JP2000154733A - Closed brayton cycle gas turbine device - Google Patents
Closed brayton cycle gas turbine deviceInfo
- Publication number
- JP2000154733A JP2000154733A JP10329823A JP32982398A JP2000154733A JP 2000154733 A JP2000154733 A JP 2000154733A JP 10329823 A JP10329823 A JP 10329823A JP 32982398 A JP32982398 A JP 32982398A JP 2000154733 A JP2000154733 A JP 2000154733A
- Authority
- JP
- Japan
- Prior art keywords
- gas
- gas turbine
- compressor
- inlet
- heater
- 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
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、閉鎖ループを形成
して循環する作動ガスで駆動されるガスタービンによ
り、作動ガスを昇圧させるガス圧縮機を作動させると共
に、同ガス圧縮機を作動させる出力を越えて外部出力を
発生させるようにしたクローズドブレイトンサイクルガ
スタービン装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine driven by a working gas circulating in a closed loop to operate a gas compressor for pressurizing the working gas and an output for operating the gas compressor. And a closed Brayton cycle gas turbine apparatus which generates an external output beyond the above.
【０００２】[0002]
【従来の技術】図５及び図６に基づいて従来のクローズ
ドブレイトンサイクルガスタービン装置の概要について
説明する。従来のクローズドガスタービンを示した図５
の系統図に於いて、６はガスタービン、７はガス圧縮機
で、同ガス圧縮機７はガスタービン６の外部出力を取り
出す出力軸１６の途中に取付けられている。2. Description of the Related Art An outline of a conventional closed Brayton cycle gas turbine device will be described with reference to FIGS. FIG. 5 showing a conventional closed gas turbine
In the system diagram, reference numeral 6 denotes a gas turbine, 7 denotes a gas compressor, and the gas compressor 7 is mounted in the middle of an output shaft 16 for taking out an external output of the gas turbine 6.
【０００３】８は加熱器、９は再生熱交換器で、同再生
熱交換器９はガスタービン６の排熱によりガス圧縮機７
で昇圧された作動ガス１５を予熱し、この予熱された作
動ガス１５は加熱器８で外部から熱Ｑ1 を受けて加熱さ
れ、ガスタービン６の入口から作動ガス１５b として供
給される。[0003] Reference numeral 8 denotes a heater, 9 denotes a regenerative heat exchanger, and the regenerative heat exchanger 9 uses a gas compressor 7 by exhaust heat of the gas turbine 6.
In preheating the pressurized working gas 15, the pre-heated working gas 15 is heated from outside by the heater 8 by the heat Q 1, it is supplied as working gas 15 b from the inlet of the gas turbine 6.
【０００４】他方、ガスタービン６で昇圧され、同ガス
タービン６から排出されて再生熱交換器９に至った作動
ガス１５は、前記した様にガス圧縮機７で昇圧された作
動ガス１５を予熱することにより熱量を放出し、更に冷
却機１０で水等の冷却媒体により冷却されて同冷却媒体
に熱Ｑ2 を放出し、ガス圧縮機７の入口へ作動ガス１５
a として帰還する。On the other hand, the working gas 15 pressurized by the gas turbine 6 and discharged from the gas turbine 6 to reach the regenerative heat exchanger 9 preheats the working gas 15 pressurized by the gas compressor 7 as described above. Then, the heat quantity is released, and further cooled by a cooling medium such as water in the cooling machine 10 to release the heat Q 2 to the cooling medium, and the working gas 15 is supplied to the inlet of the gas compressor 7.
It is fed back as a.
【０００５】かくして作動ガス１５は、ガス圧縮機７で
圧縮され（可逆断熱変化）、再生熱交換器９及び加熱器
８で加熱され（可逆等圧変化）、ガスタービン６で膨張
され（可逆断熱変化）、再生熱交換器９及び冷却機１０
で冷却され（可逆等圧変化）ガス圧縮機７へ帰還するク
ローズドブレイトンサイクルを形成している。Thus, the working gas 15 is compressed by the gas compressor 7 (reversible adiabatic change), heated by the regenerative heat exchanger 9 and the heater 8 (reversible isobaric change), and expanded by the gas turbine 6 (reversible adiabatic change). Change), regenerative heat exchanger 9 and cooler 10
To form a closed Brayton cycle which returns to the gas compressor 7 (reversible pressure change).
【０００６】なお、ガス圧縮機７の上流には、貯気用圧
縮機１を経て貯気タンク１１に至り、同貯気タンク１１
から開閉弁２を経て戻るガス供給ライン３が並行状に組
み込まれており、起動時及び出力変化時にガスタービン
６の負荷に応じてシステム内を循環する作動ガス１５の
量を調節可能に構成されている。[0006] Upstream of the gas compressor 7, the gas reaches the storage tank 11 via the storage compressor 1, and the storage tank 11
And a gas supply line 3 returning from the valve via an on-off valve 2 is installed in parallel, so that the amount of the working gas 15 circulating in the system can be adjusted according to the load on the gas turbine 6 at the time of startup and output change. ing.
【０００７】また、ガスタービン６とガス圧縮機７を機
械的に連結した出力軸１６には起動モータ１２が連結さ
れており、作動ガス１５が加熱器８で充分に加熱されな
いことによりガスタービン６がガス圧縮機７を駆動する
ことが出来ないシステムの起動時において、出力不足を
補うように構成されている。A starting motor 12 is connected to an output shaft 16 which mechanically connects the gas turbine 6 and the gas compressor 7, and the working gas 15 is not sufficiently heated by the heater 8, so that the gas turbine 6 Is configured to compensate for the output shortage at the time of starting the system in which the gas compressor 7 cannot be driven.
【０００８】そしてこのシステムにおいては、前記作動
ガス１５として、一般的にヘリウムガス（Ｈｅ）及びヘ
リウムガス（Ｈｅ）とキセノンガス（Ｘｅ）との混合ガ
ス（Ｈｅ＋Ｘｅ）が用いられている。In this system, helium gas (He) and a mixed gas of helium gas (He) and xenon gas (Xe) (He + Xe) are generally used as the working gas 15.
【０００９】前記従来のものにおいて、このシステムを
起動する際には、まず、開閉弁２を開き、あらかじめ貯
気用圧縮機１により高圧にして貯気タンク１１内に保存
していた作動ガス１５をガス圧縮機７の入口に供給す
る。In the prior art, when the system is started, first, the on-off valve 2 is opened, and the working gas 15 previously stored in the storage tank 11 at a high pressure by the storage compressor 1 is opened. Is supplied to the inlet of the gas compressor 7.
【００１０】これと同時に起動モータ１２をスタート
し、ガス圧縮機７を駆動して作動ガス１５a を圧縮し、
この作動ガス１５を再生熱交換器９を通して加熱器８に
供給する。[0010] At the start the start motor 12 at the same time, compressing the working gas 15 a by driving the gas compressor 7,
This working gas 15 is supplied to the heater 8 through the regenerative heat exchanger 9.
【００１１】加熱器８はこの作動ガス１５が供給される
と同時に点火され、再生熱交換器９から送られてきた作
動ガス１５を徐々に加熱して高温高圧の作動ガス１５b
としてガスタービン６に供給する。The heater 8 is ignited at the same time that the working gas 15 is supplied, and gradually heats the working gas 15 sent from the regenerative heat exchanger 9 to produce a high-temperature and high-pressure working gas 15 b.
To the gas turbine 6.
【００１２】この高温高圧の作動ガス１５b がガスター
ビン６に供給されて初めてガスタービン６は出力し始
め、作動ガス１５b が徐々に、更に高温化することに伴
ってガスタービン６の出力は増加する。The gas turbine 6 starts to output only after the high-temperature and high-pressure working gas 15b is supplied to the gas turbine 6, and the output of the gas turbine 6 is gradually increased as the working gas 15b gradually increases in temperature. To increase.
【００１３】そしてガスタービン６の出力がガス圧縮機
７の必要入力を上回ったとき、起動モータ１２の出力は
完全に不要となり、起動モータ１２を切り離してガスタ
ービン６を自立させ、ガスタービン６によりガス圧縮機
７を駆動すると共に、同ガス圧縮機７の駆動力を越える
余剰のガスタービン出力が軸出力として利用されること
になる。When the output of the gas turbine 6 exceeds the required input of the gas compressor 7, the output of the starting motor 12 becomes completely unnecessary, and the starting motor 12 is disconnected to make the gas turbine 6 self-supporting. When the gas compressor 7 is driven, an excess gas turbine output exceeding the driving force of the gas compressor 7 is used as the shaft output.
【００１４】[0014]
【発明が解決しようとする課題】前記した様に従来のシ
ステムは一連の操作で起動が完了することになるが、こ
の経過を時間軸上に展開すると図６（ａ）、（ｂ）の様
に示される。As described above, in the conventional system, the start-up is completed by a series of operations. If this progress is developed on a time axis, as shown in FIGS. 6 (a) and 6 (b). Is shown in
【００１５】すなわち、貯気タンクに保存していた作動
ガスがガス圧縮機に供給されてガス圧縮機流量が発生し
てから、同作動ガスが再生熱交換器、加熱器を経てガス
タービンガス供給を開始し、ガスタービン流量が発生す
るまでには一定の時間がかかり、いわゆる時間遅れとい
う不具合がある。That is, after the working gas stored in the storage tank is supplied to the gas compressor to generate a gas compressor flow rate, the working gas is supplied to the gas turbine gas supply via the regenerative heat exchanger and the heater. Starts, and a certain time is required until the gas turbine flow rate is generated, which is a so-called time delay.
【００１６】そしてこの時間遅れを持ってガスタービン
が起動し、ガスタービン出力がガス圧縮機入力を越えて
いわゆるガスタービン軸出力が得られ、これを契機に起
動モータを切り離してシステムの自立を完成するまでに
更に時間を要するので、起動モータが始動してからこの
システムの自立完成に至る間の駆動力を受け持つ起動モ
ータは、その出力が大きいものを用意しなければならな
いという不具合を伴うものであった。Then, the gas turbine is started with this time delay, the output of the gas turbine exceeds the input of the gas compressor, so-called gas turbine shaft output is obtained. Since it takes more time to complete the operation, the starting motor responsible for the driving force between the start of the starting motor and the completion of self-sustaining of the system has the disadvantage that a large output must be prepared. there were.
【００１７】本発明はこの様な従来のものにおける不具
合を解消し、システムの自立に至る時間を短縮して起動
モータの小型化を図り、設備の設置及び運用における経
済効果を向上させるようにしたものを提供することを課
題とするものである。The present invention solves such problems in the prior art, shortens the time required for the system to become independent, reduces the size of the starting motor, and improves the economic effect in installation and operation of equipment. It is an object to provide things.
【００１８】[0018]
【課題を解決するための手段】本発明は前記した課題を
解決すべくなされたもので、ガス圧縮機とガスタービン
を機械的に連結し、ガス圧縮機吐出側からガスタービン
入口に至り、かつ、ガスタービン出口からガス圧縮機吸
込側に至る作動ガスの閉鎖流路を形成すると共に、同閉
鎖流路内にあってガス圧縮機吸込側に高圧化した作動ガ
スを供給する貯気タンクを連絡したものにおいて、前記
高圧化した作動ガスの貯気タンクからガスタービン入口
に連絡する経路と加熱器入口に連絡する経路を設け、そ
れぞれの経路には作動ガスの供給を制御する装置を配設
したクローズドブレイトンサイクルガスタービン装置を
提供するものである。SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and has a structure in which a gas compressor and a gas turbine are mechanically connected to each other, from a gas compressor discharge side to a gas turbine inlet, and , Forming a closed flow path for working gas from the gas turbine outlet to the gas compressor suction side, and connecting an air storage tank in the closed flow path that supplies high-pressure working gas to the gas compressor suction side. In the above-mentioned structure, a path communicating from the high-pressure working gas storage tank to the gas turbine inlet and a path communicating with the heater inlet are provided, and each path is provided with a device for controlling the supply of the working gas. A closed Brayton cycle gas turbine device is provided.
【００１９】すなわち本発明によれば、前記閉鎖流路内
にあって高圧化した作動ガスの貯気タンクから作動ガス
の供給を制御する装置を介してガスタービン入口、及び
加熱器入口にそれぞれ連絡する経路を設けているので、
ガスタービンはその始動に際して同経路を経て高圧化し
た作動ガスをガスタービン入口及び加熱器入口に供給す
ることにより、ガス圧縮機入力とほぼ同時にガスタービ
ン出力が得られ、同ガスタービン出力がガス圧縮機入力
を越える点が早くなり、ガスタービンを起動モータ等の
補助手段から切り離して自立させる起動時間を短縮し、
起動モータ等の補助手段の小型化を図るようにしたもの
である。That is, according to the present invention, the gas turbine inlet and the heater inlet are connected to each other via the device for controlling the supply of the working gas from the high-pressure working gas storage tank in the closed channel. Because there is a route to
At the start of the gas turbine, the working gas, which has been increased in pressure through the same path, is supplied to the gas turbine inlet and the heater inlet, so that the gas turbine output can be obtained almost simultaneously with the input of the gas compressor. The point at which the machine input is exceeded becomes earlier, and the gas turbine is separated from auxiliary means such as a starter motor to shorten the start-up time to become independent,
The size of auxiliary means such as a starting motor is reduced.
【００２０】また、本発明はガス圧縮機とガスタービン
を機械的に連結し、ガス圧縮機吐出側からガスタービン
入口に至りガスタービン出口からガス圧縮機吸込側に至
る作動ガスの閉鎖流路を形成したものにおいて、前記ガ
ス圧縮機吐出側とガスタービン入口の間には前記閉鎖流
路内にあってガスタービン入口に高圧化した作動ガスを
供給する貯気タンクを設け、同作動ガスを供給する経路
には作動ガスの供給を制御する装置を配設したクローズ
ドブレイトンサイクルガスタービン装置を提供するもの
である。Further, the present invention mechanically connects the gas compressor and the gas turbine, and provides a closed flow path for working gas from the gas compressor discharge side to the gas turbine inlet and from the gas turbine outlet to the gas compressor suction side. A gas storage tank is provided between the discharge side of the gas compressor and the gas turbine inlet to supply a high-pressure working gas to the gas turbine inlet in the closed flow path, and the working gas is supplied. The present invention provides a closed Brayton cycle gas turbine device in which a device for controlling the supply of the working gas is disposed in the path of the closed Brayton cycle.
【００２１】すなわち、本発明によれば、前記閉鎖流路
内にあって高圧化した作動ガスの貯気タンクからガス圧
縮機吐出側とガスタービン入口の間に高圧化した作動ガ
スを供給する経路を設けているので、例えば負荷の上昇
に際して、同高圧化した作動ガスをガス圧縮機吐出側か
らガスタービン入口に加えることにより、ガス圧縮機で
必要とするガス流量よりガスタービンに供給されるガス
流量を過渡的に増加させて、ガスタービン出力の上昇を
確保するようにしたものである。That is, according to the present invention, a path for supplying a pressurized working gas from a gas storage tank of a pressurized working gas in the closed flow passage between a discharge side of the gas compressor and a gas turbine inlet. For example, when the load is increased, the working gas with the same pressure is added from the discharge side of the gas compressor to the gas turbine inlet, so that the gas supplied to the gas turbine from the gas flow rate required by the gas compressor is provided. The flow rate is transiently increased to secure an increase in gas turbine output.
【００２２】[0022]
【発明の実施の形態】本発明の実施の第１形態を図１及
び図２により説明する。なお、本実施の形態において、
前記した従来のものと同一部分については図中に同一の
符号を付して示し、本実施の形態における特徴ある構成
を重点的に説明し、従来のものと重複する説明は省略す
る。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment,
The same parts as those of the above-described conventional one are denoted by the same reference numerals in the drawings, and the characteristic configuration in the present embodiment will be mainly described, and the description overlapping with the conventional one will be omitted.
【００２３】即ち、本実施の形態においては、貯気タン
ク１１とガスタービン６の入口との間に貯気タンク１１
からガスタービン６に直接的に作動ガス１５を供給する
ガスタービン入口ガス供給ライン５を設けると共に、同
貯気タンク１１と加熱器８の入口との間に貯気タンク１
１から加熱器８に直接的に作動ガス１５を供給する加熱
器入口ガス供給ライン４を設け、同ガスタービン入口ガ
ス供給ライン５及び加熱器入口ガス供給ライン４のそれ
ぞれにガスタービン入口開閉弁１４及び加熱器入口開閉
弁１３を設けている。That is, in the present embodiment, the storage tank 11 is located between the storage tank 11 and the inlet of the gas turbine 6.
And a gas turbine inlet gas supply line 5 for directly supplying a working gas 15 to a gas turbine 6, and a storage tank 1 between the storage tank 11 and the inlet of the heater 8.
A heater inlet gas supply line 4 for directly supplying a working gas 15 from 1 to the heater 8 is provided, and a gas turbine inlet opening / closing valve 14 is provided in each of the gas turbine inlet gas supply line 5 and the heater inlet gas supply line 4. And a heater inlet opening / closing valve 13.
【００２４】従って本実施の形態においては、そのシス
テムの起動に際し、まず、起動モータ１２でガス圧縮機
７を駆動して作動ガス１５a を圧縮するが、これとほぼ
同時にガスタービン入口ガス供給ライン５を経て貯気タ
ンク１１から高圧の作動ガスをガスタービン６に供給す
ることにより、ガスタービン６にも出力を発生させるこ
とができる。[0024] Thus in the present embodiment, upon startup of the system, firstly, it compresses the working gas 15 a by driving the gas compressor 7 starts the motor 12, substantially at the same time as this gas turbine inlet gas supply line By supplying high-pressure working gas from the gas storage tank 11 to the gas turbine 6 via the gas turbine 5, an output can also be generated in the gas turbine 6.
【００２５】同時に、加熱器８を点火し、かつ、加熱器
入口ガス供給ライン４を経て貯気タンク１１から高圧の
作動ガスを加熱器８に供給することにより、高圧の作動
ガス１５b をいち早くガスタービン６に供給することが
できる。[0025] At the same time, to ignite the heater 8, and the heater inlet gas supply line 4 via the gas storage tank 11 by supplying a high-pressure working gas to the heater 8, quickly working gas 15 b of the high-pressure The gas can be supplied to the gas turbine 6.
【００２６】すなわち、図２にも示す様に、ガス圧縮機
流量とガスタービン流量とがほぼ同時に発生してガス圧
縮機入力とガスタービン出力とが得られ、ガスタービン
出力がガス圧縮機入力を越える点が前倒しとなるので、
起動モータ１２は出力を低減すると共に、自立までの起
動時間の短縮を行うことができ、小型化を図ることがで
きる。That is, as shown in FIG. 2, the gas compressor flow rate and the gas turbine flow rate occur almost simultaneously, and the gas compressor input and the gas turbine output are obtained. Because the point beyond is brought forward,
The starting motor 12 can reduce the output, shorten the starting time until the motor becomes independent, and reduce the size.
【００２７】次に本発明の実施の第２形態について図３
及び図４に基づいて説明する。なお、本実施の形態にお
いても、前記した従来のもの、及び実施の第１形態のも
のと同一の部分には同一の符号を付して示し、重複する
説明は省略する。Next, a second embodiment of the present invention will be described with reference to FIG.
A description will be given based on FIG. Also in the present embodiment, the same parts as those of the above-described conventional one and the first embodiment are denoted by the same reference numerals, and overlapping description will be omitted.
【００２８】即ち本実施の形態においては、従来、ガス
圧縮機７の入口に通じる様に配置されていた貯気タンク
１１からのガス供給ライン３を廃止し、同ガス供給ライ
ン３をガス圧縮機７の吐出側で、ガスタービン６の入口
との間に配置替えしたものである。That is, in the present embodiment, the gas supply line 3 from the air storage tank 11 which is conventionally arranged so as to communicate with the inlet of the gas compressor 7 is eliminated, and the gas supply line 3 is replaced with the gas compressor. 7 is disposed between the discharge side 7 and the inlet of the gas turbine 6.
【００２９】本実施の形態においてはこの様に、貯気タ
ンク１１からのガス供給ライン３は、ガス圧縮機７の吐
出側でガスタービン６の入口との間に配置しているの
で、負荷を上げる場合において、貯気タンク１１から作
動ガスをシステム内に供給すると、図４において破線で
示すように、ガス圧縮機７で必要とするガス流量に対し
て実線Ｇで示すガスタービン６における作動ガス流量１
５b は、過渡的に増加し、出力軸回転数Ｎで示すように
ガスタービン６の出力が増加するため、ガス圧縮機７の
必要入力の比率が小さくなる。In this embodiment, as described above, the gas supply line 3 from the gas storage tank 11 is disposed between the discharge side of the gas compressor 7 and the inlet of the gas turbine 6, so that the load is reduced. When the working gas is supplied into the system from the storage tank 11 in the case of raising, the working gas in the gas turbine 6 indicated by a solid line G with respect to the gas flow rate required by the gas compressor 7 as shown by a broken line in FIG. Flow rate 1
5 b transiently increases and the output of the gas turbine 6 increases as indicated by the output shaft rotation speed N, so that the required input ratio of the gas compressor 7 decreases.
【００３０】そのため、本実施の形態においては回転数
と出力は必ず上昇する方向に作用し、一時的にも低下す
ることはなく、しかも短時間に応答し、負荷変化に対す
る追従性が一段と向上するものである。For this reason, in the present embodiment, the rotation speed and the output always act in the rising direction, do not temporarily decrease, respond in a short time, and the followability to the load change is further improved. Things.
【００３１】なお、負荷を下げる場合は、この逆に作用
し、前記した負荷上昇時と同様に短時間に素早く応答し
て負荷変化に対する追従性が高くなる。When the load is reduced, the operation is reversed, and the response to the load change is improved by quickly responding in a short time as in the case of the load increase.
【００３２】以上、本発明を図示の実施の形態について
説明したが、本発明はかかる実施の形態に限定されず、
本発明の範囲内でその具体的構造に種々の変更を加えて
よいことはいうまでもない。Although the present invention has been described with reference to the illustrated embodiments, the present invention is not limited to such embodiments.
It goes without saying that various changes may be made to the specific structure within the scope of the present invention.
【００３３】[0033]
【発明の効果】以上説明したように本発明によれば、ガ
ス圧縮機とガスタービンを機械的に連結し、ガス圧縮機
吐出側からガスタービン入口に至り、かつ、ガスタービ
ン出口からガス圧縮機吸込側に至る作動ガスの閉鎖流路
を形成すると共に、同閉鎖流路内にあってガス圧縮機吸
込側に高圧化した作動ガスを供給する貯気タンクを連絡
したクローズドブレイトンサイクルガスタービン装置に
おいて、前記高圧化した作動ガスの貯気タンクからガス
タービン入口に連絡する経路と加熱器入口に連絡する経
路を設け、それぞれの経路には作動ガスの供給を制御す
る装置を配設して構成されているので、ガスタービンは
その始動に際して、前記ガスタービン入口に連絡する経
路及び加熱器入口に連絡する経路を経て、高圧化した作
動ガスをガスタービン入口及び加熱器入口に供給するこ
とにより、ガス圧縮機入力とほぼ同時にガスタービン出
力が得られ、同ガスタービン出力がガス圧縮機入力を越
える点が早くなり、ガスタービンを起動モータ等の補助
手段から切り離して自立させる起動時間を短縮し、起動
モータ等の補助手段の小型化を図ることができたもので
ある。As described above, according to the present invention, the gas compressor is mechanically connected to the gas turbine, the gas compressor is discharged from the gas compressor inlet to the gas turbine inlet, and the gas compressor is discharged from the gas turbine outlet to the gas compressor. In the closed Brayton cycle gas turbine device, which forms a closed flow path of the working gas reaching the suction side and communicates with a storage tank in the same closed flow path that supplies the high-pressure working gas to the gas compressor suction side. A path connecting the high-pressure working gas storage tank to the gas turbine inlet and a path connecting the heater inlet, and each path is provided with a device for controlling the supply of the working gas. When the gas turbine is started, the gas turbine passes through the path connected to the gas turbine inlet and the path connected to the heater inlet, and passes the pressurized working gas to the gas turbine. By supplying the gas to the gas inlet and the heater inlet, the gas turbine output can be obtained almost at the same time as the gas compressor input, and the point at which the gas turbine output exceeds the gas compressor input is accelerated. It is possible to shorten the starting time for the self-standing device to be separated from the means and to reduce the size of auxiliary means such as a starting motor.
【００３４】また、請求項２の発明によれば、ガス圧縮
機とガスタービンを機械的に連結し、ガス圧縮機吐出側
からガスタービン入口に至りガスタービン出口からガス
圧縮機吸込側に至る作動ガスの閉鎖流路を形成したクロ
ーズドブレイトンサイクルガスタービン装置において、
前記ガス圧縮機吐出側とガスタービン入口の間には前記
閉鎖流路内にあってガスタービン入口に高圧化した作動
ガスを供給する貯気タンクを設け、同作動ガスを供給す
る経路には作動ガスの供給を制御する装置を配設して構
成されているので、例えば負荷の上昇に際して、同高圧
化した作動ガスをガス圧縮機吐出側からガスタービン入
口に加えることにより、ガス圧縮機で必要とするガス流
量よりガスタービンに供給されるガス流量を過渡的に増
加させて、ガスタービン出力の上昇を確保し、かつ、ガ
ス圧縮機の必要入力の比率を小さくして負荷変化に対す
る追従性を一段と向上することができたものである。According to the second aspect of the present invention, the gas compressor and the gas turbine are mechanically connected, and the operation from the gas compressor discharge side to the gas turbine inlet and from the gas turbine outlet to the gas compressor suction side is performed. In a closed Brayton cycle gas turbine device forming a closed gas flow path,
An air storage tank is provided between the discharge side of the gas compressor and the gas turbine inlet to supply a high-pressure working gas to the gas turbine inlet in the closed flow path. Since the system is provided with a device for controlling the gas supply, for example, when the load is increased, the working gas having the same pressure is added to the gas turbine inlet from the gas compressor discharge side, so that the gas compressor is required. Transiently increase the gas flow rate supplied to the gas turbine from the gas flow rate to ensure a rise in the gas turbine output, and reduce the ratio of the required input of the gas compressor to improve the ability to follow load changes. It was something that could be further improved.
【図１】本発明の実施の第１形態に係るクローズドブレ
イトンサイクルガスタービン装置の系統図である。FIG. 1 is a system diagram of a closed Brayton cycle gas turbine device according to a first embodiment of the present invention.
【図２】図１のものにおける時間軸上の変化を示し、
（ａ）はガスタービン及びガス圧縮機のガス流量並びに
ガスタービンのガス温度の状況を示す説明図、（ｂ）は
ガス圧縮機入力及びガスタービン出力の状況を示す説明
図である。FIG. 2 shows the change on the time axis in FIG. 1;
(A) is an explanatory view showing the state of the gas flow rate of the gas turbine and the gas compressor and the gas temperature of the gas turbine, and (b) is an explanatory view showing the state of the gas compressor input and the gas turbine output.
【図３】本発明の実施の第２形態に係るクローズドブレ
イトンサイクルガスタービン装置の系統図である。FIG. 3 is a system diagram of a closed Brayton cycle gas turbine device according to a second embodiment of the present invention.
【図４】図３のものにおける時間変化に対するガスター
ビン及びガス圧縮機の作動ガス流量の変化、並びに出力
軸回転数の変化を示す説明図である。4 is an explanatory diagram showing a change in the working gas flow rate of the gas turbine and the gas compressor and a change in the output shaft rotation speed with respect to a time change in FIG.
【図５】従来のクローズドブレイトンサイクルガスター
ビン装置の系統図である。FIG. 5 is a system diagram of a conventional closed Brayton cycle gas turbine device.
【図６】図６のものにおける時間軸上の変化を示し、
（ａ）はガスタービン及びガス圧縮機のガス流量並びに
ガスタービンのガス温度の状況を示す説明図、（ｂ）は
ガス圧縮機入力及びガスタービン出力の状況を示す説明
図である。6 shows a change on the time axis in FIG. 6;
(A) is an explanatory view showing the state of the gas flow rate of the gas turbine and the gas compressor and the gas temperature of the gas turbine, and (b) is an explanatory view showing the state of the gas compressor input and the gas turbine output.
１ 貯気用圧縮機 ２ 開閉弁 ３ ガス供給ライン ４ 加熱器入口ガス供給ライン ５ ガスタービン入口ガス供給ライン ６ ガスタービン ７ ガス圧縮機 ８ 加熱器 ９ 再生熱交換器 １０ 冷却機 １１ 貯気タンク １２ 起動モータ １３ 加熱器入口開閉弁 １４ ガスタービン入口開閉弁 １５ 作動ガス １６ 出力軸 REFERENCE SIGNS LIST 1 gas storage compressor 2 on-off valve 3 gas supply line 4 heater inlet gas supply line 5 gas turbine inlet gas supply line 6 gas turbine 7 gas compressor 8 heater 9 regenerative heat exchanger 10 cooler 11 air storage tank 12 Start motor 13 Heater inlet on-off valve 14 Gas turbine inlet on-off valve 15 Working gas 16 Output shaft
Claims (2)
結し、ガス圧縮機吐出側からガスタービン入口に至り、
かつ、ガスタービン出口からガス圧縮機吸込側に至る作
動ガスの閉鎖流路を形成すると共に、同閉鎖流路内にあ
ってガス圧縮機吸込側に高圧化した作動ガスを供給する
貯気タンクを連絡したクローズドブレイトンサイクルガ
スタービン装置において、前記高圧化した作動ガスの貯
気タンクからガスタービン入口に連絡する経路と加熱器
入口に連絡する経路を設け、それぞれの経路には作動ガ
スの供給を制御する装置を配設したことを特徴とするク
ローズドブレイトンサイクルガスタービン装置。1. A gas compressor and a gas turbine are mechanically connected to each other, from a discharge side of the gas compressor to an inlet of the gas turbine,
In addition, a closed flow path for working gas from the gas turbine outlet to the gas compressor suction side is formed, and a storage tank for supplying a high-pressure working gas to the gas compressor suction side in the closed flow path is provided. In the connected closed Brayton cycle gas turbine device, a path connecting the high-pressure working gas storage tank to the gas turbine inlet and a path connecting the heater inlet are provided, and each path controls the supply of the working gas. A closed Brayton cycle gas turbine device, comprising:
結し、ガス圧縮機吐出側からガスタービン入口に至りガ
スタービン出口からガス圧縮機吸込側に至る作動ガスの
閉鎖流路を形成したクローズドブレイトンサイクルガス
タービン装置において、前記ガス圧縮機吐出側とガスタ
ービン入口の間には前記閉鎖流路内にあってガスタービ
ン入口に高圧化した作動ガスを供給する貯気タンクを設
け、同作動ガスを供給する経路には作動ガスの供給を制
御する装置を配設したことを特徴とするクローズドブレ
イトンサイクルガスタービン装置。2. A closed type in which a gas compressor and a gas turbine are mechanically connected to each other to form a closed flow path of working gas from a gas compressor discharge side to a gas turbine inlet and from a gas turbine outlet to a gas compressor suction side. In the Brayton cycle gas turbine device, an air storage tank is provided between the discharge side of the gas compressor and the gas turbine inlet to supply a high-pressure working gas to the gas turbine inlet in the closed flow path. A device for controlling the supply of the working gas is disposed in a path for supplying the working gas.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10329823A JP2000154733A (en) | 1998-11-19 | 1998-11-19 | Closed brayton cycle gas turbine device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10329823A JP2000154733A (en) | 1998-11-19 | 1998-11-19 | Closed brayton cycle gas turbine device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000154733A true JP2000154733A (en) | 2000-06-06 |
Family
ID=18225638
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10329823A Pending JP2000154733A (en) | 1998-11-19 | 1998-11-19 | Closed brayton cycle gas turbine device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000154733A (en) |
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