JPH01285606A - Method and device of starting 2-stage reheat type steam turbine plant - Google Patents
Method and device of starting 2-stage reheat type steam turbine plantInfo
- Publication number
- JPH01285606A JPH01285606A JP11160488A JP11160488A JPH01285606A JP H01285606 A JPH01285606 A JP H01285606A JP 11160488 A JP11160488 A JP 11160488A JP 11160488 A JP11160488 A JP 11160488A JP H01285606 A JPH01285606 A JP H01285606A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- pressure turbine
- steam
- control valve
- temperature
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims abstract description 17
- 238000009423 ventilation Methods 0.000 claims abstract description 13
- 238000004891 communication Methods 0.000 claims description 8
- 238000003303 reheating Methods 0.000 claims 1
- 230000001105 regulatory effect Effects 0.000 abstract description 5
- 230000001276 controlling effect Effects 0.000 description 8
- 239000002184 metal Substances 0.000 description 8
- 238000001816 cooling Methods 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000013022 venting Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 229910000963 austenitic stainless steel Inorganic materials 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910001105 martensitic stainless steel Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 230000002040 relaxant effect Effects 0.000 description 1
Landscapes
- Control Of Turbines (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
（産業上の利用分野）
本発明はタービンバイパス装置を有する二段再熱式蒸気
タービンプラントの起動方法およびその装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a method and apparatus for starting a two-stage reheat steam turbine plant having a turbine bypass device.
（従来の技術）
タービンバイパス系はボイラと蒸気タービンとの相互の
制約を解消または緩和することによってプラント運転の
柔軟性を高める目的で設置されるもので、次の様な機能
を有することを特徴とする。(Prior art) A turbine bypass system is installed for the purpose of increasing the flexibility of plant operation by eliminating or relaxing the mutual constraints between the boiler and the steam turbine, and is characterized by the following functions: shall be.
まず、第一の機能はボイラ負荷とタービン負荷の差の吸
収であり、ボイラの負荷応答性を超える急激な負荷変化
に対応してその時の応答遅れを吸収すると共に、送電系
統の事故等により所内単独負荷運転に移行する場合の余
剰蒸気の排出を可能とする。また、第二の機能としては
起動特性の向上であり、起動時に再熱器の蒸気冷却を行
なうことによって再熱器の焼損を防止しなからボイラ燃
焼率を高めると共に、タービン通気時のメタルマツチン
グ（タービン内蒸気通路部の温度と通気蒸気との温度差
をできるだけ小さくする）を容易に行なえることである
。第三の機能は過熱器安全弁および再熱器安全弁として
の機能を果し、特に変圧運転プラントと組合せる場合の
圧力上昇を抑えることができる。First, the first function is to absorb the difference between the boiler load and the turbine load, and in response to sudden load changes that exceed the boiler's load response, it absorbs the response delay at that time. This allows excess steam to be discharged when transitioning to single load operation. The second function is to improve the startup characteristics.By cooling the reheater with steam at startup, it prevents burnout of the reheater and increases the boiler combustion rate. cooling (reducing the temperature difference between the temperature of the steam passage in the turbine and the ventilation steam as small as possible) can be easily performed. The third function is to serve as a superheater safety valve and a reheater safety valve, which can reduce pressure rises, especially when combined with variable pressure operating plants.
上記の機能をふまえて、従来のタービンバイパス系は第
２図に示す如く、高圧タービンバイパス装置として、ボ
イラ１より発生した蒸気を高圧タービン２をバイパスし
て流すために主蒸気管３と低温再熱蒸気管４とを結ぶ高
圧タービンバイパス管５と、高圧タービンバイパス管５
の蒸気流量を制御するためのバイパス制御弁６と、この
バイパス制御弁６の出口温度を制御するための減温器７
とで構成され、低温再熱蒸気管４には高圧タービン排気
逆止弁８が設置されている。また、低圧タービンバイパ
ス装置として、ボイラの再熱器９を通過した蒸気を中圧
タービン１０および低圧タービン１１とをバイパスして
復水器１２ヘダンブするために高温再熱蒸気管１３と復
水器１２とを結ぶ中、低圧タービンバイパス管１４と、
この中、低圧タービンバイパス管１４の蒸気流量を制御
するためのバイパス制御弁１５と、バイパス制御弁１５
の出口温度を制御するための減温器１６とで構成されて
いる。復水器１２で凝縮した水は復水ポンプ１７．低圧
ヒータ１８゜脱気器１９．給水ポンプ２０．高圧ヒータ
２１の各々を通ってボイラ１に送られ、再び蒸気となり
循環される。また１通常運用時は、前述のタービンバイ
パス系は使用されず、ボイラ１により発生した蒸気は高
圧タービン２、再熱器９．中圧タービン１０゜低圧ター
ビン１１を通して＠環される６発電機２２は高圧タービ
ン２．中圧タービン１０および低圧タービン１１によっ
て駆動される。なお、符号２３は主蒸気止め弁、符号２
４は蒸気加減弁を示している。Based on the above functions, the conventional turbine bypass system, as shown in Fig. 2, is a high-pressure turbine bypass device that connects the main steam pipe 3 and low-temperature recycler to flow the steam generated from the boiler 1 bypassing the high-pressure turbine 2. A high-pressure turbine bypass pipe 5 connecting the heat steam pipe 4 and a high-pressure turbine bypass pipe 5
a bypass control valve 6 for controlling the steam flow rate of the bypass control valve 6; and a desuperheater 7 for controlling the outlet temperature of the bypass control valve 6.
A high-pressure turbine exhaust check valve 8 is installed in the low-temperature reheat steam pipe 4. In addition, as a low pressure turbine bypass device, a high temperature reheat steam pipe 13 and a condenser are used to bypass the intermediate pressure turbine 10 and the low pressure turbine 11 and dump the steam that has passed through the reheater 9 of the boiler to the condenser 12. 12, a low pressure turbine bypass pipe 14,
Among these, a bypass control valve 15 for controlling the steam flow rate of the low pressure turbine bypass pipe 14;
and a desuperheater 16 for controlling the outlet temperature. The water condensed in the condenser 12 is transferred to the condensate pump 17. Low pressure heater 18° deaerator 19. Water pump 20. It is sent to the boiler 1 through each of the high-pressure heaters 21, and is turned into steam again and circulated. Furthermore, during normal operation, the above-mentioned turbine bypass system is not used, and the steam generated by the boiler 1 is transferred to the high pressure turbine 2, the reheater 9. 6 generators 22 are connected through the intermediate pressure turbine 10° and the low pressure turbine 11 through the high pressure turbine 2. It is driven by an intermediate pressure turbine 10 and a low pressure turbine 11. In addition, numeral 23 is the main steam stop valve, numeral 2
4 indicates a steam control valve.
この従来のタービンバイパス系統を有する蒸気タービン
プラントでは、起動方式として下記の２つの方法がある
が、各々一長一短がある。まず第一の方法として、中圧
タービン１０および低圧タービン１１で起動、昇速し、
さらに低負荷を制御する。In a steam turbine plant having this conventional turbine bypass system, there are the following two startup methods, each of which has advantages and disadvantages. First, the intermediate pressure turbine 10 and the low pressure turbine 11 are started and speeded up,
Furthermore, it controls low loads.
この場合は中圧タービン１０の入口圧力が低いため制御
性が良いという長所がある反面、高圧タービン２内は蒸
気加減弁２４から僅かに漏洩する蒸気で再熱蒸気管の圧
力に近い蒸気圧力の状態となっているため、この中でロ
ータが定格回転数で回転すると蒸気と動翼の摩擦による
風損により高圧タービン２内の蒸気温度が過上昇し、こ
の温度が高圧タービン２内のロータおよび動翼の強度に
とって厳しい条件になるという問題があり、また、高圧
タービン２のケーシングとロータの伸び差に異常が生じ
るという問題がある。In this case, the inlet pressure of the intermediate pressure turbine 10 is low, so controllability is good, but on the other hand, the steam inside the high pressure turbine 2 is slightly leaked from the steam control valve 24, and the steam pressure is close to the pressure of the reheat steam pipe. If the rotor rotates at the rated speed, the steam temperature inside the high-pressure turbine 2 will rise excessively due to windage loss due to the friction between the steam and the rotor blades, and this temperature will cause the rotor inside the high-pressure turbine 2 to There is a problem that conditions are severe for the strength of the rotor blades, and there is also a problem that an abnormality occurs in the difference in expansion between the casing of the high-pressure turbine 2 and the rotor.
次に、第二の方法として、高圧タービン２のみ。Next, as a second method, only the high pressure turbine 2 is used.
あるいは高圧タービン２と中圧タービン１０と低圧ター
ビン１１で同時に起動・昇速し、さらに低負荷を制御す
る場合がある。この場合には高圧タービン２に冷却蒸気
が流れているため、高圧タービン２内の温度上昇は比較
的低く維持されるので問題にならない反面、高圧タービ
ン２の蒸気−メタルマツチングと、中圧タービン１０お
よび低圧タービン１１の蒸気−メタルマツチングを同時
に考慮して制御しなければならないという制御上の難し
さがある。Alternatively, the high-pressure turbine 2, intermediate-pressure turbine 10, and low-pressure turbine 11 may be started and speeded up simultaneously to further control a low load. In this case, since cooling steam is flowing through the high-pressure turbine 2, the temperature rise inside the high-pressure turbine 2 is maintained relatively low and is not a problem. There is a control difficulty in that the steam-to-metal matching of the low pressure turbine 10 and the low pressure turbine 11 must be considered and controlled at the same time.
この従来のタービンバイパス系を二段の再熱器を有する
ボイラと組合せた二段再熱式蒸気タービンプラントに適
用すると、第３図に示すようになる。超高圧タービンバ
イパス装置として、ボイラ１より発生した超高圧高温蒸
気を超高圧タービン２５をバイパスして流すために超高
圧主蒸気管２６と第一低温再熱蒸気管２７とを結ぶ超高
圧タービンバイパス管２８と、超高圧タービンバイパス
管２８の蒸気流量を制御するためのバイパス制御弁２９
と、バイパス制御弁２９の出口温度を制御するための減
温器３０とで構成され、第一低温再熱蒸気管２７には超
高圧タービン排気逆止弁３１が設置されている。また、
高圧タービンバイパス装置として、ボイラの第一段再熱
器３２を通過した蒸気を高圧タービン２をバイパスして
流すための第一高温再熱蒸気管３６と第二低温再熱蒸気
管３７とを結ぶ高圧タービンバイパス管３８と、高圧タ
ービンバイパス管３８の蒸気流量を制御するためのバイ
パス制御弁３９と、バイパス制御弁３９の出口温度を制
御するための減温器４０とで構成され、第二低温再熱蒸
気管３７には高圧タービン排気逆止弁４１が設置されて
いる。さらに、低圧タービンバイパス装置として、ボイ
ラの第二段再熱器４２を通過した蒸気を中圧タービン１
０および低圧タービン１１をバイパスして復水器１２ヘ
ダンプするために第二高温再熱蒸気管４３と復水ｉ１２
とを結ぶ中、低圧タービンバイパス管１４と、中、低圧
タービンバイパス管１４の蒸気流量を制御するためのバ
イパス制御弁１５と、バイパス制御弁１５の出口温度を
制御するための減温器１６とで構成されている。復水器
１２で凝縮した水は復水ポンプ１７．低圧ヒータ１８．
脱気器１９．給水ポンプ２０、高圧ヒータ２１の各々を
通ってボイラ１に送られ、再び蒸気となり循環される。When this conventional turbine bypass system is applied to a two-stage reheat steam turbine plant in combination with a boiler having a two-stage reheater, the result will be as shown in FIG. 3. As an ultra-high-pressure turbine bypass device, an ultra-high-pressure turbine bypass connects an ultra-high-pressure main steam pipe 26 and a first low-temperature reheat steam pipe 27 in order to flow the ultra-high-pressure high-temperature steam generated from the boiler 1 bypassing the ultra-high-pressure turbine 25. pipe 28 and a bypass control valve 29 for controlling the steam flow rate of the ultra-high pressure turbine bypass pipe 28
and a desuperheater 30 for controlling the outlet temperature of the bypass control valve 29, and an ultra-high pressure turbine exhaust check valve 31 is installed in the first low temperature reheat steam pipe 27. Also,
As a high-pressure turbine bypass device, a first high-temperature reheat steam pipe 36 and a second low-temperature reheat steam pipe 37 are connected for flowing steam that has passed through the first stage reheater 32 of the boiler bypassing the high-pressure turbine 2. A second low temperature A high-pressure turbine exhaust check valve 41 is installed in the reheat steam pipe 37 . Furthermore, as a low pressure turbine bypass device, the steam that has passed through the second stage reheater 42 of the boiler is transferred to the intermediate pressure turbine 1.
0 and the second high temperature reheat steam pipe 43 and condensate i12 to bypass the low pressure turbine 11 and dump to the condenser 12.
A low pressure turbine bypass pipe 14, a bypass control valve 15 for controlling the steam flow rate of the middle and low pressure turbine bypass pipe 14, and a desuperheater 16 for controlling the outlet temperature of the bypass control valve 15. It consists of The water condensed in the condenser 12 is transferred to the condensate pump 17. Low pressure heater 18.
Deaerator19. The water is sent to the boiler 1 through the water supply pump 20 and the high-pressure heater 21, and is turned into steam again and circulated.
また１通常運用時には、前述のタービンバイパス系は使
用されず、ボイラ１より発生した蒸気は超高圧タービン
２５、第一段再熱器３２、高圧タービン２、第二段再熱
器４２．中圧タービン１０．低圧タービン１１を通して
循環される。Further, during normal operation, the above-mentioned turbine bypass system is not used, and the steam generated from the boiler 1 is transferred to the ultra-high pressure turbine 25, the first stage reheater 32, the high pressure turbine 2, the second stage reheater 42, . Medium pressure turbine10. It is circulated through the low pressure turbine 11.
発電機２２は超高圧タービン２５、高圧タービン２、中
圧タービン１０、低圧タービン１１により駆動される。The generator 22 is driven by an ultra-high pressure turbine 25, a high pressure turbine 2, an intermediate pressure turbine 10, and a low pressure turbine 11.
なお、符号４４は排気管、４５は主蒸気止め弁、４６は
蒸気加減弁をそれぞれ示している。The reference numeral 44 indicates an exhaust pipe, 45 indicates a main steam stop valve, and 46 indicates a steam control valve.
（発明が解決しようとする課題）
蒸気タービンプラントの性能向上の重要開発機種として
、主蒸気圧力、温度を従来の機種より高めた超高圧高温
蒸気タービンの開発が進んでおり。(Problem to be Solved by the Invention) As an important development model for improving the performance of steam turbine plants, the development of ultra-high pressure and high temperature steam turbines with higher main steam pressure and temperature than conventional models is progressing.
国内では従来機種の主蒸気入口条件である２４６ｋｇｆ
／ｄ１５３８℃を上回る３１６ｋｇｆ／ａＪ１５６６℃
の超高圧高温蒸気タービンの開発が完了し、すでに建設
が進められている。これらの超高圧高温蒸気タービンは
基本的には二段の再熱器を有する二段再熱式蒸気タービ
ンプラントである。この二段再熱式蒸気タービンプラン
トの場合、超高圧タービンの排気圧力は従来の高圧ター
ビンの約２倍の圧力、すなわち、 １００ｋｇｆ／ａＪ
ｇ程度となる。蒸気圧力が高いということは蒸気の密
度が高いことであり、この高圧の蒸気と動翼の摩擦によ
る風損は従来よりも大きくなり、二の風損による温度上
昇のためロータおよび動翼の強度の限界を超えることが
懸念される。このため、前述のように、従来のタービン
バイパス系を二段再熱式超高圧高温タービンに適用する
のでは、タービン起動時における運転操作が非常に難し
い、さらに、超高圧高温蒸気タービンの場合、蒸気ター
ビンの部品材料にマルテンサイト系ステンレス鋼や、オ
ーステナイト系ステンレス鋼が使用されるため、タービ
ンの伸び差に対しては従来以上の厳しい管理が要求され
、この点でも、前述のような従来のバイパス系を適用す
るのでは、タービン起動時における運転操作が難しくな
る。In Japan, the main steam inlet condition for conventional models is 246 kgf.
316kgf/aJ1566℃ exceeding /d1538℃
The development of an ultra-high-pressure, high-temperature steam turbine has been completed, and construction is already underway. These ultra-high pressure, high temperature steam turbines are essentially two-stage reheat steam turbine plants with two stages of reheaters. In the case of this two-stage reheat steam turbine plant, the exhaust pressure of the ultra-high pressure turbine is approximately twice that of a conventional high-pressure turbine, that is, 100 kgf/aJ.
It will be about g. High steam pressure means high steam density, and the windage loss due to friction between this high-pressure steam and the rotor blades is greater than before, and the strength of the rotor and rotor blades is reduced due to the temperature increase due to windage loss. There is a concern that the limit will be exceeded. For this reason, as mentioned above, if a conventional turbine bypass system is applied to a two-stage reheat type ultra-high-pressure, high-temperature turbine, operation at the time of turbine startup is extremely difficult. Since martensitic stainless steel and austenitic stainless steel are used as materials for steam turbine parts, stricter control than before is required for the difference in elongation of the turbine. If a bypass system is applied, operation during turbine startup becomes difficult.
そこで、本発明の目的はプラントの起動時に臨んでター
ビン系からの制約を満しつつ、タービンバイパス系の運
転を可能とし、さらに起動時の状況に応じたタービンバ
イパス系の適用に柔軟性を持たせこれにより、起動特性
および制御性の向上を高めるようにした二段再熱式蒸気
タービンプラントの起動方法およびその装置を提供する
ことにある。Therefore, the purpose of the present invention is to enable the operation of the turbine bypass system while satisfying the constraints imposed by the turbine system at the time of plant start-up, and to provide flexibility in the application of the turbine bypass system depending on the situation at the time of start-up. Therefore, it is an object of the present invention to provide a method and apparatus for starting a two-stage reheat steam turbine plant, which improves starting characteristics and controllability.
（ＩＩ！ｉｔを解決するための手段）
上記目的を達成するために本発明においては超高圧ター
ビンと高圧タービンと中圧タービンと低圧タービンとか
らなるタービン系、第一段再熱器と第二段再熱器とから
なる再熱系、超高圧タービンバイパス系と高圧タービン
バイパス系と中、低圧タービンバイパス系とからなるタ
ービンバイパス系、各々出力制御に用いられる超高圧タ
ービン用の主蒸気加減弁、高圧タービン用の第一再熱蒸
気加減弁、中圧タービン用の第二再熱蒸気加減弁を有す
る二段再熱式蒸気タービンプラントの起動方法において
、タービンバイパス系の運転状態からタービン系への通
気を開始するにあたり、タービン系の回転部の温度が第
二段再熱器から送られる再熱蒸気の温度よりも高い場合
、中圧および低圧タービンに再熱蒸気の一部が流れるよ
うに第二再熱蒸気加減弁を制御し、かつ残りの再熱蒸気
は中、低圧タービンバイパス系にて処理し、その場合超
高圧および高圧タービンの内部圧力は低圧タービンの入
口圧力とほぼ同等に保持し、またタービン系の同転部の
温度が第一段再熱器から送られる再熱蒸気の温度よりも
低い場合、高圧タービンに再熱蒸気の一部が流れるよう
に第一再熱蒸気加減弁を制御し、かつ残りの再熱蒸気は
高圧および中、低圧タービンバイパス系を用いて処理し
、その場合超高圧タービンの内部圧力は高圧タービンの
内部圧力とほぼ同等に保持することを特徴とする。(Means for Solving II!it) In order to achieve the above object, the present invention includes a turbine system consisting of an ultra-high pressure turbine, a high pressure turbine, an intermediate pressure turbine, and a low pressure turbine, a first stage reheater and a second stage reheater. A reheat system consisting of a stage reheater, a turbine bypass system consisting of an ultra-high-pressure turbine bypass system, a high-pressure turbine bypass system, and a medium and low-pressure turbine bypass system, and a main steam control valve for the ultra-high pressure turbine each used for output control. , in a method for starting a two-stage reheat steam turbine plant having a first reheat steam control valve for a high-pressure turbine and a second reheat steam control valve for an intermediate-pressure turbine, from the operating state of the turbine bypass system to the turbine system. When starting ventilation, if the temperature of the rotating part of the turbine system is higher than the temperature of the reheated steam sent from the second stage reheater, some of the reheated steam will flow to the intermediate-pressure and low-pressure turbines. The second reheat steam control valve is controlled, and the remaining reheat steam is processed in the medium and low pressure turbine bypass system, in which case the internal pressure of the ultra-high pressure and high pressure turbines is maintained approximately equal to the inlet pressure of the low pressure turbine. However, if the temperature of the co-rotating part of the turbine system is lower than the temperature of the reheated steam sent from the first-stage reheater, the first reheated steam is adjusted so that a part of the reheated steam flows to the high-pressure turbine. valve, and the remaining reheated steam is processed using a high pressure, medium and low pressure turbine bypass system, in which case the internal pressure of the ultra high pressure turbine is maintained approximately equal to the internal pressure of the high pressure turbine. do.
また、上記目的を達成するために本発明は超高圧タービ
ンと高圧タービンと中圧タービンと低圧タービンとから
なるタービン系、第一段再熱器と第二段再熱器とからな
る再熱系、超高圧タービンバイパス系と高圧タービンバ
イパス系と中、低圧タービンバイパス系とからなるター
ビンバイパス系、各々出力制御に用いられる超高圧ター
ビン用の主蒸気加減弁、高圧タービン用の第一再熱蒸気
加減弁、中圧タービン用の第二再熱蒸気加減弁を有する
二段再熱式蒸気タービンプラントにおいて。In order to achieve the above object, the present invention also provides a turbine system including an ultra-high pressure turbine, a high pressure turbine, an intermediate pressure turbine, and a low pressure turbine, and a reheat system including a first stage reheater and a second stage reheater. , a turbine bypass system consisting of an ultra-high-pressure turbine bypass system, a high-pressure turbine bypass system, and a medium- and low-pressure turbine bypass system, a main steam control valve for the ultra-high pressure turbine used for output control, and a first reheat steam for the high-pressure turbine. In a two-stage reheat steam turbine plant having a regulating valve, a second reheat steam regulating valve for an intermediate pressure turbine.
超高圧タービンの排気側と高圧タービンの排気側とを連
絡する第一タービン排気連絡管を排気制御弁を介して、
また高圧タービンの排気側と中圧タービンの排気側とを
連絡する第二タービン排気連絡管を排気制御弁を介して
それぞれ設けたことを特徴とする。A first turbine exhaust connecting pipe that connects the exhaust side of the ultra-high pressure turbine and the exhaust side of the high pressure turbine is connected through an exhaust control valve.
The present invention is also characterized in that a second turbine exhaust communication pipe is provided to connect the exhaust side of the high-pressure turbine and the exhaust side of the intermediate-pressure turbine via exhaust control valves.
（作用）
プラントの起動時に臨んでタービン系の回転部の温度が
第二段再熱器から送られる再熱蒸気の温度よりも高い場
合、温度調節された再熱蒸気を中圧タービンおよび低圧
タービンに流し、タービン系の通気を始める。また、残
りの再熱蒸気は中。(Operation) When the temperature of the rotating part of the turbine system is higher than the temperature of the reheated steam sent from the second stage reheater at the time of plant startup, the temperature-adjusted reheated steam is sent to the intermediate pressure turbine and the low pressure turbine. and start venting the turbine system. Also, the remaining reheated steam is medium.
低圧タービンバイパス装置を使用して復水器に排出する
。Discharge to condenser using low pressure turbine bypass device.
一方、タービン系の回転部の温度が第一段再熱器から送
られる再熱蒸気の温度よりも低い場合。On the other hand, when the temperature of the rotating part of the turbine system is lower than the temperature of the reheated steam sent from the first stage reheater.
温度調節された再熱蒸気を高圧タービンに流し。The temperature-controlled reheated steam is passed through a high-pressure turbine.
タービン系の通気を開始する。Start venting the turbine system.
また、残りの再熱蒸気は高圧タービンバイパス装置およ
び中、低圧タービンバイパス装置を用いて復水器に排出
する。In addition, the remaining reheated steam is discharged to the condenser using the high pressure turbine bypass device and the medium and low pressure turbine bypass devices.
このように本発明の起動方法においてはプラント起動時
のタービン系の状況に応じて、中圧および低圧タービン
起動あるいは、高圧タービン起動を行なうことが可能で
あり、起動方法に柔軟性が与えられるため、起動特性の
向上を図ることができる。さらにこの起動過程における
タービン通気時の制御が上記の起動方法の何かを選択す
ることにより中圧タービンのみの制御あるいは、高圧タ
ービンのみの制御となるため、プラントの制御性を高め
ることができる。In this way, in the startup method of the present invention, depending on the situation of the turbine system at the time of plant startup, it is possible to start the intermediate-pressure and low-pressure turbines or to start the high-pressure turbine, which provides flexibility in the startup method. , it is possible to improve the starting characteristics. Further, by selecting one of the above-mentioned startup methods, the control during turbine ventilation during the startup process can be performed to control only the intermediate pressure turbine or only the high pressure turbine, thereby improving the controllability of the plant.
（実施例） 以下１本発明の一実施例を図面により説明する。(Example) An embodiment of the present invention will be described below with reference to the drawings.
本実施例は第１１！１に示す如くタービンバイパス系と
して、超高圧タービンバイパス管２８、バイパス制御弁
２９および減温器３０からなる系と、高圧タービンバイ
パス管３８．バイパス制御弁３９および減温器４０から
なる系と、中、低圧タービンバイパス管１４．バイパス
制御系１５．および減温器１６からなる系と、超高圧タ
ービン２５の排気管である第一低温再熱蒸気管２７．高
圧タービン２の排気管である第二低温再熱蒸気管４１と
を連絡する第一タービン排気連絡管４７．この第一ター
ビン排気連絡管４７に設置された排気制御弁４８、第二
低温再熱蒸気管３７と中圧タービン１０の排気管４４と
を連絡する第二タービン排気連絡管４９、この第二ター
ビン排気連絡管に設置された排気制御弁５０からなる系
とを備えている。なお１図中符号５０は第一再熱蒸気止
め弁。In this embodiment, as shown in No. 11!1, the turbine bypass system includes a system consisting of an ultra-high-pressure turbine bypass pipe 28, a bypass control valve 29, and a desuperheater 30, and a high-pressure turbine bypass pipe 38. A system consisting of a bypass control valve 39 and a desuperheater 40, and a medium and low pressure turbine bypass pipe 14. Bypass control system 15. and a first low-temperature reheat steam pipe 27 which is an exhaust pipe of the ultra-high pressure turbine 25. A first turbine exhaust communication pipe 47 that communicates with a second low-temperature reheat steam pipe 41 that is an exhaust pipe of the high-pressure turbine 2. An exhaust control valve 48 installed in this first turbine exhaust connecting pipe 47, a second turbine exhaust connecting pipe 49 that connects the second low temperature reheat steam pipe 37 and the exhaust pipe 44 of the intermediate pressure turbine 10, and this second turbine The system includes an exhaust control valve 50 installed in an exhaust communication pipe. Note that the reference numeral 50 in Figure 1 is the first reheat steam stop valve.
５１は第一再熱蒸気加減弁、５２は第二再熱蒸気止め弁
、５３は第二再熱蒸気加減弁を各々示している。Reference numeral 51 indicates a first reheat steam control valve, 52 a second reheat steam stop valve, and 53 a second reheat steam control valve.
蒸気タービンとボイラの負荷差を吸収するためにタービ
ンバイパス系の運転中、超高圧タービンバイパス管２８
のバイパス制御弁２９と、主蒸気加減弁４６とにより、
超高圧タービン２５に流す蒸気量を調整し、また高圧タ
ービンバイパス管３８のバイパス制御弁３９と第一再熱
蒸気加減弁５１とにより、高圧タービン２に流す流量を
１ｌｌｌ、さらに中、低圧タービンバイパス管１４のバ
イパス制御弁１５と第二再熱蒸気加減弁５３により、中
圧タービンｌＯおよび低圧タービン１１に流す蒸気量を
ｉｉａする。この時、減温器３０．４０．１６を使用す
ることにより各バイパス蒸気を冷却して第一低温再熱蒸
気管２７、第二低温再熱蒸気管３７、復水器１２に導き
、これらの機器を保護する。また、超高圧タービン排気
逆止弁３１および高圧タービン排気逆止弁４１により、
超高圧タービン２５ならびに高圧タービン２へ逆流する
のを防止する。During operation of the turbine bypass system to absorb the load difference between the steam turbine and the boiler, the ultra-high pressure turbine bypass pipe 28
By the bypass control valve 29 and the main steam control valve 46,
The amount of steam flowing to the ultra-high pressure turbine 25 is adjusted, and the flow rate flowing to the high pressure turbine 2 is adjusted to 1llll by the bypass control valve 39 of the high pressure turbine bypass pipe 38 and the first reheat steam control valve 51, and further, The bypass control valve 15 of the pipe 14 and the second reheat steam control valve 53 control the amount of steam flowing to the intermediate pressure turbine IO and the low pressure turbine 11. At this time, each bypass steam is cooled by using the desuperheater 30, 40, 16 and guided to the first low temperature reheat steam pipe 27, the second low temperature reheat steam pipe 37, and the condenser 12. Protect your equipment. In addition, the ultra-high pressure turbine exhaust check valve 31 and the high pressure turbine exhaust check valve 41 provide
This prevents backflow to the ultra-high pressure turbine 25 and the high pressure turbine 2.
次に、起動時において、タービン停止後の時間による蒸
気タービンの冷却状態に応じてタービン通気時の蒸気−
メタルマツチングを図り、起動特性を向上させるため、
タービンウオーミング初期状態において、回転部の温度
が蒸気温度に比べて高い場合には、中圧タービン１０お
よび低圧タービン１１による起動を行なう、また１回転
部の温度が通気蒸気温度よりも低くなる場合には、高圧
タービン２による起動を行なう、すなわち、状況に即し
て起動方法を使い分けて起動の柔軟性を高め。Next, at startup, depending on the cooling state of the steam turbine depending on the time after the turbine is stopped,
In order to achieve metal matching and improve starting characteristics,
In the initial state of turbine warming, if the temperature of the rotating part is higher than the steam temperature, the intermediate pressure turbine 10 and the low pressure turbine 11 are started, and if the temperature of the one rotating part becomes lower than the ventilation steam temperature, In this case, the high-pressure turbine 2 is used for starting, that is, the starting method is used depending on the situation to increase the flexibility of starting.
かつ回転部の風損による温度上昇を低く保つように以下
に述べるようにタービンバイパス系を用いて制御する。In addition, a turbine bypass system is used to control the temperature rise due to wind damage in the rotating part, as described below, in order to keep it low.
タービン起動の初期において、ボイラ１で発生した蒸気
は主蒸気加減弁４６を閉状態、バイパス制御弁２９を開
状態としておくことにより、超高圧タービンバイパス管
２８を通り、減温器３０で減温され。At the initial stage of turbine startup, the steam generated in the boiler 1 passes through the ultra-high pressure turbine bypass pipe 28 and is reduced in temperature by the attemperator 30 by keeping the main steam control valve 46 closed and the bypass control valve 29 open. It is.
第一段再熱器３２で加熱される。この再熱蒸気は第一再
熱蒸気加減弁５１を閉状態、バイパス制御弁３９を開状
態としておくことにより、高圧タービンバイパス管３８
を通り、減温器４０で減温され、第二段再熱器４２で再
び加熱され、第二高温再熱蒸気管４３に導びかれる。ま
た、第二再熱蒸気加減弁５３を閉状態とし、バイパス制
御弁１５を開状態としておくことにより、第二高温再熱
蒸気管４３に流れた再熱蒸気は復水器１２に排出される
。この時、超高圧タービン排気逆止弁３１および高圧タ
ービン排気逆止弁４１により、再熱蒸気は、各々、超高
圧タービン２５および高圧タービン２に流入することは
ない。It is heated by the first stage reheater 32. This reheated steam is transferred to the high pressure turbine bypass pipe 38 by keeping the first reheated steam control valve 51 closed and the bypass control valve 39 open.
The steam is then cooled by a desuperheater 40, heated again by a second-stage reheater 42, and guided to a second high-temperature reheat steam pipe 43. Furthermore, by keeping the second reheat steam control valve 53 closed and the bypass control valve 15 open, the reheat steam flowing into the second high temperature reheat steam pipe 43 is discharged to the condenser 12. . At this time, the ultra-high pressure turbine exhaust check valve 31 and the high-pressure turbine exhaust check valve 41 prevent reheated steam from flowing into the ultra-high pressure turbine 25 and the high-pressure turbine 2, respectively.
これにより、蒸気タービン側から制約をうけることなく
ボイラの起動特性を高めることができる。Thereby, the starting characteristics of the boiler can be improved without being constrained by the steam turbine side.
また、この時、第一タービン排気連絡管４７および第二
タービン排気連絡管４９に設置された排気制御弁４８．
５０を開状態としておくことにより、超高圧タービン２
５および高圧タービン２の内部の圧力が低圧タービン１
１の入口圧力とほぼ等しくなる。すなわち、中圧タービ
ン１０および低圧タービン１１は第二再熱蒸気加減弁５
３が閉じられているために再熱蒸気が流れず、各内部圧
力が復水器１２の器内圧力とほぼ平衡しているため、超
高圧タービン２５および高圧タービン２の内部圧力も復
水器１２の器内圧力、つまり真空状態となっている。な
お、微量ながら主蒸気加減弁４６のシート面から漏洩す
る蒸気が、第一タービン排気連絡管４７および第二ター
ビン排気連絡管４８を通って流れている。Also, at this time, the exhaust control valves 48 installed in the first turbine exhaust connecting pipe 47 and the second turbine exhaust connecting pipe 49.
By keeping 50 open, the ultra-high pressure turbine 2
5 and the pressure inside the high pressure turbine 2 is the same as that of the low pressure turbine 1.
It becomes almost equal to the inlet pressure of 1. That is, the intermediate pressure turbine 10 and the low pressure turbine 11 are connected to the second reheat steam control valve 5.
3 is closed, reheated steam does not flow, and each internal pressure is almost in equilibrium with the internal pressure of the condenser 12. Therefore, the internal pressure of the ultra-high pressure turbine 25 and the high pressure turbine 2 is also the same as that of the condenser. 12 internal pressure, that is, a vacuum state. Note that a small amount of steam leaking from the seat surface of the main steam control valve 46 flows through the first turbine exhaust communication pipe 47 and the second turbine exhaust communication pipe 48 .
この後、蒸気−メタルマツチングの適正化を図ることに
よる起動特性向上を考慮して、蒸気タービンの冷却状態
に応じて、下記■、■の何れかを選択し、タービン通気
９回転上昇、負荷上昇の順でタービン起動を進める。After this, in consideration of improving the starting characteristics by optimizing the steam-metal matching, select either of the following ■ or ■ depending on the cooling state of the steam turbine, increase the turbine ventilation by 9 rotations, and increase the load. Proceed with turbine startup in ascending order.
■・・・回転部の温度が蒸気温度と比べて高い場合上記
のタービンバイパス系の運転時、主蒸気は超高圧タービ
ン２５、高圧タービン２を通ることなく、第一段再熱器
３２および第二段再熱器４２により加熱されるため、再
熱蒸気は比較的早く温度上昇が可能であり、中圧タービ
ン１０における蒸気−メタルマツチングが図り易く、中
圧タービン１０および低圧タービン１１への通気により
回転上昇を行なう方法を採るならば、起動過程において
、タービン通気のタイミングを早めることができる。す
なわち、タービンバイパス系の運転状態から、中圧ター
ビン１０の蒸気−メタルマツチングを考慮して第二再熱
蒸気加減弁５３を開いて行き、中、低圧タービンバイパ
ス管１４を流れていた蒸気の一部を中圧タービン１０お
よび低圧タービン１１に流す、これによりタービン通気
を行ない、続いて回転上昇に入る。この時、超高圧ター
ビン２５．高圧タービン２の各内部圧力は排気制御弁４
８．５０が開状態にあるために低圧タービン１１の入口
圧力にほぼ等しくなる。このため、超高圧タービン２５
および高圧タービン２の回転部の風損による温度上昇を
小さく保つことができる。■...When the temperature of the rotating part is higher than the steam temperature When the above-mentioned turbine bypass system is operating, the main steam does not pass through the ultra-high pressure turbine 25 and the high-pressure turbine 2, and instead passes through the first stage reheater 32 and the first stage reheater 32. Since the reheated steam is heated by the two-stage reheater 42, the temperature of the reheated steam can be increased relatively quickly, and steam-metal matching in the intermediate pressure turbine 10 can be easily achieved, and the temperature of the reheated steam can be increased relatively quickly. If a method of increasing rotation through ventilation is adopted, the timing of turbine ventilation can be advanced during the startup process. That is, from the operating state of the turbine bypass system, the second reheat steam control valve 53 is opened in consideration of the steam-metal matching of the intermediate pressure turbine 10, and the steam flowing through the intermediate and low pressure turbine bypass pipe 14 is reduced. A portion is passed to the intermediate pressure turbine 10 and the low pressure turbine 11, thereby providing turbine ventilation and subsequently entering the rotation up. At this time, the ultra-high pressure turbine 25. Each internal pressure of the high pressure turbine 2 is controlled by the exhaust control valve 4
8.50 is in the open state, it becomes approximately equal to the inlet pressure of the low pressure turbine 11. For this reason, the ultra-high pressure turbine 25
Also, the temperature rise due to wind damage in the rotating part of the high-pressure turbine 2 can be kept small.
この状態から、超高圧タービン２５および高圧タービン
２の蒸気−メタルマツチングと伸び差等を考慮して、主
蒸気加減弁４６および第一再熱蒸気加減弁５１を開いて
行き、同時に、バイパス制御弁２９゜３９を閉鎖して行
く、これにより、超高圧タービン２５および高圧タービ
ン２の排気圧力が上昇し、第一低温再熱蒸気管２７およ
び第二低温再熱蒸気管３７に設置された超高圧タービン
排気逆止弁３１および高圧タービン排気逆止弁４１がそ
れぞれ全開されるために超高圧タービン２５および高圧
タービン２内を蒸気が通過するようになる。したがって
、これ以後蒸気による仕事がなされ、タービン負荷の上
昇が行なわれる。この後、主蒸気加減弁４６．第一再熱
蒸気加減弁５１．第二再熱蒸気加減弁５３を開いて行き
、これと共にバイパス制御弁２９．３９．１５を閉鎖し
て行き、タービン負荷をさらに上昇して行く、バイパス
１ｔ制御弁２９．３９．１５が全閉すると共に。From this state, the main steam control valve 46 and the first reheat steam control valve 51 are opened, taking into account the steam-metal matching and expansion difference of the ultra-high pressure turbine 25 and the high-pressure turbine 2, and at the same time, the bypass control valve 46 and the first reheat steam control valve 51 are opened. As the valves 29 and 39 are closed, the exhaust pressure of the ultra-high pressure turbine 25 and the high-pressure turbine 2 increases, and the Since the high-pressure turbine exhaust check valve 31 and the high-pressure turbine exhaust check valve 41 are fully opened, steam passes through the ultra-high-pressure turbine 25 and the high-pressure turbine 2. Therefore, after this, work is performed by the steam, and the turbine load is increased. After this, the main steam control valve 46. First reheat steam control valve 51. The second reheat steam control valve 53 is opened, and the bypass control valve 29.39.15 is closed at the same time, and the turbine load is further increased.The bypass 1t control valve 29.39.15 is fully closed. Along with.
第一再熱蒸気加減弁５１．第二再熱蒸気加減弁５３を全
開状態とし、これ以後さらにタービン負荷を上昇させる
には、主蒸気加減弁４６で蒸気量を増加して行く、これ
により回転部の温度が蒸気温度に比べて高い場合におい
ても、タービンバイパス系を開いてタービン通気のタイ
ミングを早めることが可能となり、タービン起動特性を
向上させることができる。また、タービン通気時の制御
が第二再熱蒸気加減弁５３のみとなるため、制御特性も
向上する。First reheat steam control valve 51. The second reheat steam control valve 53 is fully opened, and in order to further increase the turbine load, the main steam control valve 46 increases the amount of steam.This causes the temperature of the rotating part to become lower than the steam temperature. Even when the air pressure is high, it is possible to open the turbine bypass system and advance the timing of turbine ventilation, thereby improving the turbine startup characteristics. Further, since only the second reheat steam control valve 53 is controlled during turbine ventilation, control characteristics are also improved.
■・・・回転部温度が蒸気温度と比べて低い場合上記の
タービンバイパス運転時、超高圧タービンバイパス管２
８に設置された減温器３０を使用して。■...When the rotating part temperature is lower than the steam temperature During the above turbine bypass operation, the ultra-high pressure turbine bypass pipe 2
Using a desuperheater 30 installed at 8.
第一高温再熱蒸気管３６を流れる再熱蒸気の温度を比較
的低く保つことにより、高圧タービン２の回転部メタル
温度との温度差を少なくする。第一再熱蒸気加減弁５１
を開いて行き、高圧タービンバイパス管３８を流れてい
たバイパス蒸気の一部を高圧タービン２に導き、同時に
排気制御弁５０を閉鎖状態にする。この排気制御弁５０
が閉鎖されると、高圧タービン２の排気圧力が上昇し、
高圧タービン排気逆止弁４５は開状態となり、高圧ター
ビン２に通気が行なわれ、タービン速度が上昇し始める
。By keeping the temperature of the reheated steam flowing through the first high-temperature reheated steam pipe 36 relatively low, the temperature difference between the reheated steam and the rotating part metal temperature of the high-pressure turbine 2 is reduced. First reheat steam control valve 51
The high pressure turbine bypass pipe 38 is opened and a part of the bypass steam flowing through the high pressure turbine bypass pipe 38 is guided to the high pressure turbine 2, and at the same time, the exhaust control valve 50 is closed. This exhaust control valve 50
is closed, the exhaust pressure of the high pressure turbine 2 increases,
The high-pressure turbine exhaust check valve 45 is opened, the high-pressure turbine 2 is vented, and the turbine speed begins to increase.
この時、排気制御弁４８が開いているため、超高圧ター
ビン２５の内部圧力は高圧タービン２の排気圧力とほぼ
平衡させられる。また、中圧タービンｌＯおよび低圧タ
ービン１１には蒸気が流れていないため、復水器１２の
器内圧力にほぼ同等の圧力となっている。超高圧タービ
ン２５、中圧タービン１０、低圧タービン１１はそれぞ
れ上記した排気圧力のもとで回され、それぞれの回転部
は風損のために若干温度が上昇する。この風損による温
度上昇を逆に。At this time, since the exhaust control valve 48 is open, the internal pressure of the ultra-high pressure turbine 25 is approximately balanced with the exhaust pressure of the high pressure turbine 2. Furthermore, since no steam is flowing through the intermediate pressure turbine 1O and the low pressure turbine 11, the pressure is approximately the same as the internal pressure of the condenser 12. The ultra-high-pressure turbine 25, the intermediate-pressure turbine 10, and the low-pressure turbine 11 are each rotated under the above exhaust pressure, and the temperature of each rotating part increases slightly due to windage loss. Reverse the temperature rise due to windage damage.
超高圧タービン２５および中圧タービン１０のウオーミ
ング熱源として利用し、この後超高圧タービン２５およ
び中圧タービン１０の蒸気−メタル温度のマツチングを
図り、伸び差を考慮しつつ、主蒸気加減弁４６および第
二再熱蒸気加減弁５３を開いて行く。It is used as a warming heat source for the ultra-high-pressure turbine 25 and the intermediate-pressure turbine 10, and after that, the steam-metal temperature of the ultra-high-pressure turbine 25 and the intermediate-pressure turbine 10 is matched, and while taking into account the difference in expansion, the main steam control valve 46 and The second reheat steam control valve 53 is opened.
これにより、中圧タービン１０と低圧タービン１１に再
熱蒸気が流れ出し、これらの起動が開始される。As a result, reheated steam flows into the intermediate pressure turbine 10 and the low pressure turbine 11, and their startup is started.
この時、同時に排気制御弁４８を閉鎖することにより、
超高圧タービン２５の排気圧力が上昇し、超高圧タービ
ン排気逆止弁３１は開状態となり、超高圧タービン２５
内を蒸気が通過するようになり、タービン負荷の上昇が
可能になる。At this time, by simultaneously closing the exhaust control valve 48,
The exhaust pressure of the ultra-high pressure turbine 25 increases, the ultra-high pressure turbine exhaust check valve 31 becomes open, and the ultra-high pressure turbine 25
Steam can now pass through it, allowing the turbine load to increase.
この後、主蒸気加減弁４６、第一再熱蒸気加減弁５１、
第二再熱蒸気加減弁５３を開くと同時に、バイパス制御
弁２ｇ、 ３９．１５を絞りこみ、タービン負荷を上昇
させる。そして、バイパス制御弁２ｇ、 ３９゜１５が
全閉となった時に第一再熱蒸気加減弁５１および第二再
熱蒸気加減弁５３を全開させる。これ以後。After this, the main steam control valve 46, the first reheat steam control valve 51,
At the same time as opening the second reheat steam control valve 53, the bypass control valves 2g and 39.15 are throttled to increase the turbine load. Then, when the bypass control valves 2g and 39°15 are fully closed, the first reheat steam control valve 51 and the second reheat steam control valve 53 are fully opened. After this.
さらにタービン負荷を上昇させるには、主蒸気加減弁４
６で蒸気量を増加して行く、これにより、回転部温度が
蒸気温度より低い場合も、タービンバイパス系を用いた
起動が可能となり、起動特性を向上させることができる
。また、タービン通気時の制御が第一再熱蒸気加減弁５
１のみの制御となるので制御性も向上する。To further increase the turbine load, the main steam control valve 4
The amount of steam is increased in step 6. As a result, even when the rotating part temperature is lower than the steam temperature, startup using the turbine bypass system is possible, and the startup characteristics can be improved. In addition, the control during turbine ventilation is performed by the first reheat steam control valve 5.
Since only 1 is controlled, controllability is also improved.
以上詳述したように本発明は、二段再熱式蒸気タービン
プラントの起動に臨んで、タービンバイパス系を適切に
用いて同転部の風損による温度上昇を低く抑えつつ、タ
ービン起動状況に応じた。As described in detail above, the present invention appropriately uses a turbine bypass system to keep the temperature rise due to wind damage in the rotary section low when starting up a two-stage reheat steam turbine plant, while adjusting the turbine startup situation. I complied.
適正で、かつ制御性の高い運転方法を与えることができ
る。したがって、本発明によればプラントの起動特性お
よび制御性が高められるという優れた効果を奏する。An appropriate and highly controllable driving method can be provided. Therefore, according to the present invention, the excellent effect of improving the start-up characteristics and controllability of the plant is achieved.
第１図は本発明方法に適用される起動装置を含む二段再
熱式蒸気タービンプラントの系統図、第２図は従来のタ
ービンバイパス系を有する蒸気タービンプラントの系統
図、第３図は従来のタービンバイパス系を有する二段再
熱式蒸気タービンプラントの系統図である。
１・・・ボイラ ２・・・高圧タービン１０・
・・中圧タービン １１・・・低圧タービン１４・・
・中、低圧タービンバイパス１２５・・・超高圧タービ
ン
２８・・・超高圧タービンバイパス１
３２・・・第一段再熱器
３８・・・高圧タービンバイパス管
４２・・・第二段再熱器 ４６・・・主蒸気加減弁４
７・・・第一タービン排気連絡管
４８、５０・・・排気制御弁
４９・・・第二タービン排気連絡管
５１・・・第一再熱蒸気加減弁
５３・・・第二再熱蒸気加減弁
代理人 弁理士 則 近 憲 佑
同 第子丸 健
第１図Fig. 1 is a system diagram of a two-stage reheat steam turbine plant including a starting device applied to the method of the present invention, Fig. 2 is a system diagram of a steam turbine plant having a conventional turbine bypass system, and Fig. 3 is a system diagram of a conventional steam turbine plant. 1 is a system diagram of a two-stage reheat steam turbine plant having a turbine bypass system. 1... Boiler 2... High pressure turbine 10.
...Intermediate pressure turbine 11...Low pressure turbine 14...
- Medium and low pressure turbine bypass 125...Ultra high pressure turbine 28...Ultra high pressure turbine bypass 1 32...First stage reheater 38...High pressure turbine bypass pipe 42...Second stage reheater 46...Main steam control valve 4
7... First turbine exhaust communication pipe 48, 50... Exhaust control valve 49... Second turbine exhaust communication pipe 51... First reheated steam control valve 53... Second reheated steam control valve Patent Attorney Nori Ken Yudo Ken Daishimaru Figure 1
Claims (2)
低圧タービンとからなるタービン系、第一段再熱器と第
二段再熱器とからなる再熱系、超高圧タービンバイパス
系と高圧タービンバイパス系と中、低圧タービンバイパ
ス系とからなるタービンバイパス系、各々出力制御に用
いられる超高圧タービン用の主蒸気加減弁、高圧タービ
ン用の第一再熱蒸気加減弁、中圧タービン用の第二再熱
蒸気加減弁を有する二段再熱蒸気タービンプラントの起
動方法において、前記タービンバイパス系の運転状態か
ら前記タービン系への通気を開始するにあたり、該ター
ビン系の回転部の温度が前記第二段再熱器から送られる
再熱蒸気の温度よりも高い場合、前記中圧および低圧タ
ービンに再熱蒸気の一部が流れるように前記第二再熱蒸
気加減弁を制御し、かつ残りの再熱蒸気は前記中、低圧
タービンバイパス系にて処理し、その場合前記超高圧お
よび高圧タービンの内部圧力は前記低圧タービンの入口
圧力とほぼ同等に保持し、また前記タービン系の回転部
の温度が前記第一段再熱器から送られる再熱蒸気の温度
よりも低い場合、前記高圧タービンに再熱蒸気の一部が
流れるように前記第一再熱蒸気加減弁を制御し、かつ残
りの再熱蒸気は前記高圧および中、低圧タービンバイパ
ス系を用いて処理し、その場合前記超高圧タービンの内
部圧力は前記高圧タービンの内部圧力とほぼ同等に保持
することを特徴とする二段再熱式蒸気タービンプラント
の起動方法。(1) A turbine system consisting of an ultra-high pressure turbine, a high pressure turbine, an intermediate pressure turbine and a low pressure turbine, a reheat system consisting of a first stage reheater and a second stage reheater, an ultra high pressure turbine bypass system and a high pressure turbine A turbine bypass system consisting of a bypass system and a medium- and low-pressure turbine bypass system, a main steam control valve for the ultra-high pressure turbine used for output control, a first reheat steam control valve for the high-pressure turbine, and a first reheat steam control valve for the medium-pressure turbine. In a method for starting a two-stage reheat steam turbine plant having two reheat steam control valves, when starting ventilation to the turbine system from the operating state of the turbine bypass system, the temperature of the rotating part of the turbine system is If the temperature is higher than the temperature of the reheated steam sent from the two-stage reheater, the second reheated steam control valve is controlled so that a part of the reheated steam flows to the intermediate pressure and low pressure turbines, and the remaining The reheated steam is processed in the medium and low pressure turbine bypass system, in which case the internal pressures of the ultra high pressure and high pressure turbines are maintained approximately equal to the inlet pressure of the low pressure turbine, and the temperature of the rotating part of the turbine system is maintained. is lower than the temperature of the reheated steam sent from the first stage reheater, the first reheated steam control valve is controlled so that a part of the reheated steam flows to the high pressure turbine, and the remaining Two-stage reheating characterized in that the reheated steam is processed using the high pressure, intermediate and low pressure turbine bypass system, in which case the internal pressure of the ultra high pressure turbine is maintained approximately equal to the internal pressure of the high pressure turbine. How to start a steam turbine plant.
低圧タービンとからなるタービン系、第一段再熱器と第
二段再熱器とからなる再熱系、超高圧タービンバイパス
系と高圧タービンバイパス系と中、低圧タービンバイパ
ス系とからなるタービンバイパス系、各々出力制御に用
いられる超高圧タービン用の主蒸気加減弁、高圧タービ
ン用の第一再熱蒸気加減弁、中圧タービン用の第二再熱
蒸気加減弁を有する二段再熱式蒸気タービンプラントに
おいて、前記超高圧タービンの排気側と前記高圧タービ
ンの排気側とを連絡する第一タービン排気連絡管を排気
制御弁を介して、前記高圧タービンの排気側と前記中圧
タービンの排気側とを連絡する第二タービン排気連絡管
を排気制御弁を介してそれぞれ設けたことを特徴とする
二段再熱式蒸気タービンプラントの起動装置。(2) A turbine system consisting of an ultra-high-pressure turbine, a high-pressure turbine, an intermediate-pressure turbine, and a low-pressure turbine, a reheat system consisting of a first-stage reheater and a second-stage reheater, an ultra-high-pressure turbine bypass system, and a high-pressure turbine A turbine bypass system consisting of a bypass system and a medium- and low-pressure turbine bypass system, a main steam control valve for the ultra-high pressure turbine used for output control, a first reheat steam control valve for the high-pressure turbine, and a first reheat steam control valve for the medium-pressure turbine. In a two-stage reheat steam turbine plant having two reheat steam control valves, a first turbine exhaust connecting pipe connecting the exhaust side of the ultra-high pressure turbine and the exhaust side of the high pressure turbine is connected through an exhaust control valve; A starting device for a two-stage reheat steam turbine plant, characterized in that a second turbine exhaust communication pipe connecting the exhaust side of the high-pressure turbine and the exhaust side of the intermediate-pressure turbine is provided through an exhaust control valve. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63111604A JP2677598B2 (en) | 1988-05-10 | 1988-05-10 | Start-up method for two-stage reheat steam turbine plant. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63111604A JP2677598B2 (en) | 1988-05-10 | 1988-05-10 | Start-up method for two-stage reheat steam turbine plant. |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01285606A true JPH01285606A (en) | 1989-11-16 |
| JP2677598B2 JP2677598B2 (en) | 1997-11-17 |
Family
ID=14565558
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63111604A Expired - Lifetime JP2677598B2 (en) | 1988-05-10 | 1988-05-10 | Start-up method for two-stage reheat steam turbine plant. |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2677598B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108301882A (en) * | 2018-03-12 | 2018-07-20 | 西安热工研究院有限公司 | A kind of generating set three-level series-parallel connection bypath system and its adjusting method |
| CN110056402A (en) * | 2019-03-26 | 2019-07-26 | 华电电力科学研究院有限公司 | Steam surplus energy utility for coal-fired thermal power unit power peak regulation couples extraction for heat supply system and adjusting method |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5838305A (en) * | 1981-08-31 | 1983-03-05 | Toshiba Corp | 2-stage reheat turbine |
| JPS6282304U (en) * | 1985-11-13 | 1987-05-26 |
-
1988
- 1988-05-10 JP JP63111604A patent/JP2677598B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5838305A (en) * | 1981-08-31 | 1983-03-05 | Toshiba Corp | 2-stage reheat turbine |
| JPS6282304U (en) * | 1985-11-13 | 1987-05-26 |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108301882A (en) * | 2018-03-12 | 2018-07-20 | 西安热工研究院有限公司 | A kind of generating set three-level series-parallel connection bypath system and its adjusting method |
| CN108301882B (en) * | 2018-03-12 | 2024-03-05 | 西安热工研究院有限公司 | Three-stage series-parallel bypass system of generator set and adjusting method thereof |
| CN110056402A (en) * | 2019-03-26 | 2019-07-26 | 华电电力科学研究院有限公司 | Steam surplus energy utility for coal-fired thermal power unit power peak regulation couples extraction for heat supply system and adjusting method |
| CN110056402B (en) * | 2019-03-26 | 2023-11-28 | 华电电力科学研究院有限公司 | Steam complementary energy utilization coupling steam extraction heat supply system and adjusting method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2677598B2 (en) | 1997-11-17 |
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