JPH01177422A - Gas turbine plant - Google Patents
Gas turbine plantInfo
- Publication number
- JPH01177422A JPH01177422A JP33323987A JP33323987A JPH01177422A JP H01177422 A JPH01177422 A JP H01177422A JP 33323987 A JP33323987 A JP 33323987A JP 33323987 A JP33323987 A JP 33323987A JP H01177422 A JPH01177422 A JP H01177422A
- Authority
- JP
- Japan
- Prior art keywords
- gas turbine
- compressor
- combustion air
- drive shaft
- variable speed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 claims abstract description 34
- 239000007789 gas Substances 0.000 abstract description 66
- 239000000567 combustion gas Substances 0.000 abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 3
- 230000008878 coupling Effects 0.000 abstract 3
- 238000010168 coupling process Methods 0.000 abstract 3
- 238000005859 coupling reaction Methods 0.000 abstract 3
- 230000007423 decrease Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000007906 compression Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 230000002747 voluntary effect Effects 0.000 description 1
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、ガスタービンに燃焼用空気を送る圧縮機がガ
スタービンにより駆動されるガスタービンプラントに関
する。しかしながら、これに限らず加圧流動床ボイラに
燃焼用又は流動用空気を送る圧縮機がガスタービンによ
り駆動されるガスタービンプラントにも適用されるもの
である。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a gas turbine plant in which a compressor for supplying combustion air to a gas turbine is driven by a gas turbine. However, the present invention is not limited to this, and can also be applied to a gas turbine plant in which a compressor that sends combustion or fluidized air to a pressurized fluidized bed boiler is driven by a gas turbine.
従来の技術
周知の技術であるガスタ−ビンプラントて、燃焼用空気
の圧縮機はガスタービンにより駆動されるのが一般的で
ある。BACKGROUND OF THE INVENTION In gas turbine plants, which are well known in the art, the combustion air compressor is typically driven by a gas turbine.
例えば、第５図に示すように、ガスタービンｌの燃焼ガ
スを排ガスボイラ２に供給し、給水ポンプ３から送られ
た給水を加熱して蒸気を発生させるガスタービンプラン
トでは、ガスタービン１に燃焼用空気を送る圧縮機４が
駆動軸５を介してガスタービンｌによって駆動されてい
た。また、他の例として加圧流動床ボイラ（図示されず
）の燃焼ガスを用いてガスタービンを駆動させるガスタ
ービンプラントでは、加圧流動床ボイラに燃焼用もしく
は流動用空気を送る圧縮機がガスタービンによって駆動
されるものもあった。For example, as shown in FIG. 5, in a gas turbine plant in which combustion gas from a gas turbine 1 is supplied to an exhaust gas boiler 2 and feed water sent from a feed water pump 3 is heated to generate steam, the gas turbine 1 is A compressor 4 for supplying air for use was driven by a gas turbine 1 via a drive shaft 5. In addition, as another example, in a gas turbine plant that uses combustion gas from a pressurized fluidized bed boiler (not shown) to drive a gas turbine, a compressor that sends combustion or fluidized air to the pressurized fluidized bed boiler is equipped with a gas turbine. Some were powered by turbines.
さて、図に示す如くガスタービン！は通常発電機６に接
続し、このプラントではその間に蒸気タービン７を同軸
に設置したものである。もちろん、この蒸気タービンの
ないプラントも多く使用されていることは云うまでもな
いが、この場合、ガスタービンプラントにおける発電機
６は一定の回転−度で運転することが望ましいため、そ
の発電機６′
を駆動させるためのガスタービン１の駆動軸〜の回転速
度を一定とするよう、ガスタービン１への燃焼用空気の
量又は圧力の制御は、そのガスタービンに接続する圧縮
機４の上流側若しくは下流側に設けたダンパ、ベーン又
はバルブ等（図示されず）により行っていた。なお、図
中、符号８は燃焼器、９は電動機、及び１０は煙突を夫
々示す。Now, as shown in the figure, it's a gas turbine! is normally connected to a generator 6, and in this plant, a steam turbine 7 is installed coaxially between them. Of course, it goes without saying that many plants without this steam turbine are also used, but in this case, it is desirable that the generator 6 in the gas turbine plant be operated at a constant rotation degree, so the generator 6 The amount or pressure of combustion air to the gas turbine 1 is controlled by the upstream side of the compressor 4 connected to the gas turbine so as to keep the rotational speed of the drive shaft of the gas turbine 1 constant. Alternatively, this was done using a damper, vane, valve, etc. (not shown) provided on the downstream side. In the figure, reference numeral 8 indicates a combustor, 9 indicates an electric motor, and 10 indicates a chimney.
発明が解決しようとする問題点
以上述べた従来のガスタービンプラントでは、圧縮機４
は略一定の回転速度で運転されていたため、例えば発電
機負荷が低下したときガスタービンでの燃料消費が減少
し、必要燃焼用空気量も減少するようなときには、前述
の如く圧縮機４の回転数を低減する方向へ制限すること
ができなかったので、その代わりに、前記ダンパ、ベー
ン又はバルブ等をガスタービンｌと圧縮機４間の空気系
統に配置し、これらの開開操作で制御せざるを得なかっ
た。Problems to be Solved by the Invention In the conventional gas turbine plant described above, the compressor 4
Since the compressor 4 was operated at a substantially constant rotational speed, for example, when the generator load decreases, the fuel consumption in the gas turbine decreases, and the required amount of combustion air also decreases, the rotation of the compressor 4 changes as described above. Since it was not possible to limit the number of dampers, vanes, valves, etc., were placed in the air system between the gas turbine 1 and the compressor 4, and the dampers, vanes, valves, etc. I had no choice.
この場合、第６図で示す圧縮機の流量−揚程特性曲線（
Ｑ −Ｈカーブ）に基づいて、ダンパ、ベーン又はバル
ブ等で燃焼用空気の圧力損失を変化させ、圧縮機４の差
圧を変えることにより、前記特性曲線上での運転点を変
化させ、燃焼用空気流量を制御していた。In this case, the flow rate-head characteristic curve of the compressor shown in Fig. 6 (
By changing the pressure loss of combustion air using a damper, vane, or valve, etc., and changing the differential pressure of the compressor 4 based on the Q-H curve, the operating point on the characteristic curve is changed, and the combustion controlled the air flow rate.
ところが、燃焼用空気の量又は圧力の制御をダンパ、ベ
ーン又はバルブ等により行うことは、夫々にエネルギー
の損失、即ち圧力損失が生じ、ガスタービンプラント全
体の効率を低下させる不都合があった。However, controlling the amount or pressure of combustion air using a damper, vane, valve, or the like causes a loss of energy, that is, a loss of pressure, which inconveniently reduces the efficiency of the entire gas turbine plant.
問題点を解決するための手段
本発明は、このような従来の問題点を解決するために、
ガスタービンプラントにおいて、ガスタービンに燃焼用
空気を送る圧縮機の駆動軸と、ガスタービンの駆動軸と
を可変速継手を介して接続し、圧縮機出口の燃焼用空気
量を制御量として該燃焼用空気量の測定値と目標値との
制御偏差を前記可変速継手にフィードバックする制御装
置を設けたものである。Means for Solving the Problems In order to solve these conventional problems, the present invention provides the following:
In a gas turbine plant, the drive shaft of a compressor that sends combustion air to the gas turbine is connected to the drive shaft of the gas turbine through a variable speed joint, and the amount of combustion air at the outlet of the compressor is used as a control variable to control the combustion. A control device is provided which feeds back a control deviation between the measured value and the target value of the amount of air used to the variable speed joint.
作用
従って、圧縮機を可変速継手を介してガスタービン≠会
≠幸により駆動させるため、この可変速継手により圧縮
機の回転速度を変化させて適切なブ等を不要にして、こ
れらで失われていたエネルギーの損失をなくすことがで
きる。Therefore, since the compressor is driven by the gas turbine via the variable speed joint, the rotational speed of the compressor is changed by the variable speed joint, eliminating the need for appropriate brakes and reducing the amount of energy lost by these. It is possible to eliminate the energy loss that would otherwise have occurred.
実施例
以下第１〜４図を参照して、本発明による実施例につい
て説明する。EXAMPLES Hereinafter, examples according to the present invention will be described with reference to FIGS. 1 to 4.
しかして、第１図に示すように、ガスタービン１に燃焼
用空気を送る圧縮機４と、ガスタービンｌとを接続する
従来の駆動軸５（第５図参照）に代えて、この駆動軸５
を縁切りした、図に示す如く圧縮機４用の駆動軸５ａと
、ガスタービン１用の駆動軸５ｂとを夫々設けて、両部
動軸端部には可変速継手１１を接続している。As shown in FIG. 1, this drive shaft is used instead of the conventional drive shaft 5 (see FIG. 5) that connects the compressor 4 that sends combustion air to the gas turbine 1 and the gas turbine l. 5
As shown in the figure, a drive shaft 5a for the compressor 4 and a drive shaft 5b for the gas turbine 1 are provided, respectively, and a variable speed joint 11 is connected to the ends of both drive shafts.
そして、本発明によるガスタービンプラントには、例え
ば圧縮機４出口の燃焼用空気量を制御量としてこの可変
速継手にフィードバック制御を行う制御量Ｒ１２を設け
ている。。The gas turbine plant according to the present invention is provided with a control variable R12 that performs feedback control on the variable speed joint by using, for example, the amount of combustion air at the outlet of the compressor 4 as a control variable. .
即ち、第２図に良く示すように、この制御装置は、ガス
タービンｌの駆動軸５ｂから圧縮機４の駆動軸５ａへ伝
達する回転数が可変速継手１１を介して増減するよう設
置したもので、圧縮機４出口の燃焼用空気量を制御量と
して、目標（必要）値との制御偏差を可変速継手１１に
フィードバックする。That is, as clearly shown in FIG. 2, this control device is installed so that the rotational speed transmitted from the drive shaft 5b of the gas turbine 1 to the drive shaft 5a of the compressor 4 can be increased or decreased via the variable speed joint 11. Then, using the amount of combustion air at the outlet of the compressor 4 as a control amount, the control deviation from the target (required) value is fed back to the variable speed joint 11.
このため、制御装置１２は大略、圧縮機４出口側に設け
られた燃焼用空気量を測定する流量計１３と、後述する
運転点の導入方法により設定された燃焼用空気量の目標
値を送り出す４ための設定部１４と、この設定部からの
空気量要求信号を受けて指示された目標値と前述の流量
計１３から検出される測定値とを比較演算する演算器１
５と、これから導かれる動作信号の値によって次の操作
部となる可変速継手１１に必要な訂正信号、つまり修正
の回転数を送り出す調節部１６とからなっている。For this reason, the control device 12 generally sends out a target value for the amount of combustion air set by a flow meter 13 provided on the outlet side of the compressor 4 that measures the amount of combustion air and a method of introducing an operating point to be described later. a setting section 14 for 4, and a computing unit 1 that compares and calculates a target value instructed in response to an air amount request signal from this setting section and a measured value detected from the aforementioned flow meter 13.
5, and an adjusting section 16 which sends out a necessary correction signal, that is, a corrected rotational speed, to the variable speed joint 11, which is the next operating section, based on the value of the operating signal derived from the operating signal.
以上のような構成により、ガスタービンｌと蒸気タービ
ン７とは出力軸６′を発電機６に接続して駆動し、ガス
タービンｌへの燃焼用空気は圧縮゛機４により圧縮され
ガスタービンｌに送られる。With the above configuration, the gas turbine 1 and the steam turbine 7 are driven by connecting the output shaft 6' to the generator 6, and the combustion air to the gas turbine 1 is compressed by the compressor 4, and the gas turbine 1 is compressed by the compressor 4. sent to.
る。なお、圧縮機１は電動機９により駆動するトさス； さ由５はガスタービンプラントの起動時等に用いる。Ru. Note that the compressor 1 is driven by an electric motor 9; The shaft 5 is used when starting up a gas turbine plant.
そして、プラントの運転中、発電機６負荷が上昇・低下
して、ガスタービン！での燃料消費が増減し、必要燃焼
空気量も増減するようなときは、そのガスタービンに供
される空気流量が常に適正となるよう圧縮機４の回転数
を変えてガスタービン１に送られる燃焼用空気量を変化
させれば良い。Then, while the plant is operating, the generator 6 load increases and decreases, and the gas turbine! When fuel consumption increases or decreases, and the required amount of combustion air also increases or decreases, the rotation speed of the compressor 4 is changed so that the amount of air supplied to the gas turbine is always appropriate, and the air is sent to the gas turbine 1. All you have to do is change the amount of combustion air.
このため圧縮機４とガスタービン１の各駆動軸５ａ。For this purpose, each drive shaft 5a of the compressor 4 and the gas turbine 1.
１Ｑ５ｂに接続した可変速継手１１の操作によりその回
転数を制御することとなる。The rotation speed is controlled by operating the variable speed joint 11 connected to 1Q5b.
しかして、圧縮機４の回転数を調整する理由について説
明すると、第３図に示すように、この圧縮機の回転数ｎ
を変化させると、空気流量Ｑは回転数ｎに比例して、ま
た揚程（圧縮機で得られる差圧）Ｈはｎのへ乗に比例し
て容易に目標の空気流量を得ることができるからであり
、従って、圧縮機４の回転数が可変速継手、１１の機械
的な操作により制御することが可能だからである。Therefore, to explain the reason for adjusting the rotation speed of the compressor 4, as shown in FIG. 3, the rotation speed n of this compressor is
By changing , the air flow rate Q is proportional to the rotation speed n, and the head (differential pressure obtained by the compressor) H is proportional to the power of n, so the target air flow rate can be easily obtained. Therefore, the rotation speed of the compressor 4 can be controlled by mechanical operation of the variable speed joint 11.
一方、第４図において、圧縮機４の回転数ｎに対する特
性曲線（Ｑ −Ｆｌ カーブ）の変化の概要を示して
おり、通常、ある空気量が流れたときの系統の圧力損失
の値１’ｌ（システム圧損）はほぼ−様に決まるため、
ガスタービン必要空気量に対する必要揚程も一通りに定
まることとなる。On the other hand, Fig. 4 shows an overview of the change in the characteristic curve (Q - Fl curve) with respect to the rotation speed n of the compressor 4, and normally the value of pressure loss in the system when a certain amount of air flows is 1' Since l (system pressure loss) is determined approximately in a - manner,
The required head for the required air amount of the gas turbine will also be determined.
そこで、ガスタービンｌに必要とされる燃焼用空気量に
対しては、前記の第３図のデータと第４図のデータとを
重ね合わせ、揚程とシステム圧損とを等しく採ることに
より、最適な運転点が求まり、制御装置１２における設
定部１４での燃焼用空気量（又は圧力）の目標値を設定
することができる。Therefore, the amount of combustion air required for the gas turbine 1 can be determined optimally by overlapping the data in Figure 3 and the data in Figure 4, and by taking the head and system pressure drop equally. The operating point is determined, and the target value of the combustion air amount (or pressure) can be set in the setting section 14 of the control device 12.
そして、この目標値と、圧縮機４出口で流量計１３によ
り検出された制御量となる燃焼用空気量の測定値との制
御偏差をフィードバックすることにより、駆動軸５ａを
介して可変速継手１１による圧縮機４の回転数が確実に
制御された後、ガスタービン１へは適正な燃焼用空気量
を送れることとなる。Then, by feeding back the control deviation between this target value and the measured value of the amount of combustion air, which is the control amount detected by the flow meter 13 at the outlet of the compressor 4, the variable speed joint 11 After the rotational speed of the compressor 4 is reliably controlled, an appropriate amount of combustion air can be sent to the gas turbine 1.
゛ しかしながら、本発明によれば、測定対象は前述の
圧縮機４出口での燃焼用空気量だけに限定されるもので
はなく、他の実施例として、ガスタービンｌ出口の酸素
濃度や同じくガスタービン１出口の燃焼（排）ガス量等
によってなされても良い。゛ However, according to the present invention, the measurement target is not limited to the amount of combustion air at the compressor 4 outlet described above, but can also be measured by the oxygen concentration at the gas turbine 1 outlet or the gas turbine 1 outlet. It may also be determined by the amount of combustion (exhaust) gas at one outlet.
また、可変速継手１１の操作においても前述のフィード
バック制御に限定されるものではなく、他の実施例と８
ガスタービンｌ負荷や燃料流量に対し所定の圧縮機４の
回転数とする公知の技術による制御方式が採用されても
良いことは云うまでもない。Furthermore, the operation of the variable speed joint 11 is not limited to the above-described feedback control, and may be performed using other embodiments or 8.
It goes without saying that a control method based on a known technique may be adopted in which the rotation speed of the compressor 4 is set to a predetermined number with respect to the gas turbine load and fuel flow rate.
発明の効果
以上の結果、発電機の負荷変動等が生じた場合に、可変
速継手の制御により圧縮機側の回転数を調整することで
ガスタービンへの必要空気量を容易に、かつ確実に供給
することができるため、従来、使用されていたダンパ、
ベーン又はパルプ等の装置を基本的に不要とするので、
これらに発生した圧力損失をなくし、よってガスタービ
ンプラント全体の効率を高めることができる。As a result of the invention, the amount of air required for the gas turbine can be easily and reliably adjusted by controlling the speed of the compressor by controlling the variable speed joint when load fluctuations occur on the generator. Dampers, which were traditionally used, can be supplied with
Since equipment such as vanes or pulp is basically unnecessary,
It is possible to eliminate the pressure loss generated in these, thereby increasing the efficiency of the entire gas turbine plant.
また、制御性向上の観点からダンパ、ベーン、又はバル
ブ等を可変速継手と併設して同時に制御に用いる場合に
も、従来と比較してエネルギーの損失を低減できる。Furthermore, even when a damper, vane, valve, or the like is installed together with a variable speed joint and used for control at the same time from the viewpoint of improving controllability, energy loss can be reduced compared to the conventional method.
更に、圧縮機の消費する軸動力の低減分は、発電機によ
り有効に回収される。Furthermore, the reduced shaft power consumed by the compressor is effectively recovered by the generator.
第１図は本発明によるガスタービンプラントの一例を示
す系統図、第２図は圧縮機の回転数をフィードバックす
る制御装置を示す系統図、第３図は圧縮機の回転数を変
化させたときの流量−揚程特性曲線（Ｑ −Ｈカーブ）
図、第４図は圧縮機の回転数に対する流量−システム圧
損特性曲線図、第５図は従来のガスタービンプラントを
示す系統図、第６図は圧縮機のある一定回転数での滝壷
−揚程酌
特性曲倉接ある。
ｌ・・ガスタービン、４・・圧縮機、５ａ・・圧縮機の
駆動軸、５ｂ・・ガスタービンの駆動軸、１１・・可変
速継手、１２・・制御装置。
第１図
１ ：カ′人タービ゛ン
４：圧縮橿。
５（１：圧縮後峻動徊
５ｂ：ゴスタービンｐｊ！動軸
１１：可変梨Ｉ佳手
１２：制御装置
第２図
第３因
第４図
Ｏｑ気流量０ □
第５図
第す図
手続補正書（自発）
昭和６３年２月１７日
特許庁長官 小 川 邦 夫 殿
１、事件の表示 特願昭６２年３３３２３９号２、
発明の名称 ガスタービンプラント３、補正をする
者 事件との関係 特許出願人名称 三菱重工業
株式会社
４、代 理 人 〒１００東京都千代田区有楽町−
丁目８番１号「発明の詳細な説明」の欄、並びに
図面の第１図及び第２図
６、補正の内容
［■］明細書を次のように補正します。
（１）特許請求の範囲を別紙のとおり訂正。
（２）第１頁第１６行「しかしながら、」の後に「本発
明は、」を加入。
（３）第２頁において、第１５行「図」を「第５図」と
訂正、第１６行「この」を「またこの第５図に示す」と
訂正、第１７行「したものである。」を「している。」
と訂正、第１９行「ないが、この場合」を「ない。そし
て、」と訂正。
（４）第４頁第１６〜１９行「、圧縮機・・・設け」を
削除。
（５）第５頁において、第１行「従って」の前に「この
ような手段によれば、」を加入、第９行「による」を「
の」と訂正、第１Ｏ行「説明する。」の後に「なお、第
１図において、第５図に示したものと同一の部分には同
一の符号を付して、その詳細な説明は省略する。」を加
入、第１８〜１９行「本発明・・・例えば」を「本実施
例によれば、」と訂正。
（６）第７頁において、第４〜５行「圧縮機・・・用い
る。」を「ガスタービンプラントの起動時等においては
、圧縮機ｌは継手１７を介して電動機９により駆動する
こともできる。」と訂正。
（７）第９頁において、第１行「しかし・・・よれば」
を「なお」と訂正、第１３行「の結果」を「述べたよう
に、本発明によれば、」と訂正。
［１１］図面の第１及び２図をそれぞれ別紙のとおり訂
正します。
特許請求の範囲
ガスタービンに燃焼用空気を送る圧縮機の駆動軸と、ガ
スタービンの駆動軸とを可変速継手を介して接続したこ
とを特徴とするガスタービンプラント。
第１図
１ ：力１人タービン
４：圧縮線・
５１；圧縮後峻動徊
５ら：ゴスタービン憶動軸
１１：可変距Ｕ味手
１２：制岬装置Fig. 1 is a system diagram showing an example of a gas turbine plant according to the present invention, Fig. 2 is a system diagram showing a control device that feeds back the rotation speed of the compressor, and Fig. 3 is a system diagram showing a control device that feeds back the rotation speed of the compressor. Flow rate-head characteristic curve (Q-H curve)
Fig. 4 is a flow rate-system pressure drop characteristic curve diagram with respect to the rotation speed of the compressor, Fig. 5 is a system diagram showing a conventional gas turbine plant, and Fig. 6 is a waterfall basin-lift height at a certain rotation speed of the compressor. There is a kakukura-touchi characteristic of the sake cup. l...Gas turbine, 4...Compressor, 5a...Compressor drive shaft, 5b...Gas turbine drive shaft, 11...Variable speed joint, 12...Control device. Figure 1 1: Car turbine 4: Compression rod. 5 (1: Steep movement after compression 5b: Gosturbin pj! Axis of movement 11: Variable position I/O 12: Control device Figure 2 Figure 3 Cause Figure 4 Oq air flow rate 0 □ Figure 5 Figure 2 Procedure amendment (Voluntary) February 17, 1988 Kunio Ogawa, Commissioner of the Patent Office 1, Indication of the case Patent Application No. 333239 of 1988 2,
Title of the invention Gas turbine plant 3, person making the amendment Relationship to the case Patent applicant name Mitsubishi Heavy Industries, Ltd. 4, agent Yurakucho, Chiyoda-ku, Tokyo 100-
The column of "Detailed Description of the Invention" in No. 8-1, Figures 1 and 2 of the drawings, 6, and the content of the amendment [■] The description will be amended as follows. (1) The scope of claims has been amended as shown in the attached sheet. (2) On page 1, line 16, after “however,” add “the present invention”. (3) On page 2, "Figure" in line 15 is corrected to "Figure 5,""this" in line 16 is corrected to "also shown in this figure 5," and line 17 says "This is what we did." .” is “doing.”
In line 19, "No, but in this case" was corrected to "No, and." (4) Page 4, lines 16 to 19, ``Providing a compressor...'' was deleted. (5) On page 5, add ``by such means'' before ``therefore'' in the first line, and change ``by'' to ``by'' in the 9th line.
"," was corrected, and after "Explain" in line 1O, "In addition, in Figure 1, the same parts as shown in Figure 5 are given the same reference numerals, and detailed explanations thereof are omitted. In lines 18 and 19, ``The present invention...for example'' was corrected to ``According to this embodiment.'' (6) On page 7, in lines 4 and 5, "Compressor... is used." I can do it.'' I corrected myself. (7) On page 9, line 1: “However…”
In line 13, ``result of'' was corrected to ``as stated, according to the present invention.'' [11] Figures 1 and 2 of the drawings are corrected as shown in the attached sheets. Claims: A gas turbine plant characterized in that a drive shaft of a compressor that sends combustion air to a gas turbine and a drive shaft of the gas turbine are connected via a variable speed joint. Figure 1 1: Power 1 person turbine 4: Compression line 51; Post-compression movement 5 etc.: Gosturbine storage shaft 11: Variable distance U taster 12: Control cape device
Claims (1)
スタービンの駆動軸とを可変速継手を介して接続し、圧
縮機出口の燃焼用空気量を制御量として該燃焼用空気量
の測定値と目標値との制御偏差を前記可変速継手にフィ
ードバックする制御装置を設けたことを特徴とするガス
タービンプラント。The drive shaft of the compressor that sends combustion air to the gas turbine is connected to the drive shaft of the gas turbine via a variable speed joint, and the amount of combustion air at the outlet of the compressor is used as a control variable to measure the amount of combustion air. A gas turbine plant, comprising: a control device that feeds back a control deviation between a value and a target value to the variable speed joint.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33323987A JPH01177422A (en) | 1987-12-29 | 1987-12-29 | Gas turbine plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33323987A JPH01177422A (en) | 1987-12-29 | 1987-12-29 | Gas turbine plant |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01177422A true JPH01177422A (en) | 1989-07-13 |
Family
ID=18263879
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33323987A Pending JPH01177422A (en) | 1987-12-29 | 1987-12-29 | Gas turbine plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01177422A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20180100661A (en) * | 2016-02-12 | 2018-09-11 | 지멘스 악티엔게젤샤프트 | Gas turbine train with starter motor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5231208A (en) * | 1975-09-03 | 1977-03-09 | Komatsu Ltd | Control system for single-shaft differential gas turbine |
| JPS60150438A (en) * | 1984-01-19 | 1985-08-08 | Toshio Sugimori | Gas turbine engine |
-
1987
- 1987-12-29 JP JP33323987A patent/JPH01177422A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5231208A (en) * | 1975-09-03 | 1977-03-09 | Komatsu Ltd | Control system for single-shaft differential gas turbine |
| JPS60150438A (en) * | 1984-01-19 | 1985-08-08 | Toshio Sugimori | Gas turbine engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20180100661A (en) * | 2016-02-12 | 2018-09-11 | 지멘스 악티엔게젤샤프트 | Gas turbine train with starter motor |
| JP2019512056A (en) * | 2016-02-12 | 2019-05-09 | シーメンス アクティエンゲゼルシャフト | Gas turbine section with starter motor |
| US10570827B2 (en) | 2016-02-12 | 2020-02-25 | Siemens Aktiengesellschaft | Gas turbine train with starter motor |
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