JP2003013702A - Device and method for controlling extraction steam pressure of main engine turbine - Google Patents
Device and method for controlling extraction steam pressure of main engine turbineInfo
- Publication number
- JP2003013702A JP2003013702A JP2001200597A JP2001200597A JP2003013702A JP 2003013702 A JP2003013702 A JP 2003013702A JP 2001200597 A JP2001200597 A JP 2001200597A JP 2001200597 A JP2001200597 A JP 2001200597A JP 2003013702 A JP2003013702 A JP 2003013702A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- steam
- extraction
- main engine
- engine turbine
- 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.)
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Links
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- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
- Control Of Turbines (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本願発明は、船舶における蒸
気タービン推進プラントにおいて、主機タービンからの
抽気蒸気をＬＰＳＧ［Low Pressure Steam Generator］
（以下「低圧蒸気発生器」という）の加熱蒸気として利
用する場合に、主機タービンの抽気蒸気圧力変化に応じ
て加熱蒸気圧力を制御する装置とその方法に関するもの
である。TECHNICAL FIELD The present invention relates to LPSG [Low Pressure Steam Generator] for extracting steam extracted from a main turbine in a steam turbine propulsion plant for a ship.
The present invention relates to an apparatus and a method for controlling a heating steam pressure according to a change in extraction steam pressure of a main engine turbine when used as heating steam (hereinafter referred to as “low pressure steam generator”).
【０００２】[0002]
【従来の技術】従来から、船舶における蒸気タービン推
進プラントにおいては、主機タービンからの抽気蒸気を
低圧蒸気発生器の加熱蒸気として利用している。この低
圧蒸気発生器は、蒸気タービンプラントで発生する蒸気
を加熱用蒸気として利用し、他のプラント機器や船内燃
料ヒータ等で使用する蒸気を発生させる装置である。2. Description of the Related Art Conventionally, in steam turbine propulsion plants for ships, extracted steam from a main engine turbine is used as heating steam for a low pressure steam generator. This low-pressure steam generator is a device that uses steam generated in a steam turbine plant as heating steam to generate steam for use in other plant equipment, onboard fuel heaters, and the like.
【０００３】このような低圧蒸気発生器を採用する場
合、一般的に、その定格蒸気圧力を得る加熱蒸気の最低
圧力を発生蒸気圧力よりも約６kg/cm2程度高くしてお
り、この加熱蒸気圧力のコントロールは一定圧力制御に
よって行われている。When such a low-pressure steam generator is adopted, generally, the minimum pressure of the heating steam for obtaining the rated steam pressure is set to about 6 kg / cm 2 higher than the generated steam pressure. The pressure is controlled by constant pressure control.
【０００４】図３は、従来の低圧蒸気発生器使用時にお
ける抽気蒸気圧力の制御装置の一例を示す系統図であ
り、図４はこの制御装置による制御方法を示す線図であ
る。なお、以下の説明では、低圧蒸気発生器において発
生させる定格蒸気圧力を８kg/cm2とし、この蒸気圧力を
得るための加熱蒸気圧力として前記６kg/cm2を加えた１
４kg/cm2とした例を説明する。FIG. 3 is a system diagram showing an example of a control device for the extracted steam pressure when a conventional low-pressure steam generator is used, and FIG. 4 is a diagram showing a control method by this control device. In the following description, the rated steam pressure generated in the low-pressure steam generator is set to 8 kg / cm 2, and 6 kg / cm 2 is added as the heating steam pressure for obtaining this steam pressure.
An example of 4 kg / cm 2 will be described.
【０００５】図３に示すように、低圧蒸気発生器５１に
加熱蒸気を供給する経路として、メインボイラからの供
給路５２と、主機タービンの抽気口５３からの抽気路５
４が設けられている。供給路５２には、メインボイラか
ら供給される６０kg/cm2の圧力を補助蒸気１４kg/cm2の
二次側蒸気圧力に落とす圧力制御弁５５が設けられてい
る。５６は、圧力制御弁５５の出口側の圧力を検出する
圧力検出器であり、この圧力検出器５６からの信号で圧
力制御弁５５の二次側圧力が一定に保たれている。As shown in FIG. 3, as a path for supplying the heating steam to the low pressure steam generator 51, a supply path 52 from the main boiler and an extraction path 5 from an extraction port 53 of the main engine turbine are provided.
4 are provided. The supply path 52 is provided with a pressure control valve 55 for reducing the pressure of 60 kg / cm 2 supplied from the main boiler to the secondary side steam pressure of 14 kg / cm 2 of auxiliary steam. Reference numeral 56 is a pressure detector that detects the pressure on the outlet side of the pressure control valve 55, and the secondary pressure of the pressure control valve 55 is kept constant by a signal from this pressure detector 56.
【０００６】一方、抽気路５４には、主機タービンの抽
気口５３に設けられた圧力センサ５７で検出した抽気蒸
気圧力が１６kg/cm2以上になったら開放され、１５kg/c
m2以下になったら閉鎖される抽気弁５８が設けられてい
る。この抽気弁５８は、いわゆる電磁弁である。また、
この抽気路５４には、圧力制御弁５５側からの蒸気が抽
気口５３側へ流れないようにする逆止弁５９が設けられ
ている。なお、このようにメインボイラからの蒸気圧力
を制御する圧力制御弁５５の設定圧力である１４kg/cm2
と、抽気弁５８の開閉圧力である１６kg/cm2／１５kg/c
m2との間に１〜２kg/cm2の差圧を設けているのは、内部
圧力損失や製作誤差等による設定圧力の誤差を吸収し、
弁５５，５８の開閉時にハンチング現象を生じないよう
にするためである。On the other hand, the extraction passage 54 is opened when the extraction steam pressure detected by the pressure sensor 57 provided at the extraction port 53 of the main engine turbine becomes 16 kg / cm 2 or more, and 15 kg / c.
A bleed valve 58 is provided which is closed when the pressure drops below m 2 . The bleed valve 58 is a so-called solenoid valve. Also,
The bleed passage 54 is provided with a check valve 59 that prevents steam from the pressure control valve 55 side from flowing to the bleed port 53 side. The pressure set by the pressure control valve 55 for controlling the steam pressure from the main boiler is 14 kg / cm 2
When a closing pressure of the bleed valve 58 16kg / cm 2 / 15kg / c
The difference in pressure between 1 and 2 kg / cm 2 is provided between m 2 and the pressure difference due to internal pressure loss and manufacturing error.
This is to prevent the hunting phenomenon from occurring when the valves 55 and 58 are opened and closed.
【０００７】低圧蒸気発生器５１へ供給される蒸気の供
給路６０には、この低圧蒸気発生器５１で発生させる蒸
気圧力が８kg/cm2となるように蒸気流量を制御する流量
制御弁６１が設けられている。この流量制御弁６１に
は、低圧蒸気発生器５１で発生させている蒸気圧力が圧
力検出器６２によってフィードバックされている。この
流量制御弁６１によって調整された蒸気流量により低圧
蒸気発生器５１で定格蒸気圧力８kg/cm2の蒸気が発生さ
せられている。A flow control valve 61 for controlling the flow rate of steam so that the steam pressure generated by the low pressure steam generator 51 is 8 kg / cm 2 is provided in the supply path 60 of the steam supplied to the low pressure steam generator 51. It is provided. The pressure detector 62 feeds back the steam pressure generated by the low-pressure steam generator 51 to the flow rate control valve 61. With the steam flow rate adjusted by the flow rate control valve 61, the low-pressure steam generator 51 is generating steam with a rated steam pressure of 8 kg / cm 2 .
【０００８】図４に示す実線(a) は抽気蒸気圧力であ
り、点線(b) は補助蒸気圧力であり、１点鎖線(c) は低
圧蒸気発生器発生蒸気圧力である。前記したように構成
された抽気蒸気圧力制御装置６３による制御は、主機タ
ービン抽気蒸気圧力が抽気弁５８の開放圧力である１６
kg/cm2以下の場合には、メインボイラからの蒸気が圧力
制御弁５５で１４kg/cm2に減圧され、この蒸気が流量制
御弁６１で流量調整されて低圧蒸気発生器５１に供給さ
れている。この時、供給路５２の蒸気は逆止弁５９によ
って抽気弁５８側へ流れることはない。この状態で主機
タービン抽気蒸気圧力が１６kg/cm2に達すると、圧力セ
ンサ５７が抽気弁５８を開放させるので、抽気路５４か
ら逆止弁５９を介して供給路６０へ抽気蒸気が供給され
る。その後は、主機タービンの抽気蒸気圧力が１５kg/c
m2に下がるまで、抽気路５４からの抽気蒸気が低圧蒸気
発生器５１に供給される。The solid line (a) shown in FIG. 4 is the extraction steam pressure, the dotted line (b) is the auxiliary steam pressure, and the alternate long and short dash line (c) is the low pressure steam generator generated steam pressure. In the control by the extraction steam pressure control device 63 configured as described above, the main engine turbine extraction steam pressure is the opening pressure of the extraction valve 58.
In the case of kg / cm 2 or less, the pressure of the steam from the main boiler is reduced to 14 kg / cm 2 by the pressure control valve 55, the flow rate of this steam is adjusted by the flow rate control valve 61, and the low pressure steam generator 51 is supplied. There is. At this time, the steam in the supply passage 52 does not flow to the extraction valve 58 side by the check valve 59. When the main engine turbine extraction steam pressure reaches 16 kg / cm 2 in this state, the pressure sensor 57 opens the extraction valve 58, so that extraction steam is supplied from the extraction path 54 to the supply path 60 via the check valve 59. . After that, the extraction steam pressure of the main engine turbine is 15kg / c
Extracted steam from the extraction passage 54 is supplied to the low-pressure steam generator 51 until the pressure falls to m 2 .
【０００９】このように低圧蒸気発生器５１の加熱蒸気
源として主機タービンの抽気蒸気を利用するために、主
機タービンの設計においては、あらかじめ主機タービン
負荷に対する抽気蒸気抽出位置、つまり主機タービンの
抽気段数を考慮し、低圧蒸気発生器５１へ供給する蒸気
圧力が常に１４kg/cm2以上となるような抽気段から抽気
して一定圧力制御することによって、低圧蒸気発生器５
１において発生させる蒸気圧力が常に８kg/cm2となるよ
うに設計されている。つまり、主機タービンの運転状態
に関わらず、常に、船内で利用する定格蒸気量を発生さ
せるように構成されている。In order to use the extracted steam of the main engine turbine as the heating steam source of the low-pressure steam generator 51 in this manner, in the design of the main engine turbine, the extraction steam extraction position with respect to the main engine turbine load, that is, the number of extraction stages of the main engine turbine is preliminarily set. In consideration of the above, the low-pressure steam generator 5 is controlled by extracting the steam from the extraction stage so that the steam pressure supplied to the low-pressure steam generator 51 is always 14 kg / cm 2 or more and controlling the constant pressure.
It is designed so that the steam pressure generated in 1 is always 8 kg / cm 2 . That is, it is configured to always generate the rated steam amount to be used onboard the ship, regardless of the operating state of the main engine turbine.
【００１０】なお、この種の従来技術として、特開昭５
５−１０１７０８号公報記載の抽気タービンの抽気圧力
制御方式があるが、この発明は、本願発明のように、主
機タービンの抽気蒸気圧力変化に応じて低圧蒸気発生器
の加熱蒸気圧力を変化させることにより、広い範囲で主
機タービンの抽気蒸気を低圧蒸気発生器の加熱蒸気とし
て利用するようなものではない。As a conventional technique of this kind, Japanese Patent Laid-Open No.
Although there is an extraction pressure control system for an extraction turbine described in Japanese Patent Laid-Open No. 5-101708, the present invention changes the heating steam pressure of the low-pressure steam generator according to the change in extraction steam pressure of the main engine turbine as in the present invention. Therefore, the extracted steam of the main engine turbine is not used as the heating steam of the low-pressure steam generator in a wide range.
【００１１】[0011]
【発明が解決しようとする課題】しかしながら、前記し
たように低圧蒸気発生器へ供給する蒸気圧力を一定圧力
制御した場合、圧力制御弁５５の設定圧力が１４kg/cm2
に固定されているので、主機タービン抽気蒸気圧力が１
６kg/cm2になるまでの低負荷時（例えば、主機タービン
負荷が７０〜８０％の運転状態まで）には、主機タービ
ンの抽気蒸気を使用することなくメインボイラからの蒸
気を使用することとなり、主機タービン負荷が８０〜１
００％の範囲でのみ抽気蒸気を利用することとなる。However, when the steam pressure supplied to the low-pressure steam generator is controlled to a constant pressure as described above, the set pressure of the pressure control valve 55 is 14 kg / cm 2
The main engine turbine extraction steam pressure is 1 because it is fixed at
When the load is low up to 6 kg / cm 2 (for example, the operating condition of the main turbine load is 70 to 80%), the steam from the main boiler is used without using the extracted steam of the main turbine. , Main engine turbine load is 80-1
The extracted steam will be used only in the range of 00%.
【００１２】したがって、この場合には、多くの補助蒸
気を圧力制御弁５５で６０kg/cm2から１４kg/cm2に落と
して使用することとなるため、高い熱エネルギーを無駄
にすることになり、蒸気タービンプラントとしての効率
が悪化する。Accordingly, in this case, because that would be used by dropping a number of auxiliary steam from 60 kg / cm 2 with a pressure control valve 55 to 14kg / cm 2, results in wasting high thermal energy, The efficiency as a steam turbine plant deteriorates.
【００１３】一方、近年、主機タービンの５０％以上の
出力状態で、この主機タービンの抽気蒸気を低圧蒸気発
生器５１の加熱蒸気として利用したいという要求があ
る。しかしながら、上述した従来の方法では常に一定圧
力制御を行うので、主機タービンの５０％負荷付近の低
負荷運転時に抽気蒸気を利用しようとすると、必要とす
る蒸気圧力を得るためには主機タービンの抽気口の段数
を上げる必要がある。すなわち、１００％負荷でかなり
高い圧力を発生するようにタービンを設計して、低負荷
運転時でも必要抽気圧力を得ることができるように蒸気
タービンプラントを設計しなければならなくなる。On the other hand, in recent years, there is a demand to utilize the extracted steam of the main engine turbine as the heating steam for the low pressure steam generator 51 in the output state of 50% or more of the main engine turbine. However, since the constant pressure control is always performed in the above-described conventional method, when attempting to use the extracted steam during low load operation near the 50% load of the main turbine, it is necessary to extract the main turbine to obtain the required steam pressure. It is necessary to increase the number of steps in the mouth. That is, the turbine must be designed to generate a considerably high pressure at 100% load, and the steam turbine plant must be designed to obtain the required extraction pressure even at low load operation.
【００１４】しかし、このように主機タービンの抽気段
数をより高圧段側にして常に高圧蒸気を抽気するように
した場合、高圧蒸気を抽気してしまうので主機タービン
効率上得策ではない上、抽気蒸気を利用できる主機ター
ビン負荷範囲が高圧段側の限られた範囲となり狭くなっ
てしまう。However, in the case where the extraction stage number of the main engine turbine is set to the higher pressure side so that the high pressure steam is always extracted, the high pressure steam is extracted, which is not a good measure for the efficiency of the main engine turbine. The load range of the main engine turbine that can utilize is limited to a limited range on the high pressure stage side and becomes narrow.
【００１５】また、仮に、低圧蒸気発生器の圧力制御弁
へ供給する加熱蒸気の圧力を下げると主機タービンの抽
気蒸気利用範囲は広がるが、この場合には加熱蒸気が常
に低い蒸気圧力となってしまい、主機タービンの通常運
転時に低圧蒸気発生器で定格蒸気圧力を得ることができ
なくなる。Further, if the pressure of the heating steam supplied to the pressure control valve of the low-pressure steam generator is lowered, the extraction steam utilization range of the main engine turbine is expanded, but in this case, the heating steam always has a low steam pressure. As a result, the rated steam pressure cannot be obtained by the low pressure steam generator during the normal operation of the main engine turbine.
【００１６】そこで、本願発明は、主機タービンの低負
荷時においても、この主機タービンの負荷に応じて抽気
蒸気を低圧蒸気発生器の加熱蒸気として使用することが
できる抽気蒸気圧力の制御方法を提供することを目的と
する。Therefore, the present invention provides a method for controlling the extraction steam pressure, which enables the extraction steam to be used as the heating steam for the low-pressure steam generator according to the load of the main engine turbine even when the load of the main engine turbine is low. The purpose is to do.
【００１７】[0017]
【課題を解決するための手段】前記課題を解決するため
に、本願発明の制御装置は、補助蒸気を低圧蒸気発生器
に供給する供給路と、主機タービンの抽気蒸気を低圧蒸
気発生器に供給する抽気路とを設け、前記供給路に、補
助蒸気の圧力を所定の二次側蒸気圧力に減圧する圧力制
御弁を設け、前記抽気路に、主機タービン抽気蒸気圧力
が所定圧力以上になったら開放し、所定圧力以下になっ
たら閉鎖する抽気弁を設け、該抽気路と前記圧力制御弁
との間に、該抽気路の蒸気圧力に応じて圧力制御弁の二
次側蒸気圧力を抽気弁の開閉圧力よりも所定圧力だけ低
い圧力に設定する制御装置を設けている。このように蒸
気プラントの主機タービン抽気蒸気を低圧蒸気発生器の
加熱蒸気として使用する場合に、補助蒸気の蒸気圧力を
抽気蒸気圧力に応じて低く設定することで、主機タービ
ン負荷のより低い範囲で抽気蒸気を低圧蒸気発生器の加
熱蒸気として利用できるので、補助蒸気を使用する範囲
が狭まり、エネルギーを無駄にする運転範囲が狭くなっ
てプラント効率を向上させることができる。In order to solve the above problems, the control device of the present invention supplies a supply path for supplying auxiliary steam to a low pressure steam generator and an extraction steam of a main turbine to the low pressure steam generator. A pressure control valve for reducing the pressure of the auxiliary steam to a predetermined secondary side steam pressure in the supply path, and in the extraction path, when the main turbine extraction steam pressure becomes equal to or higher than a predetermined pressure. A bleed valve that opens and closes when the pressure falls below a predetermined pressure is provided between the bleed passage and the pressure control valve, and the secondary side steam pressure of the pressure control valve is bleed according to the steam pressure in the bleed passage. A control device for setting a pressure lower than the opening / closing pressure by a predetermined pressure is provided. In this way, when the main turbine extraction steam of the steam plant is used as the heating steam of the low-pressure steam generator, by setting the steam pressure of the auxiliary steam to a low value in accordance with the extraction steam pressure, in the lower range of the main turbine load. Since the extracted steam can be used as heating steam for the low-pressure steam generator, the range in which the auxiliary steam is used is narrowed, the operating range in which energy is wasted is narrowed, and plant efficiency can be improved.
【００１８】前記圧力制御弁の二次側圧力を検出する圧
力検出器を設け、抽気路の蒸気圧力を検出する蒸気圧力
検出器を設け、該蒸気圧力検出器の検出値と前記圧力検
出器の検出値とを比較して圧力制御弁の二次側蒸気圧力
を抽気路の蒸気圧力よりも所定圧力だけ低い設定圧力に
変更する制御回路を制御装置に設けることにより、制御
装置で圧力制御弁の二次側圧力を抽気路の圧力よりも所
定圧力だけ低い圧力に可変制御することが安定してでき
るので、抽気蒸気圧力が変化しても圧力制御弁と抽気弁
との間でハンチング現象を生じることなく安定した運転
を行うことができる。A pressure detector for detecting the secondary pressure of the pressure control valve is provided, and a steam pressure detector for detecting the steam pressure in the extraction passage is provided. The detected value of the steam pressure detector and the pressure detector By providing the control device with a control circuit that compares the detected value with the secondary side steam pressure of the pressure control valve to a set pressure that is lower than the steam pressure of the extraction passage by a predetermined pressure, the control device can control the pressure control valve Since the secondary pressure can be variably controlled to a pressure lower than the pressure in the extraction passage by a predetermined pressure, hunting phenomenon occurs between the pressure control valve and the extraction valve even if the extraction steam pressure changes. Stable operation can be performed without
【００１９】一方、本願発明の制御方法は、低圧蒸気発
生器の加熱蒸気として、主機タービンの抽気蒸気圧力が
低い時は補助蒸気を使用し、主機タービンの抽気蒸気圧
力が上昇して所定圧力に達したら前記補助蒸気の設定圧
力を抽気蒸気圧力よりも低い圧力に設定して主機タービ
ン負荷の低い範囲で抽気蒸気を低圧蒸気発生器の加熱蒸
気として利用できるようにしている。このように抽気蒸
気圧力が所定の圧力に達したら補助蒸気の設定圧力を抽
気蒸気圧力よりも低くするような可変圧力とすることに
より、主機タービンの抽気蒸気を主機タービン負荷のよ
り広い範囲で低圧蒸気発生器の加熱蒸気として利用でき
るので、補助蒸気を使用する範囲が狭まり、エネルギー
を無駄にする運転範囲が狭くなってプラント効率を向上
させることができる。On the other hand, in the control method of the present invention, auxiliary steam is used as the heating steam for the low-pressure steam generator when the extraction steam pressure of the main engine turbine is low, and the extraction steam pressure of the main engine turbine rises to a predetermined pressure. When it reaches, the set pressure of the auxiliary steam is set to a pressure lower than the extracted steam pressure so that the extracted steam can be used as the heating steam of the low-pressure steam generator in a low range of the main turbine load. In this way, by setting the variable pressure so that the set pressure of the auxiliary steam becomes lower than the extracted steam pressure when the extracted steam pressure reaches a predetermined pressure, the extracted steam of the main engine turbine is reduced to a low pressure in a wider range of the main engine turbine load. Since it can be used as heating steam for the steam generator, the range in which the auxiliary steam is used is narrowed, the operating range in which energy is wasted is narrowed, and plant efficiency can be improved.
【００２０】また、補助蒸気の設定圧力を抽気蒸気圧力
よりも低い圧力に設定した後、補助蒸気の設定圧力と抽
気蒸気圧力との差圧を保ちながら主機タービンの抽気蒸
気圧力変化に応じて補助蒸気の設定圧力を変化させるよ
うにすれば、抽気蒸気圧力が変化しても常に差圧を保っ
た状態の補助蒸気圧力とすることができるので、抽気蒸
気圧力に差圧以上の大きな変化を生じても補助蒸気を迅
速に供給するようにできる。After the set pressure of the auxiliary steam is set to a pressure lower than the extracted steam pressure, the auxiliary pressure is changed according to the extracted steam pressure of the main turbine while maintaining the differential pressure between the auxiliary steam set pressure and the extracted steam pressure. If the set steam pressure is changed, the auxiliary steam pressure can be maintained at a constant differential pressure even if the extracted steam pressure changes.Therefore, the extracted steam pressure changes greatly beyond the differential pressure. However, the auxiliary steam can be supplied quickly.
【００２１】さらに、抽気蒸気の利用開始設定圧力を、
主機タービンのほぼ５０％負荷状態の蒸気圧力とすれ
ば、抽気蒸気を使用する範囲が５０〜１００％になり、
主機タービンの負荷がほぼ５０％の低い状態では低圧蒸
気発生器の加熱蒸気としての圧力は低いが、主機タービ
ンの通常運転状態では定格圧力を確保することができ、
主機タービンの広い運転状態で抽気蒸気を利用すること
ができる。Further, the set pressure for starting the utilization of extracted steam is
If the steam pressure of the main turbine is about 50% load, the range of using extracted steam is 50 to 100%,
The pressure of the low-pressure steam generator as the heating steam is low when the load of the main engine turbine is low at about 50%, but the rated pressure can be secured in the normal operating state of the main engine turbine.
The extracted steam can be used in a wide range of operating conditions of the main turbine.
【００２２】また、抽気蒸気圧力が上昇して所定の設定
圧力に達したら補助蒸気の圧力を徐々に下げて抽気蒸気
圧力よりも低い圧力に設定し、抽気蒸気圧力が下降して
所定の設定圧力に達したら補助蒸気の圧力を徐々に上げ
て定格蒸気圧力に設定すれば、圧力制御弁からの補助蒸
気使用時と、主機タービンからの抽気蒸気利用時との切
り替え時に急激な圧力変化を生じることなくスムーズに
切り替えることができる。When the extracted steam pressure rises to reach a predetermined set pressure, the pressure of the auxiliary steam is gradually reduced to a pressure lower than the extracted steam pressure, and the extracted steam pressure is lowered to reach the predetermined set pressure. If the auxiliary steam pressure is gradually increased to the rated steam pressure when the temperature reaches the set point, a sudden pressure change will occur when switching between using the auxiliary steam from the pressure control valve and using the extracted steam from the main engine turbine. You can switch smoothly without.
【００２３】さらに、補助蒸気の設定圧力を、抽気蒸気
圧力よりも１〜２kg/cm2低く設定することにより、補助
蒸気と抽気蒸気との切替え圧力近辺で弁がハンチング現
象を起こすのを防止して安定した切り替えを行うことが
できる。Furthermore, by setting the set pressure of the auxiliary steam to be lower than the extracted steam pressure by 1 to 2 kg / cm 2, it is possible to prevent the valve from causing a hunting phenomenon in the vicinity of the switching pressure between the auxiliary steam and the extracted steam. And stable switching can be performed.
【００２４】[0024]
【発明の実施の形態】以下、本願発明の一実施形態を図
面に基づいて説明する。図１は本願発明の一実施形態を
示す抽気蒸気圧力の制御装置の系統図であり、図２はこ
の制御装置による制御方法を示す線図である。なお、こ
の実施形態では、低圧蒸気発生器において発生させる定
格蒸気圧力を８kg/cm2とし、メインボイラからの補助蒸
気の二次圧を抽気蒸気圧力に応じて変化させる例に基い
て説明する。また、この実施形態における各設定圧力は
一例である。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a system diagram of a control apparatus for extraction steam pressure showing an embodiment of the present invention, and FIG. 2 is a diagram showing a control method by this control apparatus. In this embodiment, the rated steam pressure generated in the low-pressure steam generator is set to 8 kg / cm 2, and the secondary pressure of the auxiliary steam from the main boiler is changed according to the extracted steam pressure. Moreover, each set pressure in this embodiment is an example.
【００２５】図１に示すように、低圧蒸気発生器１に蒸
気を供給する経路として、メインボイラ（図示略）から
の供給路２と、主機タービンの抽気口３からの抽気路４
とが設けられており、供給路２には、メインボイラから
供給される一次側圧力が６０kg/cm2の補助蒸気を、二次
側圧力が１１．５〜１４kg/cm2の範囲の設定圧力に落と
す圧力制御弁５が設けられている。この圧力制御弁５
は、制御装置６からの信号によって二次側設定圧力を可
変にできるものであり、圧力制御弁５の二次側圧力（出
口側圧力）を圧力検出器７で検出して制御装置６で制御
するようにしている。As shown in FIG. 1, as a path for supplying steam to the low-pressure steam generator 1, a supply path 2 from a main boiler (not shown) and an extraction path 4 from an extraction port 3 of a main engine turbine.
Doo is provided, in the supply channel 2, the primary side pressure auxiliary steam 60 kg / cm 2 is supplied from the main boiler, the set pressure range the secondary side pressure is 11.5~14kg / cm 2 A pressure control valve 5 for dropping the pressure is provided. This pressure control valve 5
Is capable of varying the secondary side set pressure by a signal from the control device 6, and detects the secondary side pressure (outlet side pressure) of the pressure control valve 5 by the pressure detector 7 and controls by the control device 6. I am trying to do it.
【００２６】一方、主機タービン抽気口３には、抽気蒸
気圧力の圧力を検出する抽気圧力検出器８が設けられて
おり、この抽気圧力検出器８で検出された圧力は、常に
前記制御装置６で監視されている。また、この抽気口３
には圧力センサ１０が設けられており、この圧力センサ
１０で検出した抽気蒸気圧力が所定圧力になると開閉す
る抽気弁９が抽気路４に設けられている。この抽気弁９
は電磁弁であり、圧力センサ１０で検出した抽気蒸気圧
力が１３．５kg/cm2以上になったら開放され、１２．５
kg/cm2以下になったら閉鎖されるように設定されてい
る。さらに、この抽気弁９の圧力制御弁５側には、圧力
制御弁５側の蒸気が抽気口３側へ流れないようにする逆
止弁１１が設けられている。On the other hand, the main turbine turbine bleed port 3 is provided with a bleed air pressure detector 8 for detecting the pressure of the bleed steam pressure, and the pressure detected by the bleed air pressure detector 8 is always the control device 6 described above. Is being monitored by. Also, this extraction port 3
A pressure sensor 10 is provided in the exhaust passage 4, and an extraction valve 9 that opens and closes when the extraction steam pressure detected by the pressure sensor 10 reaches a predetermined pressure is provided in the extraction passage 4. This bleed valve 9
Is a solenoid valve, which is opened when the extraction steam pressure detected by the pressure sensor 10 becomes 13.5 kg / cm 2 or more, and 12.5 kg / cm 2 is released.
It is set so that it will be closed when it becomes less than kg / cm 2 . Further, on the pressure control valve 5 side of the bleed valve 9, a check valve 11 is provided to prevent steam on the pressure control valve 5 side from flowing to the bleed port 3 side.
【００２７】なお、この実施形態の場合、メインボイラ
からの補助蒸気圧力を制御する圧力制御弁５の設定圧力
である１４〜１１．５kg/cm2と、抽気弁９の開閉圧力で
ある１３．５kg/cm2／１２．５kg/cm2との間に約１kg/c
m2（２kg/cm2でも可）の圧力差を設けることにより、管
内の圧力損失や弁の製作誤差等による設定圧力誤差の吸
収と、弁開閉時のハンチング現象防止を図っている。In the case of this embodiment, the set pressure of the pressure control valve 5 for controlling the auxiliary steam pressure from the main boiler is 14 to 11.5 kg / cm 2 and the opening / closing pressure of the extraction valve 9 is 13. about 1 kg / c between 5kg / cm 2 /12.5kg/cm 2
By providing a pressure difference of m 2 (2 kg / cm 2 is also possible), it is possible to absorb the set pressure error due to the pressure loss inside the pipe and the manufacturing error of the valve, and to prevent the hunting phenomenon when opening and closing the valve.
【００２８】一方、低圧蒸気発生器１への蒸気供給路１
２には、供給される蒸気の流量制御弁１３が設けられて
いる。この流量制御弁１３によって、低圧蒸気発生器１
で発生させる蒸気圧力が、この実施形態では８kg/cm2と
なるように蒸気供給路１２から供給される蒸気流量が制
御されている。この流量制御弁１３には、低圧蒸気発生
器１で発生させている蒸気圧力を検出する圧力検出器１
４からの信号がフィードバックされている。なお、この
流量制御弁１３は、蒸気流量の上限を制御するものであ
り、低圧蒸気発生器１で発生させる蒸気圧力が８kg/cm2
以下の場合には全開状態となる。On the other hand, the steam supply path 1 to the low pressure steam generator 1
2 is provided with a flow rate control valve 13 for the supplied steam. With this flow control valve 13, the low-pressure steam generator 1
The flow rate of the steam supplied from the steam supply passage 12 is controlled so that the steam pressure generated in step 2 is 8 kg / cm 2 in this embodiment. The flow rate control valve 13 includes a pressure detector 1 for detecting the steam pressure generated by the low pressure steam generator 1.
The signal from 4 is fed back. The flow control valve 13 controls the upper limit of the steam flow rate, and the steam pressure generated by the low-pressure steam generator 1 is 8 kg / cm 2
In the following cases, it will be in a fully open state.
【００２９】図２に示す実線(a) は抽気蒸気圧力であ
り、点線(b) は補助蒸気圧力であり、１点鎖線(c) は低
圧蒸気発生器発生蒸気圧力である。図２に基いて、前記
したように構成された抽気蒸気圧力制御装置１５による
制御方法を説明する。主機タービン側の抽気蒸気圧力
は、常に抽気圧力検出器８で検出されて制御装置６に入
力されている。この抽気蒸気圧力が、抽気弁９の開放圧
力である１３．５kg/cm2以下の約１２kg/cm2になるまで
は、メインボイラから供給される補助蒸気が圧力制御弁
５で１４kg/cm2に減圧されて供給路２から低圧蒸気発生
器１へ供給される。この供給路２から供給される蒸気
は、蒸気供給路１２に設けられた流量制御弁１３によっ
て、低圧蒸気発生器１で８kg/cm2の蒸気を発生させるこ
とができる流量に制御されて低圧蒸気発生器１に供給さ
れている。この時、供給路２の蒸気は逆止弁１１によっ
て抽気弁９側へ流れることはない。The solid line (a) shown in FIG. 2 is the extraction steam pressure, the dotted line (b) is the auxiliary steam pressure, and the alternate long and short dash line (c) is the low pressure steam generator generated steam pressure. A control method by the extraction steam pressure control device 15 configured as described above will be described based on FIG. The extraction steam pressure on the main turbine side is always detected by the extraction pressure detector 8 and input to the control device 6. The extraction steam pressure, is to approximately 12 kg / cm 2 of 13.5 kg / cm 2 or less is a opening pressure of the bleed valve 9, 14kg / cm 2 in the auxiliary steam pressure control valve 5 is supplied from the main boiler It is depressurized to and is supplied from the supply path 2 to the low-pressure steam generator 1. The steam supplied from the supply path 2 is controlled by the flow rate control valve 13 provided in the steam supply path 12 to a flow rate at which the low-pressure steam generator 1 can generate 8 kg / cm 2 of steam. It is supplied to the generator 1. At this time, the steam in the supply passage 2 does not flow to the extraction valve 9 side by the check valve 11.
【００３０】そして、抽気圧力検出器８で検出している
主機タービン抽気蒸気圧力が、この実施形態では、約１
２kg/cm2の圧力になったら、その抽気蒸気圧力の上昇に
応じて制御装置６が圧力制御弁５の二次側圧力設定値を
１４kg/cm2から徐徐に下げる（図中ｖ点）。そして、主
機タービン抽気蒸気圧力が１３．５kg/cm2の所定圧力に
達した時に、圧力制御弁５の二次側圧力が１２．５kg/c
m2となるように制御装置６で制御される（図中ｗ点）。The main engine turbine extraction steam pressure detected by the extraction pressure detector 8 is about 1 in this embodiment.
When the pressure reaches 2 kg / cm 2 , the control device 6 gradually lowers the secondary side pressure set value of the pressure control valve 5 from 14 kg / cm 2 in accordance with the increase in the extracted steam pressure (point v in the figure). Then, when the main engine turbine extraction steam pressure reaches a predetermined pressure of 13.5 kg / cm 2 , the secondary pressure of the pressure control valve 5 becomes 12.5 kg / c.
It is controlled by the control device 6 to be m 2 (point w in the figure).
【００３１】また、このように主機タービン抽気蒸気圧
力が１３．５kg/cm2に達したら圧力スイッチ１０が抽気
弁９を開放させ、抽気蒸気が抽気路４へと流れる。この
時、前記したように制御装置６で圧力制御弁５の二次側
圧力が抽気蒸気圧力よりも１kg/cm2だけ低く設定されて
いるので、抽気路４から供給される抽気蒸気が逆止弁１
１を介して蒸気供給路１２へと供給される。When the main turbine extracted steam pressure reaches 13.5 kg / cm 2 , the pressure switch 10 opens the extraction valve 9 and the extracted steam flows into the extraction passage 4. At this time, as described above, since the secondary pressure of the pressure control valve 5 is set to be lower than the extraction steam pressure by 1 kg / cm 2 by the control device 6, the extraction steam supplied from the extraction passage 4 is non-returned. Valve 1
It is supplied to the steam supply path 12 via 1.
【００３２】つまり、制御装置６によって圧力制御弁５
の二次側圧力を抽気弁９からの抽気蒸気圧力よりも１kg
/cm2低くしているので、抽気弁９が開放した時には抽気
路４からの蒸気が低圧蒸気発生器１の加熱蒸気として流
量制御弁１３へと供給される。その後、抽気圧力が上昇
したら、抽気圧力検出器８からの信号で制御装置６が圧
力制御弁５の二次側圧力をその抽気圧力よりも１kg/cm2
低くなる差圧をもつように制御する。つまり、抽気蒸気
の変化に応じて補助蒸気の設定圧力が変化させられる。
なお、抽気圧力が１５kg/cm2を越えた後は１８．５kg/c
m2まで達するが、圧力制御弁５の二次側設定圧力は、低
圧蒸気発生器１で定格蒸気量が得られる１４kg/cm2の一
定圧に保たれる。That is, the pressure control valve 5 is controlled by the control device 6.
The secondary side pressure of 1kg than the extraction steam pressure from the extraction valve 9
Since / cm 2 is lowered, the steam from the extraction passage 4 is supplied to the flow rate control valve 13 as the heating steam of the low pressure steam generator 1 when the extraction valve 9 is opened. After that, when the bleed air pressure rises, the control device 6 causes the secondary pressure of the pressure control valve 5 to be 1 kg / cm 2 lower than the bleed air pressure by a signal from the bleed air pressure detector 8.
Control to have a lower differential pressure. That is, the set pressure of the auxiliary steam is changed according to the change of the extracted steam.
After the extraction pressure exceeds 15kg / cm 2 , 18.5kg / c
Although reaching m 2, the secondary side set pressure of the pressure control valve 5 is kept at a constant pressure of 14 kg / cm 2 at which the rated steam amount can be obtained by the low pressure steam generator 1.
【００３３】このようにメインボイラ側の補助蒸気圧力
を抽気蒸気圧力の変化に応じて差圧を保ちながら変化さ
せることにより、仮に抽気蒸気圧力が一時的に落ちたと
しても、その時にはメインボイラ側の補助蒸気が低圧蒸
気発生器１へ供給されるので、抽気蒸気圧力に大きな変
化を生じるような場合でも低圧蒸気発生器１へ安定した
蒸気供給ができるようにしている。As described above, by changing the auxiliary steam pressure on the main boiler side while maintaining the differential pressure in accordance with the change in the extracted steam pressure, even if the extracted steam pressure temporarily drops, at that time the main boiler side Since the auxiliary steam of 1 is supplied to the low-pressure steam generator 1, stable steam can be supplied to the low-pressure steam generator 1 even when the extracted steam pressure changes greatly.
【００３４】なお、この実施形態では主機タービン抽気
蒸気圧力がほぼ１２kg/cm2に達した時点から圧力制御弁
５の二次側圧力を徐々に下げるようにしているが、この
圧力制御弁５の二次側圧力を下げる圧力はこの実施形態
に限定されるものではなく、蒸気タービンプラントの仕
様等に応じて設定すればよい。In this embodiment, the secondary pressure of the pressure control valve 5 is gradually decreased from the time when the main turbine extraction steam pressure reaches approximately 12 kg / cm 2 , but this pressure control valve 5 has The pressure for lowering the secondary pressure is not limited to this embodiment, and may be set according to the specifications of the steam turbine plant.
【００３５】一方、主機タービン抽気蒸気圧力が下降す
る過程では、主機タービン抽気蒸気圧力が１２．５kg/c
m2に落ちるまで、抽気路４からの抽気蒸気が低圧蒸気発
生器１に供給される。この時も、主機タービン抽気蒸気
圧力に対して圧力制御弁５の二次側圧力が１kg/cm2低く
なるように制御装置６で制御されている。つまり、抽気
蒸気圧力が１５kg/cm2に下がった時点から圧力制御弁５
の二次側圧力も１kg/cm2の差圧を保ちながら下げられ、
抽気蒸気圧力が１２．５kg/cm2に下がった時には１１．
５kg/cm2となるように制御されている（図中ｘ点）。そ
して、抽気蒸気圧力が１２．５kg/cm2に下がって、圧力
スイッチ１０が抽気弁９を閉鎖して抽気路４へ流れる抽
気蒸気を遮断した後、圧力制御弁５の二次側圧力が１
１．５kg/cm2から徐徐に上げられ、１４kg/cm2になった
時点でその圧力が保たれる（図中ｙ点）。On the other hand, in the process of lowering the steam extraction pressure of the main turbine, the steam extraction pressure of the main turbine is 12.5 kg / c.
Extracted steam from the extraction passage 4 is supplied to the low-pressure steam generator 1 until it falls to m 2 . Also at this time, the control device 6 controls the secondary pressure of the pressure control valve 5 to be 1 kg / cm 2 lower than the main turbine extracted steam pressure. In other words, the pressure control valve 5 starts when the extracted steam pressure drops to 15 kg / cm 2.
The secondary pressure of is also reduced while maintaining a differential pressure of 1 kg / cm 2 .
11. When the extraction steam pressure drops to 12.5 kg / cm 2 .
It is controlled to be 5 kg / cm 2 (point x in the figure). Then, after the extracted steam pressure drops to 12.5 kg / cm 2 , the pressure switch 10 closes the extraction valve 9 to shut off the extracted steam flowing to the extraction passage 4, and then the secondary pressure of the pressure control valve 5 becomes 1
1.5 kg / cm 2 gradually raised from its pressure is kept as it becomes 14kg / cm 2 (in the drawing point y).
【００３６】このように主機タービン抽気蒸気圧力に対
して圧力制御弁５の二次側圧力設定値が１kg/cm2低くな
るように設定するとともに、抽気弁２の閉鎖圧力の設定
値が抽気弁２の開放圧力設定値よりも１kg/cm2低くなる
ようにコントロールしているので、主機タービン負荷の
変化によって抽気蒸気圧力が変動しても、圧力制御弁５
と抽気弁９との間でハンチング現象を起こすことなく、
安定した圧力制御を行うことができる。In this way, the secondary side pressure set value of the pressure control valve 5 is set to 1 kg / cm 2 lower than the main turbine extracted steam pressure, and the set value of the closing pressure of the extraction valve 2 is set to the extraction valve. Since it is controlled to be 1 kg / cm 2 lower than the open pressure setting value of 2, even if the extraction steam pressure fluctuates due to changes in the main turbine load, the pressure control valve 5
Without causing a hunting phenomenon between the bleed valve 9 and
Stable pressure control can be performed.
【００３７】このように抽気蒸気圧力を制御した場合、
主機タービンの負荷が低い状態（この例では、８０％以
下程度）では、低圧蒸気発生器の加熱蒸気として流量制
御弁１３へ供給する蒸気圧力が１４kg/cm2以下になる
が、この場合には主機タービンが低い負荷状態であるた
め、その負荷状態において船内で利用する蒸気量は発生
させることができる。例えば、主機タービンの５０％負
荷の状態では、低圧蒸気発生器が発生させる蒸気圧力は
６．５kg/cm2程度となっているが（図中ｚ点）、その負
荷状態で必要な蒸気は得ることができる。そして、主機
タービン出力が常用出力点ＮＣＲ（例えば、９０％負
荷）であれば、抽気弁９から供給される蒸気圧力が１４
kg/cm2であるため、低圧蒸気発生器１では定格蒸気圧力
である８kg/cm2を発生することができる。When the extraction steam pressure is controlled in this way,
In the state where the load of the main engine turbine is low (about 80% or less in this example), the steam pressure supplied to the flow rate control valve 13 as the heating steam of the low-pressure steam generator is 14 kg / cm 2 or less, but in this case, Since the main turbine is in a low load state, the amount of steam used onboard the ship can be generated in that load state. For example, when the main engine turbine is loaded at 50%, the steam pressure generated by the low-pressure steam generator is about 6.5 kg / cm 2 (point z in the figure), but the required steam can be obtained under that load condition. be able to. When the main engine turbine output is the normal output point NCR (for example, 90% load), the steam pressure supplied from the extraction valve 9 is 14
Since it is kg / cm 2 , the low-pressure steam generator 1 can generate a rated steam pressure of 8 kg / cm 2 .
【００３８】このように低圧蒸気発生器１の加熱蒸気源
として低負荷状態（例えば、５０％程度）の主機タービ
ンの抽気蒸気を利用できるようにすることにより、主機
タービン抽気蒸気圧力が低い場合でも、その抽気蒸気に
よって低圧蒸気発生器１で蒸気を発生させることができ
るようにしている。As described above, the extracted steam of the main engine turbine in a low load state (for example, about 50%) can be used as the heating steam source of the low pressure steam generator 1, so that the extracted steam of the main engine turbine steam pressure is low. The low-pressure steam generator 1 can generate steam by the extracted steam.
【００３９】つまり、主機タービンの運転状態（負荷状
態）に応じて低圧蒸気発生器１の加熱蒸気圧力を制御す
る圧力制御弁５を制御して加熱蒸気圧力を変化させるこ
とにより、その運転状態において使用する蒸気量を低圧
蒸気発生器１で発生させることができるようにし、常用
出力点の運転状態では十分な定格蒸気量が得られるよう
に構成している。That is, the pressure control valve 5 for controlling the heating steam pressure of the low-pressure steam generator 1 is controlled according to the operating state (load state) of the main engine turbine to change the heating steam pressure, thereby The low-pressure steam generator 1 can generate the amount of steam to be used, and is configured so that a sufficient rated steam amount can be obtained in the operating state of the normal output point.
【００４０】したがって、低い負荷まで主機タービン抽
気蒸気を利用することが可能となり、メインボイラから
の補助蒸気を使用する範囲が狭まって抽気蒸気を利用で
きる主機タービン負荷範囲が広がるので、エネルギーを
無駄にする補助蒸気使用範囲が狭まり、プラント効率の
向上が計れる。Therefore, it is possible to use the main engine turbine extracted steam up to a low load, the range of using the auxiliary steam from the main boiler is narrowed, and the main engine turbine load range where the extracted steam can be used is widened, so energy is wasted. The use range of auxiliary steam is reduced and plant efficiency can be improved.
【００４１】なお、主機タービンの８０％負荷で１４kg
/cm2以上の抽気蒸気圧力を得ることができる出力のター
ビンであれば、上述したように８０％負荷以上となる常
用出力点では１４kg/cm2の抽気蒸気圧力を得ることがで
きるので、低圧蒸気発生器１で定格蒸気量を発生させる
ことができ、各々のプラントによって抽気口の段数を変
える必要がなくなり、主機タービンの設計が行いやすく
なる。At the load of 80% of the main turbine, 14 kg
If the turbine has an output capable of obtaining extraction steam pressure of at least / cm 2, it is possible to obtain extraction steam pressure of 14 kg / cm 2 at the normal output point of 80% load or more, as described above. The steam generator 1 can generate the rated amount of steam, and it is not necessary to change the number of stages of the extraction port depending on each plant, which facilitates the design of the main engine turbine.
【００４２】また、このように抽気蒸気圧力を、低圧蒸
気発生器伝熱面積の計算上、発生蒸気量負荷が最低とな
る１１．５kg/cm2で設計することができるので、従来に
比べて低圧蒸気発生器１を小型化することができる。Further, since the extraction steam pressure can be designed to be 11.5 kg / cm 2 at which the generated steam amount load becomes the minimum in the calculation of the heat transfer area of the low pressure steam generator in this way, compared with the conventional case. The low pressure steam generator 1 can be downsized.
【００４３】ところで、主機タービンからの抽気蒸気圧
力が安定している場合には、抽気蒸気圧力が圧力制御弁
５と抽気弁９との切替え圧力よりも高い時は圧力制御弁
５からの補助蒸気は使われないので、圧力制御弁５の二
次側圧力を制御する必要がない。このように抽気蒸気圧
力が安定している場合には、上述した抽気蒸気圧力が１
３．５kg/cm2の所定圧力に達したら、圧力制御弁５の二
次側圧力が１２．５kg/cm2となるように制御装置６で設
定し、その後は、この圧力制御弁５の二次側圧力よりも
高い抽気蒸気を低圧蒸気発生器１へ供給する。By the way, when the extraction steam pressure from the main turbine is stable, when the extraction steam pressure is higher than the switching pressure between the pressure control valve 5 and the extraction valve 9, the auxiliary steam from the pressure control valve 5 is used. Is not used, it is not necessary to control the secondary pressure of the pressure control valve 5. When the extracted steam pressure is stable, the extracted steam pressure is 1
When the predetermined pressure of 3.5 kg / cm 2 is reached, the secondary pressure of the pressure control valve 5 is set by the control device 6 to be 12.5 kg / cm 2, and thereafter, the secondary pressure of this pressure control valve 5 is set. Extracted steam higher than the secondary pressure is supplied to the low pressure steam generator 1.
【００４４】そして、抽気蒸気圧力が１３．５kg/cm2ま
で下がった時点から１２．５kg/cm2に下がるまで、圧力
制御弁５の二次側圧力を１２．５kg/cm2から１１．５kg
/cm2の間で抽気蒸気圧力との間に１kg/cm2の差圧を保つ
ように制御装置６で制御するようにしてもよい。このよ
うに抽気蒸気圧力が所定圧力以上の場合には、圧力制御
弁５の二次側圧力を変化させるように制御しなくてもよ
い。この場合、制御装置６での制御が容易になるが、こ
のような制御を行うか否かは、蒸気タービンプラントの
構成等に応じて適宜選択すればよい。[0044] Then, 11.5 kg from the time of extraction steam pressure drops to 13.5 kg / cm 2 down to 12.5 kg / cm 2, the secondary pressure of the pressure control valve 5 from 12.5 kg / cm 2
/ between cm 2 at may be controlled by the control device 6 so as to maintain the differential pressure 1 kg / cm 2 between the extraction steam pressure. As described above, when the extracted steam pressure is equal to or higher than the predetermined pressure, it is not necessary to control the secondary pressure of the pressure control valve 5 to change. In this case, control by the control device 6 becomes easy, but whether or not to perform such control may be appropriately selected according to the configuration of the steam turbine plant and the like.
【００４５】なお、上述した実施形態は一実施形態であ
り、本願発明の要旨を損なわない範囲での種々の変更は
可能であり、本願発明は上述した実施形態に限定される
ものではない。The above-described embodiment is an embodiment, and various modifications can be made without departing from the spirit of the invention, and the invention is not limited to the above-described embodiment.
【００４６】[0046]
【発明の効果】本願発明は、以上説明したような形態で
実施され、以下に記載するような効果を奏する。The present invention is carried out in the form as described above and has the following effects.
【００４７】低圧蒸気発生器の加熱蒸気となる補助蒸気
の圧力を制御する圧力制御弁の設定圧力を制御すること
で、主機タービンの低い負荷まで抽気蒸気を利用するこ
とができるので、補助蒸気を使用する範囲が狭まり、プ
ラント効率の向上を計ることが可能となる。By controlling the set pressure of the pressure control valve that controls the pressure of the auxiliary steam that becomes the heating steam of the low-pressure steam generator, the extracted steam can be used up to a low load of the main engine turbine. The range of use is narrowed, and it is possible to improve plant efficiency.
【図１】本願発明の一実施形態を示す抽気蒸気圧力の制
御装置の系統図である。FIG. 1 is a system diagram of a bleed steam pressure control device showing an embodiment of the present invention.
【図２】図１に示す制御装置による制御方法を示す線図
である。FIG. 2 is a diagram showing a control method by the control device shown in FIG.
【図３】従来の低圧蒸気発生器使用時における抽気蒸気
圧力の制御装置の一例を示す系統図である。FIG. 3 is a system diagram showing an example of a control device for extracting steam pressure when a conventional low-pressure steam generator is used.
【図４】図３に示す制御装置による制御方法を示す線図
である。FIG. 4 is a diagram showing a control method by the control device shown in FIG.
１…低圧蒸気発生器 ２…供給路 ３…抽気口 ４…抽気路 ５…圧力制御弁 ６…制御装置 ７…圧力検出器 ８…抽気圧力検出器 ９…抽気弁 １０…圧力センサ １１…逆止弁 １２…蒸気供給路 １３…流量制御弁 １４…圧力検出器 １５…抽気蒸気圧力制御装置 1. Low pressure steam generator 2 ... Supply path 3 ... Bleed port 4 ... extraction passage 5 ... Pressure control valve 6 ... Control device 7 ... Pressure detector 8 ... Bleed pressure detector 9 ... Bleed valve 10 ... Pressure sensor 11 ... Check valve 12 ... Steam supply path 13 ... Flow control valve 14 ... Pressure detector 15 ... Extraction steam pressure control device
フロントページの続き (72)発明者 岩瀬 文雄 兵庫県神戸市中央区東川崎町３丁目１番１ 号 川崎重工業株式会社神戸工場内 Ｆターム(参考） 3G071 AB05 BA07 BA31 CA07 DA00 EA02 EA05 FA03 HA03 JA02 3L021 CA06 DA04 DA31 FA02 FA05Continued front page (72) Inventor Fumio Iwase 3-1-1 Higashikawasaki-cho, Chuo-ku, Kobe-shi, Hyogo No. Kawasaki Heavy Industries, Ltd.Kobe factory F-term (reference) 3G071 AB05 BA07 BA31 CA07 DA00 EA02 EA05 FA03 HA03 JA02 3L021 CA06 DA04 DA31 FA02 FA05
Claims (7)
給路と、主機タービンの抽気蒸気を低圧蒸気発生器に供
給する抽気路とを設け、前記供給路に、補助蒸気の圧力
を所定の二次側蒸気圧力に減圧する圧力制御弁を設け、
前記抽気路に、主機タービン抽気蒸気圧力が所定圧力以
上になったら開放し、所定圧力以下になったら閉鎖する
抽気弁を設け、該抽気路と前記圧力制御弁との間に、該
抽気路の蒸気圧力に応じて圧力制御弁の二次側蒸気圧力
を抽気弁の開閉圧力よりも所定圧力だけ低い圧力に設定
する制御装置を設けた主機タービンの抽気蒸気圧力制御
装置。1. A supply passage for supplying auxiliary steam to a low-pressure steam generator and an extraction passage for supplying extracted steam of a main engine turbine to the low-pressure steam generator are provided, and a pressure of the auxiliary steam is set to a predetermined value in the supply passage. Provided with a pressure control valve for reducing the steam pressure to the secondary side,
The extraction passage is provided with an extraction valve that is opened when the main engine turbine extraction steam pressure is equal to or higher than a predetermined pressure, and is closed when the main turbine extraction steam pressure is equal to or lower than the predetermined pressure, and between the extraction passage and the pressure control valve. An extraction steam pressure control device for a main turbine, which is provided with a control device for setting the secondary side steam pressure of the pressure control valve to a pressure lower than the opening / closing pressure of the extraction valve by a predetermined pressure according to the steam pressure.
検出器を設け、抽気路の蒸気圧力を検出する抽気圧力検
出器を設け、該抽気圧力検出器の検出値と前記圧力検出
器の検出値とを比較して圧力制御弁の二次側蒸気圧力を
抽気路の蒸気圧力よりも所定圧力だけ低い設定圧力に変
更する制御回路を制御装置に設けたことを特徴とする請
求項１記載の主機タービンの抽気蒸気圧力制御装置。2. A pressure detector for detecting the secondary pressure of the pressure control valve, a bleed pressure detector for detecting the steam pressure in the bleed passage, and a detection value of the bleed pressure detector and the pressure detector. 2. The control device is provided with a control circuit for comparing the secondary side steam pressure of the pressure control valve to a set pressure which is lower than the steam pressure in the extraction passage by a predetermined pressure by comparing the detected pressure of the pressure control valve. The extraction steam pressure control device for the main engine turbine described.
タービンの抽気蒸気圧力が低い時は補助蒸気を使用し、
主機タービンの抽気蒸気圧力が上昇して所定圧力に達し
たら前記補助蒸気の設定圧力を抽気蒸気圧力よりも低い
圧力に設定して主機タービン負荷の低い範囲で抽気蒸気
を低圧蒸気発生器の加熱蒸気として利用できるようにし
た主機タービンの抽気蒸気圧力制御方法。3. Auxiliary steam is used as the heating steam for the low-pressure steam generator when the extraction steam pressure of the main engine turbine is low,
When the extraction steam pressure of the main engine turbine rises and reaches a predetermined pressure, the set pressure of the auxiliary steam is set to a pressure lower than the extraction steam pressure, and the extraction steam is heated in the low pressure steam generator in the low range of the main engine turbine load. A method for controlling the extraction steam pressure of a main engine turbine that has been made available as a product.
も低い圧力に設定した後、補助蒸気の設定圧力と抽気蒸
気圧力との差圧を保ちながら主機タービンの抽気蒸気圧
力変化に応じて補助蒸気の設定圧力を変化させるように
したことを特徴とする請求項３記載の主機タービンの抽
気蒸気圧力制御方法。4. The auxiliary steam is set to a pressure lower than the extraction steam pressure, and then the auxiliary pressure is set in accordance with a change in the extraction steam pressure of the main turbine while maintaining a differential pressure between the auxiliary steam setting pressure and the extraction steam pressure. The extraction steam pressure control method for a main engine turbine according to claim 3, wherein the set pressure of the steam is changed.
ービンのほぼ５０％負荷状態の蒸気圧力としたことを特
徴とする請求項３又は請求項４記載の主機タービンの抽
気蒸気圧力制御方法。5. The extraction steam pressure control method for a main engine turbine according to claim 3 or 4, wherein the extraction start steam utilization start pressure is set to a steam pressure at a load of the main engine turbine of approximately 50%.
に達したら補助蒸気の圧力を徐々に下げて抽気蒸気圧力
よりも低い圧力に設定し、抽気蒸気圧力が下降して所定
の設定圧力に達したら補助蒸気の圧力を徐々に上げて定
格蒸気圧力に設定することを特徴とする請求項３〜５の
いずれか１項に記載の主機タービンの抽気蒸気圧力制御
方法。6. When the extracted steam pressure rises to reach a predetermined set pressure, the pressure of the auxiliary steam is gradually reduced to a pressure lower than the extracted steam pressure, and the extracted steam pressure falls to a predetermined set pressure. 6. The method for controlling the extraction steam of the main engine turbine according to claim 3, wherein the pressure of the auxiliary steam is gradually increased to set the rated steam pressure when the temperature reaches the predetermined value.
りも１〜２kg/cm2低く設定したことを特徴とする請求項
３〜６のいずれか１項に記載の主機タービンの抽気蒸気
圧力制御方法。7. The extraction steam pressure of the main engine turbine according to any one of claims 3 to 6, wherein the set pressure of the auxiliary steam is set to be lower than the extraction steam pressure by 1 to 2 kg / cm 2. Control method.
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| CN110159453A (en) * | 2019-04-28 | 2019-08-23 | 中国石油天然气股份有限公司 | Waste heat recovery device for engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110159453A (en) * | 2019-04-28 | 2019-08-23 | 中国石油天然气股份有限公司 | Waste heat recovery device for engine |
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