JP2006161698A - Overload operation device and method for steam turbine - Google Patents

Overload operation device and method for steam turbine Download PDF

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JP2006161698A
JP2006161698A JP2004355081A JP2004355081A JP2006161698A JP 2006161698 A JP2006161698 A JP 2006161698A JP 2004355081 A JP2004355081 A JP 2004355081A JP 2004355081 A JP2004355081 A JP 2004355081A JP 2006161698 A JP2006161698 A JP 2006161698A
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steam
steam turbine
reheat
pressure
overload
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JP4509759B2 (en
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Noriaki Kitaguchi
典昭 北口
Kohei Saito
浩平 斉藤
Toshiaki Nishiyama
俊昭 西山
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Toshiba Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an overload operation device of a steam turbine capable of increasing output of the steam turbine while suppressing main steam pressure. <P>SOLUTION: In the steam turbine provided with a high pressure part 5 and a reheating part 6, leading high pressure steam to a high pressure part 5 via a main steam regulating valve 2, and leading steam to be reheated to a reheating part 6 via a reheating steam valve 3, the overload operation device for the steam turbine is branched out of an inlet side of the main steam regulating valve 2 and is communicated to an inlet side of the steam turbine reheating part 6 via an overload valve 4. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、オーバロード弁を備えた蒸気タービンの過負荷運転装置および蒸気タービンの過負荷運転方法に関する。   The present invention relates to an overload operation device for a steam turbine provided with an overload valve and an overload operation method for the steam turbine.

一般に、コンバインドサイクル発電プラントにおいては、ガスタービンの定格出力点を越えるような蒸気タービンの過負荷運転を行うことが、排熱回収ボイラにダクトファイアリングシステムを採用することにより実現可能である。   In general, in a combined cycle power plant, it is possible to perform an overload operation of a steam turbine that exceeds the rated output point of the gas turbine by adopting a duct firing system in the exhaust heat recovery boiler.

このダクトファイアリングシステムを採用する場合、コンバインドサイクル発電プラントの出力増加量は、理論的にはダクトファイアリング量を増やすことにより発電機容量の許容範囲内において制限はないが、主蒸気圧力はタービンに流入する蒸気量にほぼ比例するため、排熱回収ボイラを含む蒸気系統の設計圧力を高める必要があり、その分設備のコストが上昇することになる。   When this duct firing system is adopted, the output increase of the combined cycle power plant is theoretically not limited within the allowable range of the generator capacity by increasing the duct firing amount. Therefore, it is necessary to increase the design pressure of the steam system including the exhaust heat recovery boiler, which increases the cost of the equipment.

一方、主蒸気圧力の上昇を避けるため、オーバロード弁を用いて高圧部１段出口に過負荷分の蒸気を供給する方法も知られているが、この方法にしても主蒸気圧力がある程度上昇することは避けられない。   On the other hand, in order to avoid an increase in main steam pressure, a method of supplying overload steam to the first stage outlet of the high pressure section using an overload valve is also known, but even with this method, the main steam pressure increases to some extent. It is inevitable to do.

以下、図面を参照して従来の蒸気タービンの過負荷運転装置について説明する。
図６は蒸気タービンの過負荷運転装置の主要部を中心に示したもので、ガスタービンについては図示を省略している。図６において、排熱回収ボイラ１３の図示しない高圧加熱器から取り出された高圧の主蒸気は、主蒸気配管Ｐ１の主蒸気止弁１、主蒸気加減弁２を通過して蒸気タービン高圧部５に導入され、ここで膨張仕事を行ったあと排気管Ｐ２を介して排熱回収ボイラ１３の図示しない再熱器に送られて再熱される。そして、再熱蒸気は再熱蒸気管Ｐ３の再熱蒸気弁３を通して蒸気タービン再熱部６に導入される。そしてここで膨張仕事を行ったあと復水器７により復水にされる。１４は蒸気タービンによって回転駆動される発電機である。 Hereinafter, a conventional steam turbine overload operation device will be described with reference to the drawings.
FIG. 6 mainly shows the main part of the steam turbine overload operation device, and the illustration of the gas turbine is omitted. In FIG. 6, the high-pressure main steam taken out from the high-pressure heater (not shown) of the exhaust heat recovery boiler 13 passes through the main steam stop valve 1 and the main steam control valve 2 of the main steam pipe P1, and the steam turbine high-pressure part 5 After the expansion work is performed here, it is sent to a reheater (not shown) of the exhaust heat recovery boiler 13 through the exhaust pipe P2 and reheated. The reheat steam is introduced into the steam turbine reheat section 6 through the reheat steam valve 3 of the reheat steam pipe P3. And after performing expansion work here, it is made condensate by the condenser 7. Reference numeral 14 denotes a generator that is rotationally driven by a steam turbine.

通常では以上の蒸気系統により蒸気タービンは運転されるが、主蒸気圧力が定格点（ＶＷＯ）に到達し、かつ主蒸気加減弁の弁開度が全開のときに、さらに出力増加の要求があった場合は、図７で示すようにダクトファイアリング量を増やすことにより主蒸気流量を増加させ、主蒸気止弁１の出口側と蒸気タービン高圧部５の第１段出口との間を連通させる過負荷蒸気管Ｐ４に設けたオーバロード弁４の弁開度を開いて過負荷分に見合う蒸気量を供給し、蒸気タービン高圧部５の出力を増強させている（例えば、特許文献１参照）。   Normally, the steam turbine is operated by the above steam system, but when the main steam pressure reaches the rated point (VWO) and the valve opening degree of the main steam control valve is fully open, there is a demand for further increase in output. 7, the main steam flow rate is increased by increasing the duct firing amount as shown in FIG. 7, and the outlet side of the main steam stop valve 1 and the first stage outlet of the steam turbine high pressure section 5 are communicated with each other. The valve opening degree of the overload valve 4 provided in the overload steam pipe P4 is opened to supply a steam amount corresponding to the overload, and the output of the steam turbine high pressure section 5 is increased (for example, see Patent Document 1). .

このように、蒸気タービンの過負荷運転装置はオーバロード弁４を開いて蒸気を高圧第１段出口５１に供給するが、この高圧第１段出口５１の圧力はこれ以降の蒸気流量にほぼ比例するため圧力が上昇し、その結果主蒸気圧力も上昇する。例えば主蒸気流量を１０％増加させると、蒸気タービンの出力もほぼ１０％増加するが、そのためには主蒸気圧力が８％〜９％増加するため、この圧力に見合った蒸気系統の設備とする必要がある。
実開昭５７−１８２２０４号公報 As described above, the overload operation device for the steam turbine opens the overload valve 4 and supplies the steam to the high pressure first stage outlet 51. The pressure of the high pressure first stage outlet 51 is substantially proportional to the steam flow thereafter. As a result, the pressure rises, and as a result, the main steam pressure also rises. For example, when the main steam flow rate is increased by 10%, the output of the steam turbine is also increased by approximately 10%. For this purpose, the main steam pressure is increased by 8% to 9%. There is a need.
Japanese Utility Model Publication No. 57-182204

上述のように、従来の蒸気タービンの過負荷運転装置は、過負荷時にオーバロード弁を開いて蒸気を高圧１段出口に供給するので、排熱回収ボイラを含む蒸気系統の設計圧力を高める必要が生じ、その分蒸気プラントの設備費が嵩むことになる。   As described above, the conventional steam turbine overload operation device opens the overload valve and supplies steam to the high-pressure one-stage outlet at the time of overload, so it is necessary to increase the design pressure of the steam system including the exhaust heat recovery boiler. As a result, the cost of the steam plant increases accordingly.

近年、夏期の冷房用など電力のピーク需要が平常時に比べて突出する傾向にあり、これに対応した発電設備容量が求められるが、定格出力を最大需要に対応させるように構築した設備では設備費が割高になるため、ピーク需要に低コストで対応することのできる発電設備が求められている。   In recent years, peak demand for electricity, such as for cooling in summer, tends to be higher than normal, and power generation capacity corresponding to this demand is required. Therefore, there is a need for a power generation facility that can respond to peak demand at a low cost.

本発明は上述した従来技術の課題を解決するためになされたものであり、主蒸気圧力を押さえながら蒸気タービンの出力を増加させることのできる蒸気タービンの過負荷運転装置および蒸気タービンの過負荷運転方法を提供することを目的とするものである。   The present invention has been made to solve the above-described problems of the prior art, and is capable of increasing the output of the steam turbine while suppressing the main steam pressure, and the overload operation of the steam turbine. It is intended to provide a method.

上記の目的を達成するため、請求項１に係る蒸気タービンの過負荷運転装置の発明は、蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入した蒸気タービンにおいて、前記主蒸気加減弁の入口側から分岐して前記蒸気タービン再熱部の入口側にオーバロード弁を介して連通させたことを特徴とする。   In order to achieve the above object, an overload operation device for a steam turbine according to claim 1 includes a steam turbine high-pressure part and a steam turbine reheat part, and the high-pressure steam is supplied to the high-pressure steam turbine via a main steam control valve. In the steam turbine in which the reheat steam is introduced into the steam turbine reheat section through the reheat steam valve, the steam is branched from the inlet side of the main steam control valve to the inlet side of the steam turbine reheat section. It is characterized by communicating through an overload valve.

また、請求項２に係る蒸気タービンの過負荷運転装置の発明は、蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入した蒸気タービンにおいて、前記主蒸気加減弁の入口側から分岐して前記蒸気タービン高圧部の中間段落にオーバロード弁を介して連通させたことを特徴とする。   Further, the invention of the steam turbine overload operation device according to claim 2 comprises a steam turbine high-pressure part and a steam turbine reheat part, and introduces high-pressure steam into the steam turbine high-pressure part via the main steam control valve. In a steam turbine in which hot steam is introduced into a steam turbine reheat section via a reheat steam valve, it branches from the inlet side of the main steam control valve and communicates with an intermediate stage of the steam turbine high pressure section via an overload valve. It was made to be characterized.

さらに、請求項４に係る蒸気タービンの過負荷運転方法の発明は、蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入して蒸気タービンの過負荷運転を行うようにした運転方法において、前記主蒸気加減弁の入口側と前記蒸気タービン再熱部の入口側とを連通するオーバロード弁を、主蒸気圧力が定格点に到達し、かつ主蒸気加減弁の開度が全開のとき、オーバロード弁を開いて主蒸気を蒸気タービン再熱部の入口に導入することを特徴とする。   Further, the invention of the steam turbine overload operation method according to claim 4 comprises a steam turbine high-pressure part and a steam turbine reheat part, and introduces high-pressure steam into the steam turbine high-pressure part via the main steam control valve. In an operation method in which hot steam is introduced into a steam turbine reheat section through a reheat steam valve to perform an overload operation of the steam turbine, the inlet side of the main steam control valve and the steam turbine reheat section When the main steam pressure reaches the rated point and the opening of the main steam control valve is fully open, open the overload valve and connect the main steam to the inlet of the steam turbine reheat section. It is introduced in.

また、請求項５に係る蒸気タービンの過負荷運転方法の発明は、蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入して蒸気タービンの過負荷運転を行うようにした運転方法において、前記主蒸気加減弁の入口側と前記蒸気タービン再熱部の入口側とを連通するオーバロード弁を、主蒸気圧力が定格点に到達し、かつ主蒸気加減弁の開度が全開のとき、オーバロード弁を開いて主蒸気を高圧中間段落に導入することを特徴とする。   Further, the invention of the steam turbine overload operation method according to claim 5 comprises a steam turbine high-pressure part and a steam turbine reheat part, and introduces high-pressure steam into the steam turbine high-pressure part via the main steam control valve. In an operation method in which hot steam is introduced into a steam turbine reheat section through a reheat steam valve to perform an overload operation of the steam turbine, the inlet side of the main steam control valve and the steam turbine reheat section When the main steam pressure reaches the rated point and the main steam control valve is fully open, the overload valve communicating with the inlet side is opened and the main steam is introduced into the high-pressure intermediate stage. It is characterized by.

本発明によれば過負荷分の蒸気をオーバロード弁を介して過負荷蒸気管から蒸気タービン再熱部に導入、若しくは部分二重車室に構成された高圧タービンの中間段落に導入するようにしたので、主蒸気圧力の上昇を押さえながら蒸気タービンの出力を増加させることのできる蒸気タービンの過負荷運転装置および蒸気タービンの過負荷運転方法を提供することができる。   According to the present invention, the overload steam is introduced from the overload steam pipe into the steam turbine reheat section through the overload valve, or is introduced into an intermediate stage of the high pressure turbine configured in the partial double casing. Therefore, it is possible to provide a steam turbine overload operation device and a steam turbine overload operation method capable of increasing the output of the steam turbine while suppressing an increase in the main steam pressure.

以下、図面を参照して本発明の実施の形態について説明する。なお、各図を通して共通する部分については同一符号をつけて重複する説明は省略する。   Embodiments of the present invention will be described below with reference to the drawings. In addition, about the part which is common throughout each figure, the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

（第１の実施の形態）
図１を参照して本発明の第１の実施の形態について説明する。本実施の形態は、オーバロード弁４を備える過負荷蒸気管Ｐ４の出口側を蒸気タービン再熱部６の入口側に接続するように構成したものであり、その他の構成は従来の技術の場合と同じである。 (First embodiment)
A first embodiment of the present invention will be described with reference to FIG. In the present embodiment, the outlet side of the overload steam pipe P4 provided with the overload valve 4 is connected to the inlet side of the steam turbine reheating unit 6, and the other structure is the case of the prior art. Is the same.

このように構成した結果、本実施の形態による蒸気タービンの過負荷運転装置は、蒸気圧力が定格点に到達してかつ主蒸気加減弁が全開の時に過負荷要求があれば、オーバロード弁４を開くことにより、過負荷蒸気管Ｐ４から高温高圧蒸気をタービンの高温再熱部６に導入して、蒸気タービンの再熱部６の出力を増強させるので、発電プラントの出力はオーバロード弁４から導入される蒸気量に応じて増強する。   As a result of such a configuration, the overload operation device for the steam turbine according to the present embodiment provides an overload valve 4 if there is an overload request when the steam pressure reaches the rated point and the main steam control valve is fully open. Since the high-temperature high-pressure steam is introduced from the overload steam pipe P4 into the high-temperature reheat section 6 of the turbine to increase the output of the reheat section 6 of the steam turbine, the output of the power plant is increased by the overload valve 4. It increases according to the amount of steam introduced from

しかも、この実施の形態では、蒸気タービン再熱部６の蒸気圧力は流量に比例して増加するが、蒸気タービン高圧部５の流量は増加しないため、主蒸気圧力は定格点に比較してほとんど上昇しない。過負荷分の蒸気は再熱部のみを通過するため、主蒸気流量増加に対するタービン出力の寄与はタービン全体のうち再熱部が受け持つ出力しか増加しない。   In addition, in this embodiment, the steam pressure in the steam turbine reheating unit 6 increases in proportion to the flow rate, but the flow rate in the steam turbine high pressure unit 5 does not increase, so that the main steam pressure is almost lower than the rated point. Does not rise. Since the overloaded steam passes only through the reheat section, the contribution of the turbine output to the increase in the main steam flow rate is only increased by the output of the reheat section of the entire turbine.

通常、蒸気タービン再熱部６の出力分担は７割程度であるため、オーバロード弁４の開により主蒸気流量が１０％増加したとき、このシステムではタービン出力が７％程度増加する。このオーバロード弁４から導入された蒸気は排熱回収ボイラの再熱器を通過しないため、タービンの熱消費率は良くなる。しかも、主蒸気圧力がほとんど上昇せず、主蒸気系統の再熱回収ボイラや蒸気管の設計圧力を高くする必要がないため、経済的に蒸気タービンの過負荷運転を実現することができる。   Usually, since the output sharing of the steam turbine reheating unit 6 is about 70%, when the main steam flow rate is increased by 10% by opening the overload valve 4, the turbine output is increased by about 7% in this system. Since the steam introduced from the overload valve 4 does not pass through the reheater of the exhaust heat recovery boiler, the heat consumption rate of the turbine is improved. In addition, the main steam pressure hardly increases, and it is not necessary to increase the design pressure of the reheat recovery boiler and the steam pipe of the main steam system, so that the overload operation of the steam turbine can be realized economically.

図２は本実施の形態の特性図を示したものであり、蒸気圧力が定格点（ＶＷＯ）に到達したあと主蒸気流量を増加した場合、主蒸気圧力は定格点と比べてほとんど変化しないが、熱消費率および電気出力が増加することがわかる。   FIG. 2 is a characteristic diagram of the present embodiment. When the main steam flow rate is increased after the steam pressure reaches the rated point (VWO), the main steam pressure hardly changes compared to the rated point. It can be seen that the heat consumption rate and the electrical output increase.

（第２の実施の形態）
次に、図３を参照して本発明の第２の実施の形態について説明する。
近年の大容量コンバインドサイクル（蒸気タービン出力がおよそ１００ＭＷを越えるもの）では、主蒸気圧力が１００ｂａｒ（１０ＭＰａ）を越えて２００ｂａｒ（２０ＭＰａ）未満であることが多い。この場合、高圧タービン部のケーシングは部分二重車室になることが一般的である。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG.
In recent large-capacity combined cycles (steam turbine output exceeding approximately 100 MW), the main steam pressure is often greater than 100 bar (10 MPa) and less than 200 bar (20 MPa). In this case, the casing of the high-pressure turbine section is generally a partial double casing.

本実施の形態は、ケーシングが部分二重車室に構成された高圧タービンを採用し、オーバロード弁４を備える過負荷蒸気管Ｐ４の出口側を二重車室部の外部車室側と連通させることにより、蒸気を二重車室部と単車室部との接続部に位置する中間段落部から蒸気通路部に混入するように構成したものであり、その他の構成は図１の実施の形態の場合と同じである。   The present embodiment employs a high-pressure turbine whose casing is configured as a partial double casing, and the outlet side of an overload steam pipe P4 provided with an overload valve 4 communicates with the external casing side of the double casing. In this way, the steam is mixed into the steam passage part from the intermediate stage part located at the connection part between the double compartment part and the single compartment part, and the other construction is the embodiment of FIG. Is the same as

図４は部分二重車室に構成された蒸気タービン高圧部５の車室断面図であり、特に蒸気タービン高圧部５の二重車室部を拡大して示す図である。図４において、８は高圧外部車室、９は高圧内部車室、１０はタービン動翼、１１はタービン静翼、１２はタービンロータである。   FIG. 4 is a cross-sectional view of the casing of the steam turbine high-pressure part 5 configured in a partial double casing, and in particular, an enlarged view of the double casing of the steam turbine high-pressure part 5. In FIG. 4, 8 is a high-pressure external casing, 9 is a high-pressure internal casing, 10 is a turbine rotor blade, 11 is a turbine stationary blade, and 12 is a turbine rotor.

主蒸気加減弁２から高圧内部車室９内に導入された主蒸気Ｓ１（破線で示す）は初段動翼、静翼、…第３段動翼、静翼を通り、二重車室部と単車室部との接続部に位置する中間段落部５２に至る。   The main steam S1 (shown by a broken line) introduced from the main steam control valve 2 into the high pressure internal casing 9 passes through the first stage moving blade, the stationary blade, ... the third stage moving blade, the stationary blade, The intermediate paragraph 52 is located at the connection with the single vehicle compartment.

一方、過負荷蒸気管Ｐ４を通りオーバロード弁４から出力されて蒸気タービン高圧部５の高圧外部車室８にあけられた蒸気送り込み口５３から高圧外部車室８の外周面および高圧内部車室９の内周面間に形成された環状通路５４に送り込まれた主蒸気Ｓ２（実線で示す）は、その環状通路５４を通って前記中間段落部５２で高圧内部車室９内部を通ってきた主蒸気Ｓ１と合流し、次段落に導入される。そして最終段落の動翼、静翼を通過し排気管Ｐ２を介して再熱器に導入される。   On the other hand, the outer peripheral surface of the high-pressure external compartment 8 and the high-pressure internal compartment from the steam inlet 53 which is output from the overload valve 4 through the overload steam pipe P4 and opened in the high-pressure external compartment 8 of the steam turbine high-pressure part 5. The main steam S2 (shown by a solid line) fed into an annular passage 54 formed between the inner peripheral surfaces of the air passage 9 passes through the annular passage 54 and passes through the interior of the high-pressure internal casing 9 at the intermediate stage 52. It merges with the main steam S1 and is introduced into the next paragraph. Then, it passes through the moving blades and stationary blades in the final paragraph and is introduced into the reheater via the exhaust pipe P2.

この第２の実施の形態では、図４の蒸気タービン高圧部５の車室断面図で示したように、過負荷蒸気管Ｐ４を通りオーバロード弁４から送り込まれた蒸気Ｓ２をこの二重車室部の外部車室−内部車室間に送り込み、中間段落部５２から主蒸気Ｓ１の通路部に混入するように構成したので、外部車室８と内部車室９を貫通するスリーブが不要となるため、極めて簡単な構造で蒸気タービンの過負荷運転装置を実現することができる。   In the second embodiment, as shown in the cross-sectional view of the casing of the steam turbine high-pressure portion 5 in FIG. 4, the steam S2 fed from the overload valve 4 through the overload steam pipe P4 is supplied to the double vehicle. Since it is configured to be fed between the outer casing and the inner casing of the chamber and mixed into the passage portion of the main steam S1 from the intermediate paragraph 52, a sleeve penetrating the outer casing 8 and the inner casing 9 is unnecessary. Therefore, the steam turbine overload operation device can be realized with an extremely simple structure.

この実施の形態の特性は図５で示すように、主蒸気圧力は第１の実施の形態の特性（図２）と比較して若干上昇することは否めないが、主蒸気流量を１０％増加したときに期待できる出力の増加量は第１の実施の形態よりも大きく、図７の従来例との中間程度になる。しかし主蒸気圧力の増加は従来の特性図における８〜９％に比べて低く、２〜３％程度であり、主蒸気系統に与える影響は非常に小さい。そのためこの実施の形態でもタービンの熱消費率はほとんど低下しない。   As shown in FIG. 5, the characteristic of this embodiment is that the main steam pressure is slightly increased compared with the characteristic of the first embodiment (FIG. 2), but the main steam flow rate is increased by 10%. The amount of increase in output that can be expected is larger than that in the first embodiment, and is about the middle of the conventional example in FIG. However, the increase in the main steam pressure is lower than 8-9% in the conventional characteristic diagram, and is about 2-3%, and the influence on the main steam system is very small. Therefore, even in this embodiment, the heat consumption rate of the turbine hardly decreases.

本発明の第１の実施の形態に係る蒸気タービンの過負荷運転装置のシステム構成図。1 is a system configuration diagram of an overload operation device for a steam turbine according to a first embodiment of the present invention. 第１の実施の形態の特性図。The characteristic view of 1st Embodiment. 本発明の第２の実施の形態に係る蒸気タービンの過負荷運転装置のシステム構成図。The system block diagram of the overload operating device of the steam turbine which concerns on the 2nd Embodiment of this invention. 第２の実施の形態で採用した蒸気タービン高温部の車室断面図。FIG. 6 is a cross-sectional view of a passenger compartment of a high-temperature portion of a steam turbine employed in the second embodiment. 第２の実施の形態の特性図。The characteristic view of 2nd Embodiment. 従来技術による蒸気タービンの過負荷運転装置のシステム構成図。The system block diagram of the overload operating device of the steam turbine by a prior art. 従来技術の特性図。FIG.

符号の説明Explanation of symbols

１…主蒸気止め弁、２…主蒸気加減弁、３…再熱蒸気弁、４…オーバロード弁、５…蒸気タービン高圧部、５１…第１段出口部、５２…中間段落部、５３…蒸気送り込み口、５４…環状通路、６…蒸気タービン再熱部、７…復水器、８…高圧外部車室、９…高圧内部車室、１０…タービン動翼、１１…タービン静翼、１２…タービンロータ、１３…排熱回収ボイラ、１４…発電機、Ｐ１…主蒸気配管、Ｐ２…排気管、Ｐ３…再熱管、Ｐ４…過負荷蒸気管。

DESCRIPTION OF SYMBOLS 1 ... Main steam stop valve, 2 ... Main steam control valve, 3 ... Reheat steam valve, 4 ... Overload valve, 5 ... Steam turbine high pressure part, 51 ... 1st stage exit part, 52 ... Middle paragraph part, 53 ... Steam inlet 54, annular passage, 6 steam turbine reheat section, 7 condenser, 8 high pressure external casing, 9 high pressure internal casing, 10 turbine blade, 11 turbine stationary blade, 12 DESCRIPTION OF SYMBOLS ... Turbine rotor, 13 ... Waste heat recovery boiler, 14 ... Generator, P1 ... Main steam piping, P2 ... Exhaust pipe, P3 ... Reheat pipe, P4 ... Overload steam pipe.

Claims (5)

蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入した蒸気タービンにおいて、
前記主蒸気加減弁の入口側から分岐して前記蒸気タービン再熱部の入口側にオーバロード弁を介して連通させたことを特徴とする蒸気タービン過負荷運転装置。 It has a steam turbine high-pressure part and a steam turbine reheat part, high-pressure steam is introduced into the steam turbine high-pressure part via the main steam control valve, and reheat steam is introduced into the steam turbine reheat part via the reheat steam valve In the steam turbine,
A steam turbine overload operation device that branches from the inlet side of the main steam control valve and communicates with the inlet side of the steam turbine reheat section via an overload valve. 蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入した蒸気タービンにおいて、
前記主蒸気加減弁の入口側から分岐して前記蒸気タービン高圧部の中間段落にオーバロード弁を介して連通させたことを特徴とする蒸気タービンの過負荷運転装置。 It has a steam turbine high-pressure part and a steam turbine reheat part, high-pressure steam is introduced into the steam turbine high-pressure part via the main steam control valve, and reheat steam is introduced into the steam turbine reheat part via the reheat steam valve In the steam turbine,
An overload operation device for a steam turbine, which branches from an inlet side of the main steam control valve and communicates with an intermediate stage of the high pressure portion of the steam turbine via an overload valve. 前記蒸気タービン高圧部は部分二重車室部を備え、前記オーバロード弁の出口側を二重車室部の外部車室側と連通させ、蒸気を二重車室部と単車室部との接続部に位置する中間段落部から蒸気通路部に混入するように構成したことを特徴とする請求項２記載の蒸気タービンの過負荷運転装置。   The steam turbine high-pressure part has a partial double compartment part, the outlet side of the overload valve communicates with the external compartment side of the double compartment part, and steam is connected between the double compartment part and the single compartment part. The overload operation device for a steam turbine according to claim 2, wherein the steam turbine portion is mixed from an intermediate stage portion located in the connection portion. 蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入して蒸気タービンの過負荷運転を行うようにした運転方法において、
前記主蒸気加減弁の入口側と前記蒸気タービン再熱部の入口側とを連通するオーバロード弁を、主蒸気圧力が定格点に到達し、かつ主蒸気加減弁の開度が全開のとき、オーバロード弁を開いて主蒸気を蒸気タービン再熱部の入口に導入することを特徴とする蒸気タービンの過負荷運転方法。 A steam turbine high-pressure part and a steam turbine reheat part are provided, high-pressure steam is introduced into the steam turbine high-pressure part via the main steam control valve, and reheat steam is introduced into the steam turbine reheat part via the reheat steam valve. In the operation method for overloading the steam turbine,
An overload valve that communicates the inlet side of the main steam control valve and the inlet side of the steam turbine reheat unit, when the main steam pressure reaches the rated point and the opening of the main steam control valve is fully open, An overload operation method for a steam turbine, wherein an overload valve is opened to introduce main steam into an inlet of a steam turbine reheat section. 蒸気タービン高圧部および蒸気タービン再熱部を備え、高圧蒸気を主蒸気加減弁を介して蒸気タービン高圧部に導入し、再熱蒸気を再熱蒸気弁を介して蒸気タービン再熱部に導入して蒸気タービンの過負荷運転を行うようにした運転方法において、
前記主蒸気加減弁の入口側と前記蒸気タービン再熱部の入口側とを連通するオーバロード弁を、主蒸気圧力が定格点に到達し、かつ主蒸気加減弁の開度が全開のとき、オーバロード弁を開いて主蒸気を高圧中間段落に導入することを特徴とする蒸気タービンの過負荷運転方法。

A steam turbine high-pressure part and a steam turbine reheat part are provided, high-pressure steam is introduced into the steam turbine high-pressure part via the main steam control valve, and reheat steam is introduced into the steam turbine reheat part via the reheat steam valve. In the operation method for overloading the steam turbine,
An overload valve that communicates the inlet side of the main steam control valve and the inlet side of the steam turbine reheat unit, when the main steam pressure reaches the rated point and the opening of the main steam control valve is fully open, An overload operation method for a steam turbine, wherein an overload valve is opened to introduce main steam into a high-pressure intermediate stage.

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JP2013502538A (en) * 2009-09-22 2013-01-24 シーメンス アクティエンゲゼルシャフト Power plant system with overload control valve
FR2962763A1 (en) * 2010-07-14 2012-01-20 Gen Electric SYSTEM FOR ADJUSTING FLOW IN A STEAM TURBINE
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