JPH0684801B2 - Supercritical pressure transformer type boiler - Google Patents
Supercritical pressure transformer type boilerInfo
- Publication number
- JPH0684801B2 JPH0684801B2 JP60271370A JP27137085A JPH0684801B2 JP H0684801 B2 JPH0684801 B2 JP H0684801B2 JP 60271370 A JP60271370 A JP 60271370A JP 27137085 A JP27137085 A JP 27137085A JP H0684801 B2 JPH0684801 B2 JP H0684801B2
- Authority
- JP
- Japan
- Prior art keywords
- bypass
- boiler
- pressure
- flue
- supercritical
- 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.)
- Expired - Fee Related
Links
Landscapes
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、超臨界変圧運転形ボイラに関し、更に詳細に
は、この種ボイラにおいて水と蒸気の系統の圧力損失を
低減させる技術の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a supercritical variable pressure operation type boiler, and more particularly to improvement of a technique for reducing pressure loss of a water and steam system in such a boiler.
従来の技術 従来の超臨界変圧運転形ボイラとして、第５図及び第６
図に示すような２つの給水バイパス方式のものがある。2. Description of the Related Art As a conventional supercritical transformer operation type boiler, FIGS.
There are two types of water supply bypass system as shown in the figure.
すなわち、第５図に示すボイラにおいては、ボイラへの
給水は節炭器（図示せず）より火炉１、ウォータセパレ
ータ２、後部煙道周壁３及び過熱器4,5の順に流れるよ
うになっている。そして、このボイラは、後部煙道周壁
３が蒸気により冷却される方式のボイラであって、後部
煙道周壁３のバイパス管６のみが設けられ、弁を用いず
に圧力バランスのみでバイパスが行われる方式である。That is, in the boiler shown in FIG. 5, water is supplied to the boiler in the order of the furnace 1, the water separator 2, the rear flue peripheral wall 3, and the superheaters 4 and 5 from a economizer (not shown). There is. This boiler is a boiler in which the rear flue peripheral wall 3 is cooled by steam, only the bypass pipe 6 of the rear flue peripheral wall 3 is provided, and bypass is performed only by pressure balance without using a valve. It is a method that is used.
一方、第６図に示すボイラは、後部煙道周壁３が水冷壁
構造方式のボイラであって、後部煙道周壁３のバイパス
管６とバイパス弁７とが設けられ、これによりバイパス
量を調整するようにした方式である。On the other hand, in the boiler shown in FIG. 6, the rear flue peripheral wall 3 is a water cooling wall structure type boiler, and the bypass pipe 6 and the bypass valve 7 of the rear flue peripheral wall 3 are provided to adjust the bypass amount. This is the method that was adopted.
なお、第６図において、８は節炭器、９は循環ポンプで
あり、また1,2及び４は第５図と同様それぞれ火炉、ウ
ォータセパレータ及び過熱器である。In FIG. 6, 8 is a economizer, 9 is a circulation pump, and 1, 2 and 4 are a furnace, a water separator and a superheater, respectively, as in FIG.
しかして、第５図に示される方式のボイラにおいては、
バイパス量を積極的に調整しないので、ボイラの全負荷
帯にわたり系統内の圧力のバランスによってバイパスす
る蒸気が定まる。Then, in the boiler of the system shown in FIG. 5,
Since the bypass amount is not actively adjusted, the steam to be bypassed is determined by the pressure balance in the system over the entire load zone of the boiler.
一方、第６図に示される方式のボイラにおいては、バイ
パス弁によりバイパス量を調整することができる。そし
て、ボイラの低負荷時などにおいて、バイパスを行う
と、むしろ後部煙道周壁の管内を流れる流量が減少する
ため、流動不安定現象などを引起すおそれがある場合
に、バイパスさせないようにバイパス弁を閉止すること
ができる。On the other hand, in the boiler of the system shown in FIG. 6, the bypass amount can be adjusted by the bypass valve. When bypassing is performed when the boiler has a low load, the flow rate inside the pipe of the rear flue peripheral wall rather decreases, so if there is a risk of flow instability, a bypass valve should be used to prevent bypassing. Can be closed.
以上述べたように、第５図及び第６図に示した２つの方
式のボイラは、いずれも、後部煙道の周壁部分の圧力損
失を軽減せしめ、ポンプの動力を節減しようとするもの
である。As described above, each of the two types of boilers shown in FIGS. 5 and 6 is intended to reduce the pressure loss of the peripheral wall portion of the rear flue and to save the power of the pump. .
発明が解決しようとする課題 以上述べた従来例においては、しかし、次のような問題
があった。すなわち、第５図および第６図に示すボイラ
は、いずれも、後部煙道の周壁部分のみを給水バイパス
の対象としており、極くせまい範囲に限られたものであ
った。このため、圧力損失低減対策としては限界があっ
た。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, the conventional example described above has the following problems. That is, in the boilers shown in FIGS. 5 and 6, only the peripheral wall portion of the rear flue was subjected to the water supply bypass, and it was limited to the extremely small range. Therefore, there is a limit as a measure for reducing the pressure loss.
その上、第５図に示したボイラでは、バイパス量を調整
しないので、気液二相流が流れる亜臨界圧域においては
管内流動特性が不安定になり易い欠点があった。Moreover, in the boiler shown in FIG. 5, since the bypass amount is not adjusted, the in-pipe flow characteristics are likely to be unstable in the subcritical pressure region where the gas-liquid two-phase flow flows.
一方、第６図に示したボイラにおいても、効果的な運用
を行うためには、バイパス弁の操作領域が複雑になり、
ボイラの運転操作が難しくなる欠点があった。On the other hand, in the boiler shown in FIG. 6 as well, in order to perform effective operation, the operation area of the bypass valve becomes complicated,
There was a drawback that it became difficult to operate the boiler.
本発明は、このような従来技術の課題を解決するために
なされたもので、全負荷帯にわたり高い信頼性を維持し
つつ、超臨界域において圧力損失を低減できる超臨界圧
変圧運転形ボイラを提供することを目的とする。The present invention has been made in order to solve the problems of the prior art, and provides a supercritical pressure transformer operation type boiler capable of reducing pressure loss in the supercritical range while maintaining high reliability over the entire load band. The purpose is to provide.
課題を解決するための手段 上記の課題を解決するために、本発明は、過熱器、再熱
器、煙道蒸発器、節炭器などの伝熱部が配置されている
後部煙道を有し、この後部煙道の周壁が水冷壁管にて構
成されている超臨界圧変圧運転形ボイラにおいて、少な
くとも前記煙道蒸発器をバイパスする管路を設けると共
に、この管路の途中部分にバイパス弁を設け、このバイ
パス弁を超臨界圧となる高負荷域で開くようにしたもの
である。Means for Solving the Problems In order to solve the above problems, the present invention has a rear flue in which heat transfer parts such as a superheater, a reheater, a flue evaporator, and a economizer are arranged. However, in the supercritical pressure variable operation type boiler in which the peripheral wall of the rear flue is composed of a water-cooled wall pipe, at least a pipe that bypasses the flue evaporator is provided and a bypass is provided in the middle of this pipe. A valve is provided and this bypass valve is opened in the high load region where the pressure becomes supercritical.
作用 上記の手段によれば、少なくとも煙道蒸発器をバイパス
する管路に設けたバイパス弁は過熱蒸気域又は超臨界圧
域であるボイラの高負荷時において作動されて、給水が
バイパスする範囲を大きくし、これにより系統の圧力損
失が容易に軽減される。また、気液二相流が流れる領域
では、給水のバイパスを止めることにより、各伝熱部の
管内の流動に対して何らの影響も与えない。Action According to the above means, at least the bypass valve provided in the pipe bypassing the flue evaporator is operated at a high load of the boiler in the superheated steam region or the supercritical pressure region, and the range in which the feed water bypasses is The pressure loss of the system is easily reduced by increasing the size. Further, in the region where the gas-liquid two-phase flow flows, by stopping the bypass of the feed water, there is no influence on the flow in the pipe of each heat transfer section.
実施例 以下図面を参照して、本発明の実施例について詳述す
る。第１図は本発明による超臨界圧変圧運転形ボイラの
全体概略を示し、第２図および第３図は同ボイラにおけ
る給水バイパス装置の異なる２つの実施態様の詳細を示
す。Embodiments Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 shows a general outline of a supercritical pressure variable pressure operation type boiler according to the present invention, and FIGS. 2 and 3 show details of two different embodiments of a feed water bypass device in the boiler.
第１図に示すボイラは、蒸気タービンの負荷に応じて超
臨界圧域から亜臨界圧域まで変圧運転が行われるもの
で、火炉11と後部煙道12とにより構成されており、火炉
11の上部および後部煙道12に過熱器13,14,15、再熱器1
6,17、煙道蒸発器18、節炭器19などの伝熱部が配置され
ている。The boiler shown in FIG. 1 performs a variable pressure operation from a supercritical pressure region to a subcritical pressure region according to the load of a steam turbine, and is composed of a furnace 11 and a rear flue 12,
11 upper and rear flues 12 superheater 13,14,15, reheater 1
Heat transfer parts such as 6,17, flue evaporator 18 and economizer 19 are arranged.
しかして、ボイラへの給水は、節炭器19、火炉11、後部
煙道12の周壁12′、煙道蒸発器18、ウォータセパレータ
20の順に流れ、さらに過熱器13,14,15を経て過熱され、
蒸気タービン（図示せず）に導かれる。そして、一般
に、最低貫流負荷（20〜30％負荷）以上の負荷において
は、ウォータセパレータ20には乾き蒸気のみが流入し、
ドレンは発生しない。これに対して、最低貫流負荷以下
の低負荷においては、ウォータセパレータ20には気液二
相の状態の流体が流入し、気水分離が行われ、蒸気のみ
が過熱器13,14,15へ導かれ、ドレンは起動系統（図示せ
ず）に戻される。Water is supplied to the boiler by the economizer 19, the furnace 11, the peripheral wall 12 'of the rear flue 12, the flue evaporator 18, and the water separator.
It flows in the order of 20 and is further superheated through superheaters 13, 14 and 15.
Guided to a steam turbine (not shown). And, generally, under the load of the minimum flow-through load (20 to 30% load) or more, only dry steam flows into the water separator 20,
Drain does not occur. On the other hand, at a low load equal to or lower than the minimum flow-through load, the fluid in the gas-liquid two-phase state flows into the water separator 20 to separate water and water, and only steam is sent to the superheaters 13, 14, 15. Guided, the drain is returned to the starting system (not shown).
第２図に示す給水バイパス装置は、第１図に示したよう
なボイラの後部煙道周壁12′と煙道蒸発器18とを連続し
てバイパスするバイパス管21とバイパス弁22とを設けた
ものである。そして、圧力が超臨界圧以上である高負荷
帯においてのみ、バイパス弁22を作動させて一部の給水
をバイパスさせ、圧力損失の軽減を図る。しかし、圧力
が亜臨界圧域となる負荷以下の負荷領域であって、気液
二相流が流れる領域では、バイパス弁22を開とすること
は系統の流動不安定を生ずる恐れがあり、好ましくな
い。The water supply bypass device shown in FIG. 2 is provided with a bypass pipe 21 and a bypass valve 22 for continuously bypassing the rear flue peripheral wall 12 'and the flue evaporator 18 as shown in FIG. It is a thing. Then, only in the high load zone where the pressure is equal to or higher than the supercritical pressure, the bypass valve 22 is operated to bypass a part of the water supply to reduce the pressure loss. However, in the load region where the pressure is the subcritical pressure region or less, and in the region where the gas-liquid two-phase flow flows, opening the bypass valve 22 may cause flow instability of the system, which is preferable. Absent.
第３図に示す給水バイパス装置は、第２図に示したバイ
パスの範囲をさらに拡げ、後部煙道周壁12′、煙道蒸発
器18、ウォータセパレータ20および過熱器13を連続して
バイパスするバイパス管21′とバイパス弁22′とを設け
たものである。この場合においても、バイパス弁22′を
作動させる負荷帯は、圧力が臨界点を越える臨界に限定
される。第４図は、第２図に示したバイパス方式を活用
した場合と、バイパス弁22を全閉のままに保った場合と
のボイラ入口（節炭器入口）の圧力の比較を行った一例
を示すものである。The water supply bypass device shown in FIG. 3 further expands the range of the bypass shown in FIG. 2 and continuously bypasses the rear flue peripheral wall 12 ′, the flue evaporator 18, the water separator 20 and the superheater 13. A pipe 21 'and a bypass valve 22' are provided. Even in this case, the load zone for operating the bypass valve 22 'is limited to the critical point where the pressure exceeds the critical point. FIG. 4 shows an example of comparing the pressure at the boiler inlet (coal inlet) when the bypass method shown in FIG. 2 is used and when the bypass valve 22 is kept fully closed. It is shown.
以上述べたように、気液二相流が流れる亜臨界圧域の負
荷帯においては系統内の流動特性に何ら悪影響を与え
ず、超臨界圧域の高負荷帯においてのみバイパス弁の開
度を調整し、効果的な圧力損失低減をはかるので、プラ
ントの高効率化と、信頼性向上に大きく寄与できる。As described above, in the load zone of the subcritical pressure region where gas-liquid two-phase flow flows, there is no adverse effect on the flow characteristics in the system, and the opening degree of the bypass valve is set only in the high load zone of the supercritical pressure region. By adjusting the pressure loss effectively, the plant efficiency can be improved and the reliability can be improved.
発明の効果 以上述べたように、本発明によれば、超臨界圧変圧運転
形ボイラにおいて、少なくとも煙道蒸発器をバイパスす
る管路を設けると共に、この管路の途中部分にバイパス
弁を設け、このバイパス弁を超臨界圧となる高負荷域で
開くようにすることにより、次に述べるような顕著の効
果を奏する。As described above, according to the present invention, in the supercritical pressure variable pressure operation type boiler, at least a pipe path that bypasses the flue evaporator is provided, and a bypass valve is provided at an intermediate portion of the pipe path. By opening this bypass valve in the high load range where the pressure becomes supercritical, the following remarkable effects are achieved.
すなわち、50％以下程度の負荷以上でバイパスする場
合、50％程度の負荷では超臨界圧変圧運転形ボイラが亜
臨界圧で運転されるものであるが、亜臨界圧では後部煙
道周壁、煙道蒸発器の内部流体は二相流となるため、こ
こでバイパスすることは流動安定性の阻害要因となりか
ねないが、本発明ではバイパス運用を超臨界圧領域（各
プラントによって異なるが、普通は70％前後以上）に限
るため、流動安定性の阻害を生じる恐れがなく、またバ
イパス弁の運用基準が明確となる。That is, when bypassing above a load of about 50% or less, the supercritical pressure transformer operation type boiler operates at subcritical pressure at a load of about 50%, but at subcritical pressure, the rear flue peripheral wall, smoke Since the internal fluid of the tractor evaporator becomes a two-phase flow, bypassing it here may hinder the flow stability.However, in the present invention, bypass operation is performed in the supercritical pressure region (it varies depending on each plant, but usually Since it is limited to about 70% or more), there is no risk of impairing the flow stability, and the operational standard of the bypass valve becomes clear.
したがって、本発明によれば、給水バイパス装置の合理
的な配置を行なえるとともに、バイパス弁の明確な運用
指針を与えることができるので、ボイラの全負荷帯にわ
たり高い信頼性を維持しつつ、超臨界圧域において圧力
損失を低減させ、プラントの熱効率向上に大きく寄与す
ることが可能となる。Therefore, according to the present invention, a rational arrangement of the water supply bypass device can be performed, and a clear operation guideline for the bypass valve can be provided. Therefore, while maintaining high reliability over the entire load band of the boiler, It is possible to reduce the pressure loss in the critical pressure region and greatly contribute to the improvement of the thermal efficiency of the plant.
具体的には、例えば従来例ではバイパス部圧力損失は高
負荷でも略4kg/cm2程度であり、20％バイパス時の低減
はたかだか1.4kg/cm2であるのに対して、本発明では高
負荷時、少なくとも14kg/cm2程度の圧力損失を5kg/cm2
程度も低減でき、超臨界圧力域のみのバイパス運用で効
果的にプラントの高効率化を図ることができる。Specifically, for example, in the conventional example, the bypass section pressure loss is about 4 kg / cm 2 even under a high load, and the reduction at the time of 20% bypass is at most 1.4 kg / cm 2 , whereas in the present invention, it is high. When loaded, at least 14 kg / cm 2 of pressure loss is 5 kg / cm 2
The degree can be reduced, and by operating the bypass only in the supercritical pressure range, the efficiency of the plant can be effectively improved.
第１図は本発明による超臨界圧変圧運転形ボイラの全体
概略図、第２図及び第３図は本発明による給水バイパス
装置を含む系統の異なる二例を示す図、第４図は本発明
によるボイラ入口圧力の比較図、第５図及び第６図は従
来のボイラにおける給水バイパスの異なる二例を示す系
統図である。 11……火炉、12……後部煙道、12′……後部煙道周壁、
13,14,15……過熱器、16,17……再熱器、18……煙道蒸
発器、19……節炭器、20……ウォータセパレータ、21,2
1′……バイパス管、22,22′……バイパス弁。FIG. 1 is an overall schematic view of a supercritical pressure variable pressure operation type boiler according to the present invention, FIGS. 2 and 3 are views showing two different systems including a feed water bypass device according to the present invention, and FIG. 5 and 6 are system diagrams showing two examples of different feed water bypasses in the conventional boiler. 11 …… furnace, 12 …… rear flue, 12 ′ …… rear flue peripheral wall,
13,14,15 …… Superheater, 16,17 …… Reheater, 18 …… Flue vaporizer, 19 …… Carbulator, 20 …… Water separator, 21,2
1 '... bypass pipe, 22,22' ... bypass valve.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 柏崎 正道 東京都千代田区丸の内２丁目５番１号 三 菱重工業株式会社内 (56)参考文献 特開 昭56−74501（ＪＰ，Ａ) 実開 昭58−137204（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Masamichi Kashiwazaki Inventor Masamichi Kashiwazaki 2-5-1 Marunouchi, Chiyoda-ku, Tokyo Sanryo Heavy Industries Co., Ltd. (56) References JP-A-56-74501 (JP, A) 58-137204 (JP, U)
Claims (1)
の伝熱部が配置されている後部煙道を有し、この後部煙
道の周壁が水冷壁管にて構成されている超臨界圧変圧運
転形ボイラにおいて、少なくとも前記煙道蒸発器をバイ
パスする管路を設けると共に、この管路の途中部分にバ
イパス弁を設け、このバイパス弁を超臨界圧となる高負
荷域で開くことを特徴とする超臨界圧変圧運転形ボイ
ラ。1. A rear flue in which heat transfer parts such as a superheater, a reheater, a flue evaporator, and a economizer are arranged, and a peripheral wall of the rear flue is a water-cooled wall tube. In a supercritical pressure variable pressure operation type boiler that is used, at least a pipe that bypasses the flue evaporator is provided, and a bypass valve is provided in the middle of this pipe so that the bypass valve has a supercritical pressure. A supercritical pressure variable pressure operation type boiler characterized by opening in the region.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60271370A JPH0684801B2 (en) | 1985-12-04 | 1985-12-04 | Supercritical pressure transformer type boiler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60271370A JPH0684801B2 (en) | 1985-12-04 | 1985-12-04 | Supercritical pressure transformer type boiler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62131102A JPS62131102A (en) | 1987-06-13 |
| JPH0684801B2 true JPH0684801B2 (en) | 1994-10-26 |
Family
ID=17499120
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60271370A Expired - Fee Related JPH0684801B2 (en) | 1985-12-04 | 1985-12-04 | Supercritical pressure transformer type boiler |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0684801B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2921839B2 (en) * | 1988-12-27 | 1999-07-19 | バブコツク日立株式会社 | Supercritical pressure operation boiler |
| US5617898A (en) * | 1991-09-10 | 1997-04-08 | Smc Kabushiki Kaisha | Fluid pressure apparatus |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5674501A (en) * | 1979-11-21 | 1981-06-20 | Mitsubishi Heavy Ind Ltd | Super critical pressure variable operation type forcedly once through boiler |
| JPS58137204U (en) * | 1982-03-11 | 1983-09-14 | バブコツク日立株式会社 | boiler equipment |
-
1985
- 1985-12-04 JP JP60271370A patent/JPH0684801B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62131102A (en) | 1987-06-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4869210A (en) | Method of operating a once-through steam generator | |
| US4487166A (en) | Start-up system for once-through boilers | |
| JP3140539B2 (en) | Waste heat recovery boiler and method of supplying de-heated water | |
| JPH0684801B2 (en) | Supercritical pressure transformer type boiler | |
| JPH0417324B2 (en) | ||
| JPH0942606A (en) | Once-through boiler steam temperature control device | |
| JPH10292902A (en) | Main steam temperature controller | |
| JP3285946B2 (en) | Steam temperature controller for variable-pressure once-through boiler | |
| JPS6291703A (en) | Steaming preventive device for fuel economizer | |
| JPH03282102A (en) | Exhaust heat recovery boiler and controller of temperature reducing device used for it | |
| JP2531801B2 (en) | Exhaust heat recovery heat exchanger controller | |
| JP3176435B2 (en) | Steam generator | |
| JPH0463282B2 (en) | ||
| JPH0688605A (en) | Controlling device for temperature of steam in boiler | |
| JP2971629B2 (en) | Waste heat recovery boiler | |
| JPS62162808A (en) | Fuel-economizer steaming preventive device for thermal powerboiler system | |
| GB1600352A (en) | Power plant | |
| JPH0842802A (en) | Device for controlling generating quantity of intermediate/low pressure steam in exhaust gas boiler | |
| JP2921839B2 (en) | Supercritical pressure operation boiler | |
| JPH0330763B2 (en) | ||
| JP2908085B2 (en) | Waste heat recovery boiler | |
| JPH09195718A (en) | Main steam temperature control device | |
| JPS61289205A (en) | Variable pressure operation type once-through boiler using various fuel | |
| JPH028201B2 (en) | ||
| JPH08327006A (en) | Supercritical variable pressure once-through boiler |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |