recirculation water control valve 36 is adjusted based on the temperature controller 37 to keep the temperature of the feed water at the inlet of the low pressure economizer 15 constant.
【0007】[0007]
【発明が解決しようとする課題】ところで、上記従来例
によると、高圧給水を低圧節炭器15出口から取り出し
ているため、排熱回収ボイラ1の起動時、高圧給水ポン
プ33を通過する給水は短時間に温度上昇(約100℃
/分)する。
By the way, according to the above-mentioned conventional example, since the high pressure feed water is taken out from the outlet of the low pressure economizer 15, the feed water passing through the high pressure feed water pump 33 is not supplied when the exhaust heat recovery boiler 1 is started. Temperature rise in a short time (about 100 ℃
/ Min)
【0008】このため、高圧給水ポンプ33は過大な熱
衝撃を受け、その静止部と回転部との接触により損傷し
てポンプ構成部品が早期に劣化し、その結果寿命が短く
なり給水装置としての信頼性を著しく低下させる問題点
があった。
Therefore, the high-pressure water supply pump 33 receives an excessive thermal shock, is damaged by the contact between the stationary part and the rotating part of the high-pressure water supply pump 33, and the pump components are deteriorated at an early stage. There is a problem that the reliability is significantly lowered.
【0009】本発明は上述した事情を考慮してなされた
もので、高圧給水ポンプ入口給水温度の変化幅を極力小
さくすることにより、高圧給水ポンプの劣化を防止する
ことのできる複圧式排熱回収ボイラ給水装置を提供する
ことを目的とする。
The present invention has been made in consideration of the above-mentioned circumstances, and the double pressure type exhaust heat recovery capable of preventing deterioration of the high-pressure water supply pump by minimizing the change width of the inlet water temperature of the high-pressure water supply pump. It is intended to provide a boiler water supply device.
【0010】[0010]
【課題を解決するための手段】上述した課題を解決する
ために、本発明の請求項1は、高圧蒸発器および低圧蒸
発器にそれぞれ高圧ドラムおよび低圧ドラムを連結し、
これらのドラムにそれぞれ高圧節炭器および低圧節炭器
を介して給水を供給する複圧式排熱回収ボイラ給水装置
において、上記低圧節炭器の上流側の低圧給水管から高
圧給水管を分岐し、この高圧給水管に接続した高圧給水
ポンプを介して上記高圧節炭器へ送水したことを特徴と
する。
In order to solve the above-mentioned problems, the first aspect of the present invention is to connect a high-pressure evaporator and a low-pressure evaporator to a high-pressure drum and a low-pressure drum, respectively.
In a compound pressure heat recovery steam boiler water supply device that supplies water to these drums through a high-pressure economizer and a low-pressure economizer, respectively, a high-pressure water pipe is branched from a low-pressure water pipe upstream of the low-pressure economizer. It is characterized in that water is supplied to the high-pressure coal economizer via a high-pressure water supply pump connected to the high-pressure water supply pipe.
【0011】請求項2では、請求項1記載の高圧節炭器
の出口の最適温度箇所には分岐管が設けられ、この分岐
管を経て高圧給水管分岐点上流側の低圧給水管へ高圧給
水の一部を再循環させたことを特徴とする。
According to a second aspect of the present invention, a branch pipe is provided at an optimum temperature position at the outlet of the high pressure economizer according to the first aspect, and a high pressure water supply pipe is provided through the branch pipe to a low pressure water supply pipe upstream of the high pressure water supply pipe branch point. It is characterized in that a part of is recycled.
【0012】請求項3では、請求項1記載の低圧節炭器
出口には分岐管が設けられ、この分岐管に接続された給
水再循環ポンプを介して高圧給水管分岐点上流側の低圧
給水管へ低圧給水の一部を再循環させたことを特徴とす
る。
According to a third aspect of the present invention, a branch pipe is provided at the outlet of the low pressure economizer according to the first aspect, and a low pressure water supply upstream of the branch point of the high pressure water supply pipe is provided via a water supply recirculation pump connected to the branch pipe. It is characterized in that a part of the low-pressure feed water is recirculated to the pipe.
【0013】請求項4では、請求項2または3記載の再
循環させる管路には、高圧給水および低圧給水の量を調
整して高圧節炭器および低圧節炭器入口の給水温度を一
定に制御する手段を設けたことを特徴とする。
According to a fourth aspect of the present invention, the amount of high-pressure feed water and the amount of low-pressure feed water are adjusted in the recirculation pipe line according to the second or third aspect to keep the feed water temperature at the inlet of the high-pressure economizer and the low-pressure economizer constant. It is characterized in that means for controlling is provided.
【0014】請求項5では、請求項1記載の高圧給水ポ
ンプは、そのミニマムフロー管を高圧節炭器入口および
出口よりそれぞれ分岐して止め弁を設け、これらの止め
弁をユニットの運転状態に応じて切り換えることを特徴
とする。
According to a fifth aspect of the present invention, in the high-pressure water feed pump according to the first aspect, the minimum flow pipes are branched from the high pressure economizer inlet and outlet, respectively, to provide stop valves, and these stop valves are set to the operating state of the unit. It is characterized in that it is switched depending on the situation.
【0015】請求項6では、請求項1,2,4または5
記載の高圧節炭器は、高圧一次節炭器と高圧二次節炭器
とを備え、蒸気高圧一次節炭器を排ガスに対して低圧節
炭器と並列に配置したことを特徴とする。
In claim 6, claim 1, 2, 4 or 5
The described high-pressure economizer includes a high-pressure primary economizer and a high-pressure secondary economizer, and the steam high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to the exhaust gas.
【0016】請求項7では、高圧蒸発器および低圧蒸発
器にそれぞれ高圧ドラムおよび低圧ドラムを連結し、こ
れらのドラムにそれぞれ高圧節炭器および低圧節炭器を
介して給水を供給する複圧式排熱回収ボイラ給水装置に
おいて、上記高圧節炭器および低圧節炭器の上流側で、
且つ復水ポンプの下流側の復水管に給水ポンプを設け、
この給水ポンプの吐出水を上記高圧節炭器を通して高圧
ドラムへ送水する一方、上記給水ポンプの中間段の抽水
を上記低圧節炭器を通して低圧ドラムへ送水したことを
特徴とする。
According to the present invention, a high pressure evaporator and a low pressure evaporator are connected to a high pressure drum and a low pressure drum, respectively, and a double pressure type discharge for supplying water to these drums via the high pressure economizer and the low pressure economizer, respectively. In the heat recovery boiler water supply device, on the upstream side of the high pressure economizer and the low pressure economizer,
In addition, a water supply pump is installed in the condensate pipe on the downstream side of the condensate pump,
The discharge water of the water supply pump is sent to the high-pressure drum through the high-pressure economizer, while the extracted water in the intermediate stage of the water supply pump is sent to the low-pressure drum through the low-pressure economizer.
【0017】請求項8では、請求項7記載の低圧節炭器
の出口の最適温度箇所には分岐管が設けられ、この分岐
管を経て給水ポンプ上流側の復水管へ低圧給水の一部を
再循環させたことを特徴とする。
According to the present invention, a branch pipe is provided at the optimum temperature location at the outlet of the low-pressure economizer according to claim 7, and a part of the low-pressure feed water is fed to the condensate pipe upstream of the water feed pump via this branch pipe. It is characterized by being recycled.
【0018】請求項9では、請求項7または8記載の再
循環させる管路には、再循環水の量を調整して給水ポン
プ入口の給水温度を一定に制御する手段を設けたことを
特徴とする。
According to a ninth aspect of the present invention, the recirculation pipe line according to the seventh or eighth aspect is provided with means for adjusting the amount of recirculated water to control the feed water temperature at the feed water pump inlet at a constant level. And
【0019】請求項10では、請求項7,8または9記
載の高圧節炭器は高圧一次節炭器と高圧二次節炭器とを
備え、上記高圧一次節炭器を排ガスに対して低圧節炭器
と並列に配置したことを特徴とする。
In a tenth aspect, the high-pressure economizer according to claim 7, 8 or 9 comprises a high-pressure primary economizer and a high-pressure secondary economizer, and the high-pressure primary economizer is a low-pressure economizer for exhaust gas. It is characterized by being placed in parallel with the charcoal ware.
【0020】[0020]
【作用】上記の構成を有する本発明の請求項1において
は、低圧節炭器の上流側の低圧給水管から高圧給水管を
分岐し、この高圧給水管に接続した高圧給水ポンプを介
して高圧節炭器へ送水したことにより、高圧給水ポンプ
に過大な熱衝撃を与えることなく、高圧給水ポンプの劣
化を防止することができる。
In the first aspect of the present invention having the above-mentioned structure, the high pressure water supply pipe is branched from the low pressure water supply pipe on the upstream side of the low pressure economizer, and the high pressure water supply pump is connected to the high pressure water supply pipe. By supplying water to the economizer, it is possible to prevent deterioration of the high-pressure water supply pump without giving an excessive thermal shock to the high-pressure water supply pump.
【0021】請求項2において、高圧節炭器の出口の最
適温度箇所には分岐管が設けられ、この分岐管を経て高
圧給水管分岐点上流側の低圧給水管へ高圧給水の一部を
再循環させたことにより、低圧節炭器および高圧節炭器
における低温腐食を防止することができる。
In the second aspect, a branch pipe is provided at the optimum temperature location at the outlet of the high-pressure economizer, and a part of the high-pressure feed water is recycled to the low-pressure feed pipe upstream of the branch point of the high-pressure water feed pipe through this branch pipe. By circulating, it is possible to prevent low temperature corrosion in the low pressure economizer and the high pressure economizer.
【0022】請求項3において、低圧節炭器出口には分
岐管が設けられ、この分岐管に接続された給水再循環ポ
ンプを介して高圧給水管分岐点上流側の低圧給水管へ低
圧給水の一部を再循環させたことにより、低圧節炭器お
よび高圧節炭器における低温腐食を防止することができ
る。
In the third aspect, a branch pipe is provided at the outlet of the low-pressure economizer, and the low-pressure feed water is supplied to the low-pressure feed pipe upstream of the branch point of the high-pressure feed pipe via the feed water recirculation pump connected to the branch pipe. By recirculating a part, low temperature corrosion in a low pressure economizer and a high pressure economizer can be prevented.
【0023】請求項4において、再循環させる管路に
は、高圧給水および低圧給水の量を調整して高圧節炭器
および低圧節炭器入口の給水温度を一定に制御する手段
を設けたことにより、低圧節炭器および高圧節炭器の入
口給水温度が常に一定に維持される。
In claim 4, the recirculation pipe is provided with means for adjusting the amounts of the high-pressure feed water and the low-pressure feed water to control the feed water temperature at the inlets of the high-pressure economizer and the low-pressure economizer at a constant level. As a result, the inlet feed water temperature of the low-pressure economizer and the high-pressure economizer is always kept constant.
【0024】請求項5において、高圧給水ポンプは、そ
のミニマムフロー管を高圧節炭器入口および出口よりそ
れぞれ分岐して止め弁を設け、これらの止め弁をユニッ
トの運転状態に応じて切り換えることにより、暖機起動
時において円滑な起動が実現可能となる。
According to a fifth aspect of the present invention, in the high-pressure feed pump, the minimum flow pipe is branched from the inlet and the outlet of the high-pressure economizer to provide stop valves, and these stop valves are switched according to the operating state of the unit. A smooth start-up can be realized during warm-up start-up.
【0025】請求項6において、高圧節炭器は高圧一次
節炭器と高圧二次節炭器とを備え、高圧一次節炭器を排
ガスに対して低圧節炭器と並列に配置したことにより、
高圧一次節炭器と低圧節炭器における収熱効率を上昇さ
せることができる。
In claim 6, the high-pressure economizer comprises a high-pressure primary economizer and a high-pressure secondary economizer, and the high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to the exhaust gas.
The heat collection efficiency in the high-pressure primary economizer and the low-pressure economizer can be increased.
【0026】請求項7においては、高圧節炭器および低
圧節炭器の上流側で、且つ復水ポンプの下流側の復水管
に給水ポンプを設け、この給水ポンプの吐出水を高圧節
炭器を通して高圧ドラムへ送水する一方、給水ポンプの
中間段の抽水を低圧節炭器を通して低圧ドラムへ送水し
たことにより、給水ポンプに過大な熱衝撃を与えること
なく、給水ポンプの劣化を防止することができる。
According to a seventh aspect of the present invention, a water supply pump is provided in the condensate pipe upstream of the high pressure economizer and the low pressure economizer and downstream of the condensate pump, and the discharge water of the water supply pump is supplied to the high pressure economizer. Water is sent to the high-pressure drum through the low-pressure economizer while water is being sent to the low-pressure drum through the low-pressure economizer, while preventing the water-supply pump from deteriorating without giving an excessive thermal shock. it can.
【0027】請求項8において、低圧節炭器の出口の最
適温度箇所には分岐管が設けられ、この分岐管を経て給
水ポンプ上流側の復水管へ低圧給水の一部を再循環させ
たことにより、低圧節炭器および高圧節炭器における低
温腐食を防止することができる。
In claim 8, a branch pipe is provided at an optimum temperature location at the outlet of the low-pressure economizer, and a part of the low-pressure feed water is recirculated to the condensate pipe on the upstream side of the water feed pump through the branch pipe. Thereby, low temperature corrosion in the low pressure economizer and the high pressure economizer can be prevented.
【0028】請求項9において、再循環させる管路に
は、再循環水の量を調整して給水ポンプ入口の給水温度
を一定に制御する手段を設けたことにより、低圧節炭器
および高圧節炭器の入口給水温度が常に一定に維持され
る。
In the ninth aspect of the present invention, the recirculation pipe is provided with means for adjusting the amount of recirculated water to control the feed water temperature at the inlet of the feed water pump at a constant level. The inlet water temperature of the coal heater is always kept constant.
【0029】請求項10において、高圧節炭器は高圧一
次節炭器と高圧二次節炭器とを備え、高圧一次節炭器を
排ガスに対して低圧節炭器と並列に配置したことによ
り、高圧一次節炭器と低圧節炭器における収熱効率を上
昇させることができる。
In the tenth aspect, the high-pressure economizer includes a high-pressure primary economizer and a high-pressure secondary economizer, and the high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to exhaust gas. The heat collection efficiency in the high-pressure primary economizer and the low-pressure economizer can be increased.
【0030】[0030]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。
Embodiments of the present invention will be described below with reference to the drawings.
【0031】図1は本発明に係る複圧式排熱回収ボイラ
給水装置の第1実施例を示す系統図である。なお、従来
の構成と同一または対応する部分には同一の符号を用い
て説明する。図1において、複圧式排熱回収ボイラ1内
には、高圧蒸気過熱器11、高圧蒸発器12、高圧二次
節炭器13a、低圧蒸発器14、低圧節炭器15および
高圧一次節炭器18が排ガスの下流側に向かって配設さ
れる。
FIG. 1 is a system diagram showing a first embodiment of a compound pressure type exhaust heat recovery boiler water supply system according to the present invention. Note that the same or corresponding portions as those of the conventional configuration will be described using the same reference numerals. In FIG. 1, a high pressure steam superheater 11, a high pressure evaporator 12, a high pressure secondary economizer 13a, a low pressure evaporator 14, a low pressure economizer 15, and a high pressure primary economizer 18 are provided in the double pressure type exhaust heat recovery boiler 1. Are arranged toward the downstream side of the exhaust gas.
【0032】また、高圧蒸発器12は高圧ドラム16
と、低圧蒸発器14は低圧ドラム17とそれぞれ連結さ
れ、低圧給水ポンプ31により昇圧された低圧給水は、
低圧給水ポンプ出口逆止弁42、低圧給水管32を経て
低圧節炭器15で昇温された後、低圧蒸発器14で発生
した低圧蒸気を低圧ドラム17を経て低圧主蒸気管22
に案内し、蒸気タービン23の低圧側に案内するように
なっている。
The high-pressure evaporator 12 is a high-pressure drum 16
The low-pressure evaporator 14 is connected to the low-pressure drum 17, and the low-pressure water supplied to the low-pressure water supply pump 31 is
After being heated in the low-pressure economizer 15 via the low-pressure feed pump outlet check valve 42 and the low-pressure feed pipe 32, the low-pressure steam generated in the low-pressure evaporator 14 is passed through the low-pressure drum 17 and the low-pressure main steam pipe 22.
To the low pressure side of the steam turbine 23.
【0033】一方、高圧給水は低圧給水ポンプ出口逆止
弁42の下流側で、且つ低圧節炭器15の上流側の低圧
給水管32から分岐した管路を通り高圧給水ポンプ33
に案内され、この高圧給水ポンプ33から高圧給水流量
計41を接続した高圧給水管34を通り高圧一次節炭器
18に案内される。
On the other hand, the high-pressure feed water passes through a pipe branching from the low-pressure feed pipe 32 downstream of the low-pressure feed pump outlet check valve 42 and upstream of the low-pressure economizer 15, and the high-pressure feed pump 33.
And is guided from the high-pressure water supply pump 33 to the high-pressure primary economizer 18 through the high-pressure water supply pipe 34 connected to the high-pressure water supply flow meter 41.
【0034】さらに、この高圧一次節炭器18で昇温さ
れた給水は、高圧給水管34を通り高圧二次節炭器13
aで一段と昇温されて高圧ドラム16に案内される。こ
の高圧ドラム16から蒸気化しない給水は高圧蒸発器1
2に案内され、ここで蒸気化され、高圧蒸気となる。こ
の高圧蒸気は高圧ドラム16を経て高圧蒸気過熱器11
に送られ、ここで過熱され、高温高圧の乾き蒸気とさ
れ、この高圧蒸気が高圧蒸気管21を通して蒸気タービ
ン23の高圧側に供給される。
Further, the feed water heated by the high pressure primary economizer 18 passes through the high pressure water supply pipe 34 and the high pressure secondary economizer 13
The temperature is further raised at a and is guided to the high-pressure drum 16. The feed water that is not vaporized from the high-pressure drum 16 is the high-pressure evaporator 1
It is guided to No. 2 where it is vaporized into high pressure steam. This high-pressure steam passes through the high-pressure drum 16 and the high-pressure steam superheater 11
Is sent to the high pressure side of the steam turbine 23 through the high pressure steam pipe 21.
【0035】そして、高圧蒸気管21および低圧主蒸気
管22を経て蒸気タービン23に供給された主蒸気は、
蒸気タービン23を回転駆動させて仕事をし、蒸気ター
ビン23に連結された発電機24を駆動させる。蒸気タ
ービン23で仕事をした蒸気は、復水器25に案内さ
れ、ここで凝縮液化される。
The main steam supplied to the steam turbine 23 through the high pressure steam pipe 21 and the low pressure main steam pipe 22 is
The steam turbine 23 is rotationally driven to perform work, and a generator 24 connected to the steam turbine 23 is driven. The steam that has worked in the steam turbine 23 is guided to the condenser 25 where it is condensed and liquefied.
【0036】また、低圧節炭器15および高圧一次節炭
器18における低温腐食を防止するためには、高圧一次
節炭器18の下流側の最適温度が得られる個所の高圧給
水管34から高圧給水の一部を分岐し、この給水を給水
再循環管35を経て低圧給水ポンプ出口逆止弁42の下
流側で、且つ高圧給水管34の分岐点上流側の低圧給水
管32へ循環させ、温度コントローラ37に基づいて開
度が制御される温度調節弁である給水再循環水調節弁3
6により、高圧一次節炭器18および低圧節炭器15の
入口給水温度を常に一定の温度(約50℃)に維持する
ように調節される。
In order to prevent low-temperature corrosion in the low-pressure economizer 15 and the high-pressure primary economizer 18, high-pressure water is supplied from the high-pressure feed pipe 34 at a location where the optimum temperature on the downstream side of the high-pressure primary economizer 18 can be obtained. A part of the water supply is branched, and this water supply is circulated through the water supply recirculation pipe 35 to the low pressure water supply pipe 32 on the downstream side of the low pressure water supply pump outlet check valve 42 and on the upstream side of the branch point of the high pressure water supply pipe 34, Water recirculation water control valve 3 which is a temperature control valve whose opening is controlled based on the temperature controller 37
6, the inlet feed water temperature of the high-pressure primary economizer 18 and the low-pressure economizer 15 is adjusted so as to always maintain a constant temperature (about 50 ° C.).
【0037】さらに、高圧一次節炭器18出口からの給
水は、高圧給水管34から分岐した給水再循環管35を
経て、高圧給水ポンプ33のミニマムフローを兼用した
ミニマムフロー管38を経て、さらに高圧一次節炭器出
口ミニマムフロー止め弁44、ミニマムフロー調節弁3
9を経て復水器25へ回収することにより、給水量が必
要再循環量を確保できるようにしている。
Further, the water supply from the outlet of the high-pressure primary economizer 18 passes through a water supply recirculation pipe 35 branched from the high-pressure water supply pipe 34, a minimum flow pipe 38 which also serves as a minimum flow of the high-pressure water supply pump 33, and further, High pressure primary economizer outlet minimum flow stop valve 44, minimum flow control valve 3
By recovering the water to the condenser 25 after passing through 9, the amount of water supply can ensure the required amount of recirculation.
【0038】そして、高圧給水ポンプ33出口で且つ高
圧一次節炭器18入口の高圧給水管34は、高圧給水ポ
ンプミニマムフロー管46が分岐され、このミニマムフ
ロー管46が高圧一次節炭器入口ミニマムフロー止め弁
45を介してミニマムフロー調節弁39の上流側へ接続
されている。
The high pressure water supply pipe 33 at the outlet of the high pressure water supply pump 33 and at the inlet of the high pressure primary coal economizer 18 is branched from a high pressure water supply pump minimum flow pipe 46. It is connected to the upstream side of the minimum flow control valve 39 via the flow stop valve 45.
【0039】したがって、ユニットの暖機起動時のみ、
高圧一次節炭器出口ミニマムフロー止め弁44を閉じ、
高圧一次節炭器入口ミニマムフロー止め弁45を開にす
ることにより、暖機起動時において高圧一次節炭器18
内に滞留している高温水を復水器25からの冷水に置換
することがなくなり、これにより円滑な起動が実現可能
となる。なお、ミニマムフロー調節弁39の開度は、高
圧給水流量計41の測定結果を流量コントローラ40に
出力することにより制御される。
Therefore, only when the unit is warmed up and started,
Close the high pressure primary economizer outlet minimum flow stop valve 44,
By opening the high-pressure primary economizer inlet minimum flow stop valve 45, the high-pressure primary economizer 18 is activated during warm-up startup.
The high-temperature water staying inside is not replaced with the cold water from the condenser 25, whereby smooth startup can be realized. The opening of the minimum flow control valve 39 is controlled by outputting the measurement result of the high pressure feed water flow meter 41 to the flow rate controller 40.
【0040】次に、本実施例の作用を説明する。Next, the operation of this embodiment will be described.
【0041】高圧節炭器は、高圧一次節炭器18と高圧
二次節炭器13aとに分割され、高圧一次節炭器18を
排ガスに対して低圧節炭器15と並列に配置することに
より、高圧一次節炭器18と低圧節炭器15における収
熱効率を上昇させることができるとともに、給水再循環
水の最適な温度を選定できる。
The high pressure economizer is divided into a high pressure primary economizer 18 and a high pressure secondary economizer 13a. By disposing the high pressure primary economizer 18 in parallel with the low pressure economizer 15 with respect to the exhaust gas. The heat collection efficiency in the high pressure primary economizer 18 and the low pressure economizer 15 can be increased, and the optimum temperature of the feed water recirculation water can be selected.
【0042】ところで、高圧一次節炭器18内を通過す
る給水量は、必要再循環量により大きく変化するため、
再循環量が少量の場合は高圧一次節炭器18における熱
回収率が低下し、下流側の排ガス温度が上昇するため、
下流側に位置する煙道、煙突等の設計温度を高く設定す
る必要があり、また高温ガスを大気へ放出することによ
る環境への悪影響を引き起こす。
By the way, since the amount of water supplied through the high-pressure primary economizer 18 greatly changes depending on the required recirculation amount,
When the recirculation amount is small, the heat recovery rate in the high-pressure primary economizer 18 decreases, and the exhaust gas temperature on the downstream side rises.
It is necessary to set the design temperature of the flue, chimney, etc. located on the downstream side to a high temperature, and the high temperature gas is released into the atmosphere, which causes an adverse effect on the environment.
【0043】そこで、本実施例では高圧一次節炭器18
を通過する給水量を最小限確保するため、高圧一次節炭
器18出口からの給水を高圧給水管34、給水再循環管
35、ミニマムフロー管38、高圧一次節炭器出口ミニ
マムフロー止め弁44、そしてミニマムフロー調節弁3
9を経て復水器25へ回収することにより、給水量が必
要再循環量を確保できるようにしている。
Therefore, in this embodiment, the high pressure primary economizer 18 is used.
In order to secure the minimum amount of water passing through the high-pressure primary coal economizer 18, the high-pressure primary coal economizer 18 has a high-pressure water supply pipe 34, a water supply recirculation pipe 35, a minimum flow pipe 38, a high-pressure primary economizer outlet minimum flow stop valve 44. , And minimum flow control valve 3
By recovering the water to the condenser 25 after passing through 9, the amount of water supply can ensure the required amount of recirculation.
【0044】さらに、ユニットの暖気起動時のみ高圧一
次節炭器出口ミニマムフロー止め弁44を閉じ、高圧一
次節炭器入口ミニマムフロー止め弁45を開にすること
により、暖気起動時において高圧一次節炭器18内に滞
留している高温水を復水器25からの冷水に置換するこ
となく、円滑な起動が実現可能となる。
Further, by closing the high pressure primary economizer outlet minimum flow stop valve 44 and opening the high pressure primary economizer inlet minimum flow stop valve 45 only when the unit is warmed up, the high pressure primary coalescer is opened at warm air startup. A smooth start-up can be realized without replacing the high temperature water staying in the charcoal unit 18 with the cold water from the condenser 25.
【0045】そして、暖気起動時以外の運転状態では、
常に高圧一次節炭器入口ミニマムフロー止め弁45を
閉、高圧一次節炭器出口ミニマムフロー止め弁44を開
にしておくことにより、同様の効果が得られる。
Then, in an operating state other than the warm-up start-up,
The same effect can be obtained by always closing the high pressure primary coal economizer inlet minimum flow stop valve 45 and keeping the high pressure primary coal economizer outlet minimum flow stop valve 44 open.
【0046】このように本実施例によれば、高圧給水ポ
ンプ33へ流入する給水温度は、常に一定の温度(約5
0℃)に維持され、且つ起動時においても温度調節弁で
ある給水再循環水調節弁36の開度を調整することによ
り、温度上昇率を制御できるので、高圧給水ポンプ33
に過大な熱衝撃を与えることなく、信頼性の高い複圧式
排熱回収ボイラ給水装置を提供することができる。
As described above, according to this embodiment, the temperature of the feed water flowing into the high pressure feed pump 33 is always a constant temperature (about 5).
(0 ° C.) and the temperature rise rate can be controlled by adjusting the opening of the feed water recirculation water control valve 36, which is a temperature control valve even at the time of startup, so the high pressure feed pump 33
It is possible to provide a highly reliable double pressure type exhaust heat recovery boiler water supply device without giving an excessive thermal shock to the.
【0047】図2は本発明に係る複圧式排熱回収ボイラ
給水装置の第2実施例を示す系統図である。なお、既に
説明した第1実施例と同一の部分には同一の符号を付し
て説明する。以下の各実施例についても同様である。
FIG. 2 is a system diagram showing a second embodiment of the compound pressure type exhaust heat recovery boiler water supply system according to the present invention. The same parts as those of the first embodiment described above will be designated by the same reference numerals. The same applies to each of the following examples.
【0048】低圧給水ポンプ31により昇圧された低圧
給水は、低圧給水ポンプ出口逆止弁42、低圧給水流量
計41および低圧節炭器15を介して低圧ドラム17へ
送水される。
The low-pressure feed water whose pressure has been raised by the low-pressure feed pump 31 is sent to the low-pressure drum 17 via the low-pressure feed pump outlet check valve 42, the low-pressure feed water flow meter 41 and the low-pressure economizer 15.
【0049】一方、高圧給水は低圧給水ポンプ出口逆止
弁42の下流側で、且つ低圧節炭器15の上流側の低圧
給水管32から分岐し、高圧給水ポンプ33、高圧一次
節炭器18を介して高圧給水管34を通り、さらに高圧
二次節炭器13aを介して高圧ドラム16へ送水され
る。
On the other hand, the high-pressure feed water is branched from the low-pressure feed pipe 32 on the downstream side of the low-pressure feed pump outlet check valve 42 and on the upstream side of the low-pressure economizer 15, and the high-pressure feed pump 33 and the high-pressure primary economizer 18 are connected. Through the high pressure water supply pipe 34, and further to the high pressure drum 16 via the high pressure secondary economizer 13a.
【0050】また、低圧節炭器15および高圧一次節炭
器18における低温腐食を防止するためには、低圧節炭
器15の下流側の低圧給水管32から低圧給水の一部を
分岐し、給水再循環ポンプ43が接続された給水再循環
管35を通して低圧給水ポンプ出口逆止弁42の下流側
で、且つ高圧給水管34との分岐点上流側の低圧給水管
32へ循環させることで、給水再循環水調節弁36によ
り高圧第一次節炭器18および低圧節炭器15の入口給
水温度を常に一定の温度(約50℃)に保持するように
調節される。
In order to prevent low temperature corrosion in the low pressure economizer 15 and the high pressure primary economizer 18, a part of the low pressure feed water is branched from the low pressure feed pipe 32 on the downstream side of the low pressure economizer 15, By circulating through the water supply recirculation pipe 35 to which the water supply recirculation pump 43 is connected, to the low pressure water supply pipe 32 on the downstream side of the low pressure water supply pump outlet check valve 42 and on the upstream side of the branch point with the high pressure water supply pipe 34, The feed water recirculation water control valve 36 adjusts the inlet feed water temperature of the high pressure primary economizer 18 and the low pressure economizer 15 so as to always maintain a constant temperature (about 50 ° C.).
【0051】さらに、排熱回収ボイラ1出口の排ガス温
度上昇を防止するためには、給水再循環ポンプ43出口
の給水再循環管35からミニマムフロー管38を分岐
し、ミニマムフロー調節弁39を介して復水器25と接
続することにより、低圧節炭器15の必要最低流量およ
び給水再循環ポンプ43のミニマムフローを確保するこ
とができる。
Further, in order to prevent the exhaust gas temperature at the outlet of the exhaust heat recovery boiler 1 from rising, a minimum flow pipe 38 is branched from the feed water recirculation pipe 35 at the outlet of the feed water recirculation pump 43, and a minimum flow control valve 39 is provided. By connecting the condenser 25 with the condenser 25, the required minimum flow rate of the low pressure economizer 15 and the minimum flow of the feed water recirculation pump 43 can be secured.
【0052】なお、本実施例でも前記実施例と同様に、
高圧一次節炭器18は排ガスに対して低圧節炭器15と
並列に配置する。その他の構成および作用は前記実施例
と同一であるのでその説明を省略する。
In this embodiment, as in the above embodiment,
The high-pressure primary economizer 18 is arranged in parallel with the low-pressure economizer 15 for the exhaust gas. The other structure and operation are the same as those of the above-mentioned embodiment, and the explanation thereof is omitted.
【0053】図3は本発明に係る複圧式排熱回収ボイラ
給水装置の第3実施例を示す系統図である。本実施例で
は、高圧一次節炭器18および低圧節炭器15の上流側
であって、且つ復水ポンプ50の下流側の復水管51に
給水ポンプ52が設けられている。
FIG. 3 is a system diagram showing a third embodiment of the compound pressure type exhaust heat recovery boiler water supply system according to the present invention. In the present embodiment, a water supply pump 52 is provided in the condensate pipe 51 upstream of the high pressure primary economizer 18 and the low pressure economizer 15, and downstream of the condensate pump 50.
【0054】この給水ポンプ52の吐出水は、高圧給水
管34、高圧一次節炭器18、高圧給水管34、高圧二
次節炭器13aを通して高圧ドラム16へ送水する一
方、給水ポンプ52の中間段の抽水は、低圧給水管3
2、低圧節炭器15、低圧給水管32を通して低圧ドラ
ム17へ送水するようにしている。
The discharge water of the water supply pump 52 is sent to the high pressure drum 16 through the high pressure water supply pipe 34, the high pressure primary economizer 18, the high pressure water supply pipe 34, and the high pressure secondary economizer 13a, while the intermediate stage of the water supply pump 52. The low pressure water supply pipe 3
2. Water is supplied to the low-pressure drum 17 through the low-pressure economizer 15 and the low-pressure water supply pipe 32.
【0055】すなわち、復水ポンプ50により昇圧され
た復水は、復水逆止弁53、復水管51を経て給水ポン
プ52に送られ、さらに昇圧された後、給水ポンプ52
の吐出側から高圧給水管34を経て高圧一次節炭器18
へ案内される。
That is, the condensate water whose pressure has been increased by the condensate pump 50 is sent to the water supply pump 52 via the condensate check valve 53 and the condensate pipe 51, and after being further pressurized, the water supply pump 52.
From the discharge side of the high-pressure feed pipe 34 to the high-pressure primary economizer 18
Be guided to.
【0056】さらに、この高圧一次節炭器18で昇温さ
れた給水は、高圧給水管34を通り高圧二次節炭器13
aで一段と昇温されて高圧ドラム16に案内される。こ
の高圧ドラム16から蒸気化しない給水は高圧蒸発器1
2に案内され、ここで蒸気化され、高圧蒸気となる。こ
の高圧蒸気は高圧ドラム16を経て高圧蒸気過熱器11
に送られ、ここで過熱され、高温高圧の乾き蒸気とさ
れ、この高圧蒸気が高圧蒸気管21を通して蒸気タービ
ン23の高圧側に供給される。
Further, the feed water heated by the high pressure primary economizer 18 passes through the high pressure water supply pipe 34 and the high pressure secondary economizer 13
The temperature is further raised at a and is guided to the high-pressure drum 16. The feed water that is not vaporized from the high-pressure drum 16 is the high-pressure evaporator 1
It is guided to No. 2 where it is vaporized into high pressure steam. This high-pressure steam passes through the high-pressure drum 16 and the high-pressure steam superheater 11
Is sent to the high pressure side of the steam turbine 23 through the high pressure steam pipe 21.
【0057】一方、給水ポンプ52の中間段から抽水さ
れた低圧給水は、低圧給水管32を経て低圧節炭器15
で昇温された後、低圧ドラム17へ案内される。この低
圧ドラム17に連結された低圧蒸発器14で発生した低
圧蒸気は、低圧主蒸気管22から蒸気タービン23の低
圧側に供給される。
On the other hand, the low-pressure feed water extracted from the intermediate stage of the feed water pump 52 passes through the low-pressure feed pipe 32 and the low-pressure economizer 15
After the temperature is raised by, it is guided to the low-pressure drum 17. The low-pressure steam generated in the low-pressure evaporator 14 connected to the low-pressure drum 17 is supplied from the low-pressure main steam pipe 22 to the low-pressure side of the steam turbine 23.
【0058】そして、高圧蒸気管21および低圧主蒸気
管22を経て蒸気タービン23に供給された主蒸気は、
前記第1実施例と同様に蒸気タービン23を回転駆動さ
せて仕事をし、蒸気タービン23に連結された発電機2
4を駆動させる。蒸気タービン23で仕事をした蒸気
は、復水器25に案内され、ここで凝縮液化される。
The main steam supplied to the steam turbine 23 through the high pressure steam pipe 21 and the low pressure main steam pipe 22 is
As in the case of the first embodiment, the steam turbine 23 is driven to rotate to perform work, and the generator 2 connected to the steam turbine 23.
4 is driven. The steam that has worked in the steam turbine 23 is guided to the condenser 25 where it is condensed and liquefied.
【0059】また、低圧節炭器15および高圧一次節炭
器18における低温腐食を防止するためには、低圧節炭
器15の下流側の低圧給水管32から低圧給水の一部を
分岐し、この給水を給水再循環管35を経て復水逆止弁
53の下流側の復水管51へ循環させ、温度コントロー
ラ37に基づいて開度が制御される温度調節弁である給
水再循環水調節弁36により、高圧一次節炭器18およ
び低圧節炭器15の入口給水温度を常に一定の温度(約
50℃)に維持するように調節される。
In order to prevent low temperature corrosion in the low pressure economizer 15 and the high pressure primary economizer 18, a part of the low pressure feed water is branched from the low pressure feed pipe 32 on the downstream side of the low pressure economizer 15, This feed water is circulated through the feed water recirculation pipe 35 to the condensate pipe 51 on the downstream side of the condensate check valve 53, and the feed water recirculation water control valve which is a temperature control valve whose opening is controlled based on the temperature controller 37. The inlet water temperature of the high-pressure primary economizer 18 and the low-pressure economizer 15 is adjusted by 36 so as to always maintain a constant temperature (about 50 ° C.).
【0060】次に、本実施例の作用を説明する。Next, the operation of this embodiment will be described.
【0061】高圧節炭器は、高圧一次節炭器18と高圧
二次節炭器13aとに分割され、高圧一次節炭器18を
排ガスに対して低圧節炭器15と並列に配置することに
より、高圧一次節炭器18と低圧節炭器15における収
熱効率を上昇させることができる。
The high pressure economizer is divided into a high pressure primary economizer 18 and a high pressure secondary economizer 13a. By disposing the high pressure primary economizer 18 in parallel with the low pressure economizer 15 with respect to the exhaust gas. The heat collection efficiency in the high pressure primary economizer 18 and the low pressure economizer 15 can be increased.
【0062】また、本実施例によれば、給水ポンプ52
へ流入する給水温度は、常に一定の温度(約50℃)に
維持され、且つ起動時においても温度調節弁である給水
再循環水調節弁36の開度を調整することにより、温度
上昇率を制御できるので、給水ポンプ52に過大な熱衝
撃を与えることなく、信頼性の高い複圧式排熱回収ボイ
ラ給水装置を提供することができる。
Further, according to this embodiment, the water supply pump 52
The temperature of the feed water flowing into is constantly maintained at a constant temperature (about 50 ° C.), and the rate of temperature rise is controlled by adjusting the opening degree of the feed water recirculation water control valve 36, which is a temperature control valve even at the time of startup. Since it can be controlled, it is possible to provide a highly reliable double pressure type exhaust heat recovery boiler water supply apparatus without giving an excessive thermal shock to the water supply pump 52.
【0063】[0063]
【発明の効果】以上説明したように、本発明の請求項1
によれば、低圧節炭器の上流側の低圧給水管から高圧給
水管を分岐し、この高圧給水管に接続した高圧給水ポン
プを介して高圧節炭器へ送水したことにより、高圧給水
ポンプに過大な熱衝撃を与えることなく、高圧給水ポン
プの劣化を防止することができ、装置としての信頼性を
大幅に向上させることができる。
As described above, according to the first aspect of the present invention.
According to the above, the high-pressure water supply pipe is branched from the low-pressure water supply pipe on the upstream side of the low-pressure economizer, and the high-pressure water pump is connected to the high-pressure water pipe to supply water to the high-pressure economizer, thereby It is possible to prevent deterioration of the high-pressure water supply pump without giving an excessive thermal shock, and to greatly improve the reliability of the device.
【0064】請求項2によれば、高圧節炭器の出口の最
適温度箇所には分岐管が設けられ、この分岐管を経て高
圧給水管分岐点上流側の低圧給水管へ高圧給水の一部を
再循環させることにより、低圧節炭器および高圧節炭器
における低温腐食を防止することができ、長寿命化を図
ることができる。
According to the second aspect, a branch pipe is provided at the optimum temperature location at the outlet of the high-pressure economizer, and a part of the high-pressure feed water is supplied to the low-pressure feed pipe upstream of the branch point of the high-pressure water feed pipe through this branch pipe. By recirculating, it is possible to prevent low-temperature corrosion in the low-pressure economizer and the high-pressure economizer, and to extend the service life.
【0065】請求項3によれば、低圧節炭器出口には分
岐管が設けられ、この分岐管に接続された給水再循環ポ
ンプを介して高圧給水管分岐点上流側の低圧給水管へ低
圧給水の一部を再循環させたことにより、低圧節炭器お
よび高圧節炭器における低温腐食を防止することがで
き、長寿命化を図ることができる。
According to the third aspect, a branch pipe is provided at the outlet of the low-pressure economizer, and a low pressure is supplied to the low-pressure feed pipe upstream of the branch point of the high-pressure feed pipe via the feed water recirculation pump connected to this branch pipe. By recirculating a part of the feed water, it is possible to prevent low temperature corrosion in the low pressure economizer and the high pressure economizer, and it is possible to extend the service life.
【0066】請求項4によれば、再循環させる管路に
は、高圧給水および低圧給水の量を調整して高圧節炭器
および低圧節炭器入口の給水温度を一定に制御する手段
を設けたことにより、低圧節炭器および高圧節炭器の入
口給水温度が常に一定に維持される。
According to the fourth aspect, the recirculation pipe is provided with means for adjusting the amounts of the high pressure feed water and the low pressure feed water to control the feed water temperatures at the high pressure economizer and the low pressure economizer inlet to be constant. As a result, the inlet feed water temperature of the low-pressure economizer and the high-pressure economizer is always kept constant.
【0067】請求項5によれば、高圧給水ポンプは、そ
のミニマムフロー管を高圧節炭器入口および出口よりそ
れぞれ分岐して止め弁を設け、これらの止め弁をユニッ
トの運転状態に応じて切り換えることにより、暖機起動
時において円滑な起動が実現可能となる。
According to the fifth aspect of the present invention, in the high-pressure feed pump, the minimum flow pipes are branched from the inlet and the outlet of the high-pressure economizer to provide stop valves, and these stop valves are switched according to the operating state of the unit. As a result, a smooth start-up can be realized during warm-up start-up.
【0068】請求項6によれば、高圧節炭器は高圧一次
節炭器と高圧二次節炭器とを備え、蒸気高圧一次節炭器
を排ガスに対して低圧節炭器と並列に配置したことによ
り、高圧一次節炭器と低圧節炭器における収熱効率を上
昇させることができる。
According to claim 6, the high pressure economizer comprises a high pressure primary economizer and a high pressure secondary economizer, and the steam high pressure primary economizer is arranged in parallel with the low pressure economizer with respect to the exhaust gas. As a result, the heat collection efficiency in the high-pressure primary economizer and the low-pressure economizer can be increased.
【0069】請求項7によれば、高圧節炭器および低圧
節炭器の上流側に給水ポンプを配置したことにより、給
水ポンプの劣化を防止することができ、装置としての信
頼性を大幅に向上させることができるとともに、低圧給
水を給水ポンプの中間段から抽水することにより、給水
再循環として最適な圧力を有する給水を提供することが
できる。
According to the seventh aspect, by disposing the water supply pump on the upstream side of the high pressure economizer and the low pressure economizer, it is possible to prevent the deterioration of the water supply pump and to greatly improve the reliability of the apparatus. In addition to being able to improve, it is possible to provide water supply having an optimum pressure for water supply recirculation by extracting low-pressure water supply from the intermediate stage of the water supply pump.
【0070】請求項8によれば、低圧節炭器の出口の最
適温度箇所には分岐管が設けられ、この分岐管を経て給
水ポンプ上流側の復水管へ低圧給水の一部を再循環させ
たことにより、低圧節炭器および高圧節炭器における低
温腐食を防止することができ、長寿命化を図ることがで
きる。
According to claim 8, a branch pipe is provided at the optimum temperature location at the outlet of the low pressure economizer, and a part of the low pressure feed water is recirculated to the condensate pipe on the upstream side of the water feed pump through this branch pipe. As a result, it is possible to prevent low-temperature corrosion in the low-pressure economizer and the high-pressure economizer, and to extend the service life.
【0071】請求項9によれば、再循環させる管路に
は、再循環水の量を調整して給水ポンプ入口の給水温度
を一定に制御する手段を設けたことにより、給水ポンプ
に過大な熱衝撃を与えることがなくなる。
According to the ninth aspect of the present invention, the recirculation pipe is provided with means for adjusting the amount of recirculated water to control the feed water temperature at the inlet of the feed water pump at a constant level. No more thermal shock.
【0072】請求項10によれば、高圧節炭器は高圧一
次節炭器と高圧二次節炭器とを備え、高圧一次節炭器を
排ガスに対して低圧節炭器と並列に配置したことによ
り、高圧一次節炭器と低圧節炭器における収熱効率を上
昇させることができる。
According to claim 10, the high-pressure economizer comprises a high-pressure primary economizer and a high-pressure secondary economizer, and the high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to exhaust gas. As a result, the heat collection efficiency in the high-pressure primary economizer and the low-pressure economizer can be increased.
【図面の簡単な説明】[Brief description of drawings]
【図1】本発明に係る複圧式排熱回収ボイラ給水装置の
第1実施例を示す系統図。
FIG. 1 is a system diagram showing a first embodiment of a compound pressure type exhaust heat recovery boiler water supply device according to the present invention.
【図2】本発明に係る複圧式排熱回収ボイラ給水装置の
第2実施例を示す系統図。
FIG. 2 is a system diagram showing a second embodiment of the compound pressure type exhaust heat recovery boiler water supply device according to the present invention.
【図3】本発明に係る複圧式排熱回収ボイラ給水装置の
第3実施例を示す系統図。
FIG. 3 is a system diagram showing a third embodiment of a multi-pressure type exhaust heat recovery boiler water supply device according to the present invention.
【図4】従来の複圧式排熱回収ボイラ給水装置を示す系
統図。
FIG. 4 is a system diagram showing a conventional double pressure type exhaust heat recovery boiler water supply device.
【符号の説明】[Explanation of symbols]
1 複圧式排熱回収ボイラ 11 高圧蒸気過熱器 12 高圧蒸発器 13a 高圧二次節炭器 14 低圧蒸発器 15 低圧節炭器 16 高圧ドラム 17 低圧ドラム 18 高圧一次節炭器 31 低圧給水ポンプ 32 低圧給水管 33 高圧給水ポンプ 34 高圧給水管 35 給水再循環管 36 給水再循環水調節弁 37 温度コントローラ 38 ミニマムフロー管 39 ミニマムフロー調節弁 40 流量コントローラ 41 高圧給水流量計 42 低圧給水ポンプ出口逆止弁 43 給水再循環ポンプ 44 高圧一次節炭器出口ミニマムフロー止め弁 45 高圧一次節炭器入口ミニマムフロー止め弁 46 高圧給水ポンプミニマムフロー管 50 復水ポンプ 51 復水管 52 給水ポンプ 53 復水逆止弁 1 Double Pressure Type Exhaust Heat Recovery Boiler 11 High Pressure Steam Superheater 12 High Pressure Evaporator 13a High Pressure Secondary Economizer 14 Low Pressure Evaporator 15 Low Pressure Economizer 16 High Pressure Drum 17 Low Pressure Drum 18 High Pressure Primary Economizer 31 Low Pressure Water Pump 32 Low Pressure Water Supply Pipe 33 High pressure water supply pump 34 High pressure water supply pipe 35 Water supply recirculation pipe 36 Water supply recirculation water control valve 37 Temperature controller 38 Minimum flow pipe 39 Minimum flow control valve 40 Flow controller 41 High pressure water supply flow meter 42 Low pressure water supply pump outlet check valve 43 Water supply recirculation pump 44 High pressure primary economizer outlet minimum flow stop valve 45 High pressure primary economizer inlet minimum flow stop valve 46 High pressure water supply pump minimum flow pipe 50 Condensate pump 51 Condensate pipe 52 Water supply pump 53 Condensate check valve
───────────────────────────────────────────────────── フロントページの続き (72)発明者 山田 実 神奈川県横浜市鶴見区末広町2の4 株式 会社東芝京浜事業所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Minoru Yamada 4-4, 2 Suehiro-cho, Tsurumi-ku, Yokohama-shi, Kanagawa Toshiba Keihin Office

Claims (10)

    【特許請求の範囲】[Claims]
  1. 【請求項1】 高圧蒸発器および低圧蒸発器にそれぞれ
    高圧ドラムおよび低圧ドラムを連結し、これらのドラム
    にそれぞれ高圧節炭器および低圧節炭器を介して給水を
    供給する複圧式排熱回収ボイラ給水装置において、上記
    低圧節炭器の上流側の低圧給水管から高圧給水管を分岐
    し、この高圧給水管に接続した高圧給水ポンプを介して
    上記高圧節炭器へ送水したことを特徴とする複圧式排熱
    回収ボイラ給水装置。
    1. A double-pressure exhaust heat recovery boiler in which a high-pressure drum and a low-pressure evaporator are connected to a high-pressure drum and a low-pressure drum, respectively, and water is supplied to these drums via the high-pressure economizer and the low-pressure economizer, respectively. In the water supply device, a high-pressure water supply pipe is branched from a low-pressure water supply pipe on the upstream side of the low-pressure coal economizer, and water is supplied to the high-pressure economizer via a high-pressure water supply pump connected to the high-pressure water economizer. Compound pressure exhaust heat recovery boiler water supply device.
  2. 【請求項2】 高圧節炭器の出口の最適温度箇所には分
    岐管が設けられ、この分岐管を経て高圧給水管分岐点上
    流側の低圧給水管へ高圧給水の一部を再循環させたこと
    を特徴とする請求項1記載の複圧式排熱回収ボイラ給水
    装置。
    2. A branch pipe is provided at an optimum temperature location at the outlet of the high-pressure economizer, and a part of the high-pressure feed water is recirculated to the low-pressure feed pipe upstream of the branch point of the high-pressure water feed pipe through this branch pipe. The double pressure type exhaust heat recovery boiler water supply apparatus according to claim 1, wherein
  3. 【請求項3】 低圧節炭器出口には分岐管が設けられ、
    この分岐管に接続された給水再循環ポンプを介して高圧
    給水管分岐点上流側の低圧給水管へ低圧給水の一部を再
    循環させたことを特徴とする請求項1記載の複圧式排熱
    回収ボイラ給水装置。
    3. A branch pipe is provided at the outlet of the low pressure economizer,
    2. The multi-pressure exhaust heat according to claim 1, wherein a part of the low-pressure feed water is recirculated to the low-pressure feed pipe upstream of the branch point of the high-pressure feed pipe through the feed water recirculation pump connected to this branch pipe. Recovery boiler water supply device.
  4. 【請求項4】 再循環させる管路には、高圧給水および
    低圧給水の量を調整して高圧節炭器および低圧節炭器入
    口の給水温度を一定に制御する手段を設けたことを特徴
    とする請求項2または3記載の複圧式排熱回収ボイラ給
    水装置。
    4. The recirculation pipe line is provided with means for adjusting the amounts of high-pressure feed water and low-pressure feed water to control the feed water temperature at the inlets of the high-pressure economizer and the low-pressure economizer at a constant level. The compound pressure exhaust heat recovery boiler water supply device according to claim 2 or 3.
  5. 【請求項5】 高圧給水ポンプは、そのミニマムフロー
    管を高圧節炭器入口および出口よりそれぞれ分岐して止
    め弁を設け、これらの止め弁をユニットの運転状態に応
    じて切り換えることを特徴とする請求項1記載の複圧式
    排熱回収ボイラ給水装置。
    5. The high-pressure feed pump is characterized in that minimum flow pipes are branched from an inlet and an outlet of the high-pressure economizer, respectively, to provide stop valves, and these stop valves are switched according to an operating state of the unit. The compound pressure exhaust heat recovery boiler water supply device according to claim 1.
  6. 【請求項6】 高圧節炭器は高圧一次節炭器と高圧二次
    節炭器とを備え、蒸気高圧一次節炭器を排ガスに対して
    低圧節炭器と並列に配置したことを特徴とする請求項
    1,2,4または5記載の複圧式排熱回収ボイラ給水装
    置。
    6. The high-pressure economizer comprises a high-pressure primary economizer and a high-pressure secondary economizer, and the steam high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to exhaust gas. The compound pressure type exhaust heat recovery boiler water supply device according to claim 1, 2, 4 or 5.
  7. 【請求項7】 高圧蒸発器および低圧蒸発器にそれぞれ
    高圧ドラムおよび低圧ドラムを連結し、これらのドラム
    にそれぞれ高圧節炭器および低圧節炭器を介して給水を
    供給する複圧式排熱回収ボイラ給水装置において、上記
    高圧節炭器および低圧節炭器の上流側で、且つ復水ポン
    プの下流側の復水管に給水ポンプを設け、この給水ポン
    プの吐出水を上記高圧節炭器を通して高圧ドラムへ送水
    する一方、上記給水ポンプの中間段の抽水を上記低圧節
    炭器を通して低圧ドラムへ送水したことを特徴とする複
    圧式排熱回収ボイラ給水装置。
    7. A high pressure evaporator and a low pressure evaporator are respectively connected to a high pressure drum and a low pressure drum, and a double pressure type exhaust heat recovery boiler for supplying water to these drums via the high pressure economizer and the low pressure economizer, respectively. In the water supply device, a water supply pump is provided in the condensate pipe on the upstream side of the high-pressure economizer and the low-pressure economizer and on the downstream side of the condensate pump, and the discharge water of the water supply pump is passed through the high-pressure economizer to the high-pressure drum. A double pressure exhaust heat recovery boiler water supply device, characterized in that, while water is being sent to the low pressure drum, the extracted water in the intermediate stage of the water supply pump is sent to the low pressure drum through the low pressure economizer.
  8. 【請求項8】 低圧節炭器の出口の最適温度箇所には分
    岐管が設けられ、この分岐管を経て給水ポンプ上流側の
    復水管へ低圧給水の一部を再循環させたことを特徴とす
    る請求項7記載の複圧式排熱回収ボイラ給水装置。
    8. A branch pipe is provided at an optimum temperature location at the outlet of the low-pressure economizer, and a part of the low-pressure feed water is recirculated to the condensate pipe on the upstream side of the feed pump via the branch pipe. The multi-pressure type exhaust heat recovery boiler water supply device according to claim 7.
  9. 【請求項9】 再循環させる管路には、再循環水の量を
    調整して給水ポンプ入口の給水温度を一定に制御する手
    段を設けたことを特徴とする請求項7または8記載の複
    圧式排熱回収ボイラ給水装置。
    9. The recirculation pipe line is provided with means for adjusting the amount of recirculation water to control the feed water temperature at the feed water pump inlet at a constant level. Pressure type exhaust heat recovery boiler water supply device.
  10. 【請求項10】 高圧節炭器は高圧一次節炭器と高圧二
    次節炭器とを備え、上記高圧一次節炭器を排ガスに対し
    て低圧節炭器と並列に配置したことを特徴とする請求項
    7,8または9記載の複圧式排熱回収ボイラ給水装置。
    10. The high-pressure economizer comprises a high-pressure primary economizer and a high-pressure secondary economizer, and the high-pressure primary economizer is arranged in parallel with the low-pressure economizer with respect to exhaust gas. The compound pressure type exhaust heat recovery boiler water supply device according to claim 7, 8 or 9.
JP6247861A 1993-10-22 1994-10-13 Double pressure type waste heat recovery boiler water supplying apparatus Pending JPH07167401A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP26482293 1993-10-22
JP5-264822 1993-10-22
JP6247861A JPH07167401A (en) 1993-10-22 1994-10-13 Double pressure type waste heat recovery boiler water supplying apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6247861A JPH07167401A (en) 1993-10-22 1994-10-13 Double pressure type waste heat recovery boiler water supplying apparatus

Publications (1)

Publication Number Publication Date
JPH07167401A true JPH07167401A (en) 1995-07-04

Family

ID=26538459

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6247861A Pending JPH07167401A (en) 1993-10-22 1994-10-13 Double pressure type waste heat recovery boiler water supplying apparatus

Country Status (1)

Country Link
JP (1) JPH07167401A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100338424C (en) * 2004-09-30 2007-09-19 中信重型机械公司 Generating set system of simple low temperature waste heat from large size cement manufacture line in dry method, and technical process
JP2011196646A (en) * 2010-03-23 2011-10-06 Shin Kurushima Dockyard Co Ltd Exhaust gas economizer circulating water system
CN103353102A (en) * 2013-07-22 2013-10-16 清华大学 Device capable of exchanging heat with high-temperature high-pressure gas
CN103353100A (en) * 2013-07-22 2013-10-16 清华大学 Straight-flow type heat exchanging device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100338424C (en) * 2004-09-30 2007-09-19 中信重型机械公司 Generating set system of simple low temperature waste heat from large size cement manufacture line in dry method, and technical process
JP2011196646A (en) * 2010-03-23 2011-10-06 Shin Kurushima Dockyard Co Ltd Exhaust gas economizer circulating water system
CN103353102A (en) * 2013-07-22 2013-10-16 清华大学 Device capable of exchanging heat with high-temperature high-pressure gas
CN103353100A (en) * 2013-07-22 2013-10-16 清华大学 Straight-flow type heat exchanging device

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