JPS61223202A - Controller of mixed pressure turbine - Google Patents
Controller of mixed pressure turbineInfo
- Publication number
- JPS61223202A JPS61223202A JP6263385A JP6263385A JPS61223202A JP S61223202 A JPS61223202 A JP S61223202A JP 6263385 A JP6263385 A JP 6263385A JP 6263385 A JP6263385 A JP 6263385A JP S61223202 A JPS61223202 A JP S61223202A
- Authority
- JP
- Japan
- Prior art keywords
- mixed pressure
- valve
- pressure turbine
- mixed
- governor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
- F01K7/20—Control means specially adapted therefor
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、調速弁を介して主作動流体を供給するととも
に、途中段から混圧弁を介して、混圧用作動流体を供給
する混圧タービンの制御装置に関する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a mixed pressure turbine which supplies a main working fluid through a speed governor valve and also supplies a working fluid for mixed pressure from an intermediate stage through a mixed pressure valve. Regarding a control device.
背景技術
先行技術の混圧タービンでは、調速弁を介して主作動流
体が供給されるとともに、途中段から混圧弁を介ｔ、′
ｃｆｉ圧用作動流体が供給される。このような構成を有
する混圧タービンにおいて、その出力軸の回転速度は調
速器によって検出さ八、調速弁によって制御される。こ
の調速弁は、機械的構成を有する調速器の出力によって
制御される。BACKGROUND ART In the prior art mixed pressure turbine, the main working fluid is supplied via the speed governor valve, and the main working fluid is supplied from an intermediate stage via the mixed pressure valve.
A cfi pressure working fluid is supplied. In a mixed pressure turbine having such a configuration, the rotational speed of its output shaft is detected by a speed governor and controlled by a speed governor valve. This governor valve is controlled by the output of a governor having a mechanical configuration.
調速器には一般に調定率（ドループ）が設定されており
、調速器の出力の大終さにより、混圧タービンの回松速
度設定値が変化する構成となっている。The speed governor is generally set with a droop, and the set speed of the mixed pressure turbine changes depending on the output of the speed governor.
このような調速器によって、混圧タービンに主作動流体
を供給する調速弁の開度が制御される。Such a speed governor controls the opening degree of a speed governor valve that supplies the main working fluid to the mixed pressure turbine.
調連弁闇度が予め定めた値以上になると、混圧タービン
に混圧用作動流体を供給する混圧弁が開弁状態とされ、
開状態となった混気弁は予め定めた値以下となると遮断
される。When the regulating valve darkness level exceeds a predetermined value, the mixed pressure valve that supplies working fluid for mixed pressure to the mixed pressure turbine is opened.
The air-fuel mixture valve that is in the open state is shut off when the air-fuel mixture becomes below a predetermined value.
第６図はこの先行技術の混圧タービンの制御動作を説明
するグラフである。第６図（１）のライン！１は、混圧
タービンの出力軸の回啄速度に対する調速弁の開度の変
化を示し、第６図（２）は混圧弁の作動状態を示す、調
速弁の開度は、混圧タービンの負荷に対応する。すなわ
ち負荷が大きくなると、混圧タービンの出力軸の回啄速
度が低下するが、この低下に対応して調速弁の弁開度が
増大するようにされている。FIG. 6 is a graph explaining the control operation of this prior art mixed pressure turbine. The line in Figure 6 (1)! 1 shows the change in the opening degree of the regulating valve with respect to the rotation speed of the output shaft of the mixed pressure turbine, and FIG. 6 (2) shows the operating state of the mixed pressure valve. To accommodate the load on the turbine. That is, as the load increases, the rotation speed of the output shaft of the mixed pressure turbine decreases, but the opening degree of the governor valve increases in response to this decrease.
したがってこのような調定率によると、第６図（１）の
ライン／１で示すように、負荷の増大に伴い混圧タービ
ンの出力軸の回転速度が次第に低下―
する区間Ｌ１において、調速弁の開度は次第に増大する
。調速弁開度が、予め定められる開度Ａになったとき、
第６図（２）で示されるように混圧弁が開弁状態にされ
、混圧タービンの途中段から混圧用作動流体が与えられ
る。このとき調速弁開度が減少し、混圧タービンの回啄
速度は上昇するが、混圧弁の作動にヒステリシスを持た
せ、調速弁開度が点Ｂ以下になるまでは、混気弁は閉状
態とならない、第６図（１）に示すように負荷が引続き
増大すると、その回転速度は再び次第に減少する。Therefore, according to such a regulation rate, as shown by line /1 in Fig. 6 (1), the speed governor valve is The degree of opening gradually increases. When the regulating valve opening reaches a predetermined opening A,
As shown in FIG. 6(2), the mixed pressure valve is opened, and working fluid for mixed pressure is applied from an intermediate stage of the mixed pressure turbine. At this time, the governor valve opening decreases and the regeneration speed of the mixture pressure turbine increases. As shown in FIG. 6(1), as the load continues to increase, its rotational speed gradually decreases again.
発明が解決しようとする問題点
したがってこの上うな混圧タービンにおいでは、第６図
を参照して説明したように、調速弁開度に対応する出力
軸の回啄速度が鋸歯状に変化してしまうので、複数ター
ビンの並列運転および複数タービン相互の負荷分担など
が、不可能になっていた。Problems to be Solved by the Invention Therefore, in such a mixed pressure turbine, as explained with reference to FIG. This makes it impossible to operate multiple turbines in parallel and share loads among them.
本発明の目的は、上述の問題点を解決し、構成が簡単で
あるとともに、調定率を設定することができる改良され
た混圧タービンの制御装置を提供することである。SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems and provide an improved control device for a mixed pressure turbine that has a simple configuration and is capable of setting a regulation rate.
問題点を解決するための手段
本発明は、混圧タービンの出力軸に連結される機械式調
速器、機械的変位を空気圧力に変換する変位圧力変換器
、空気圧力によって連続的に開度が調節される混圧弁お
よび調速器出力変位を同出力と一対−の関数関係を有す
る機械的変位に変換するカム機構あるいはリンク機構を
有する混圧タービンの制御装置において、
混圧タービンに混圧用作動流体を供給する混圧弁と、
調速器の出力に応答し、混圧弁の開度を調速弁の開度の
関数として連続的に変化する手段とを含むことを特徴と
する混圧タービンの制御装置であｔ 、る。Means for Solving the Problems The present invention provides a mechanical speed governor connected to the output shaft of a mixed pressure turbine, a displacement pressure converter that converts mechanical displacement into air pressure, and a displacement pressure converter that converts mechanical displacement into air pressure. A control device for a mixed pressure turbine that has a cam mechanism or a link mechanism that converts the output displacement of the mixed pressure valve and governor into a mechanical displacement that has a pairwise functional relationship with the same output. A mixed pressure turbine, comprising: a mixed pressure valve that supplies working fluid; and means that responds to the output of the speed governor and continuously changes the opening degree of the mixed pressure valve as a function of the opening degree of the speed governor. The control device is t.
作 用
混圧タービンには、その出力軸に連結される調速器が備
えられる。また本発明に従えば、調速器からの出力によ
ってその弁開度が制御され混圧タービンに主作動流体を
供給する調速弁と、混圧タービンに混圧用作動流体を供
給する混圧弁と、調速器の出力に応答し混圧弁の開度を
調速弁の開度の関数として連続的に変化する手段とが備
えられる。したがって混圧タービンの負荷が変化しても
、混圧弁の開度が調速弁の開度の関数として連続的に変
化されるので、調速器に設定される調定率が、一定であ
るようにすることができる。The mixed pressure turbine is equipped with a speed governor connected to its output shaft. Further, according to the present invention, there is provided a governor valve whose opening degree is controlled by the output from the governor and supplies the main working fluid to the mixed pressure turbine, and a mixed pressure valve which supplies the mixed pressure working fluid to the mixed pressure turbine. , means for continuously changing the opening degree of the mixed pressure valve as a function of the opening degree of the speed governor in response to the output of the speed governor. Therefore, even if the load on the mixed pressure turbine changes, the opening degree of the mixed pressure valve is continuously changed as a function of the opening degree of the governor valve, so that the regulation rate set in the governor remains constant. It can be done.
実施例
第１図は、本発明の一実施例の混圧タービン１の制御装
置２の構成を示すブロック図、第２図は第１図のカム機
構１４に関連する構成を示すブロック図である。第１図
および第２図を参照して、制御装置２の構成を説明する
。混圧タービン１の初段には、主作動流体であるたとえ
ば高圧力蒸気が、管路３お上り連続的に弁開度を制御し
得る調速弁４を介して供給される。混圧タービン１の途
中段には、管路５お上り連続的に弁開度を制御し得る混
圧弁６を介しで、混圧用作動流体であるたとえば低圧力
蒸気が供給される。この混圧タービン１内の蒸気などは
、管路７を介して、外部に排出される。Embodiment FIG. 1 is a block diagram showing the configuration of a control device 2 of a mixed pressure turbine 1 according to an embodiment of the present invention, and FIG. 2 is a block diagram showing a configuration related to the cam mechanism 14 of FIG. 1. . The configuration of the control device 2 will be explained with reference to FIGS. 1 and 2. A main working fluid, for example, high-pressure steam, is supplied to the first stage of the mixed pressure turbine 1 through a regulating valve 4 that can continuously control the valve opening degree upstream from a conduit 3 . A working fluid for mixed pressure, such as low-pressure steam, is supplied to an intermediate stage of the mixed pressure turbine 1 through a pipe 5 and a mixed pressure valve 6 whose opening degree can be continuously controlled. Steam and the like within this mixed pressure turbine 1 are discharged to the outside via a pipe line 7.
混圧タービン１の出力軸８には、交流発電機９が連結さ
れ、電力線１０から電力が導出される。An alternating current generator 9 is connected to an output shaft 8 of the mixed pressure turbine 1, and electric power is derived from a power line 10.
この導出された電力の値は、電力計１１によって検出さ
れる。This derived power value is detected by the power meter 11.
出力軸８には調速器１２が連結され、この調速器１２の
出力軸１３は、混圧タービン１の出力軸８の回転速度に
対応した角変位を行なう、この調速器１２の出力軸１３
の角変位によって、調速弁４の弁開度が制御される。ま
たこの角変位はカム機構１４を介して、たとえば往復運
動などの変位に変換され、変位／圧力変換器１５に与え
られる。A speed governor 12 is connected to the output shaft 8 , and an output shaft 13 of the speed governor 12 is connected to an output shaft 13 of the speed governor 12 that performs an angular displacement corresponding to the rotational speed of the output shaft 8 of the mixed pressure turbine 1 . Axis 13
The valve opening degree of the speed governor valve 4 is controlled by the angular displacement of the speed governor valve 4. Further, this angular displacement is converted into a displacement such as a reciprocating motion via the cam mechanism 14, and is applied to a displacement/pressure converter 15.
詳しくは第２図に示すように、出力軸１３にカム１４ａ
が固定される。カム１４亀のカム面１４ｂには、カム機
構１４のホロア１５ａが接触している。In detail, as shown in FIG. 2, a cam 14a is attached to the output shaft 13.
is fixed. A follower 15a of the cam mechanism 14 is in contact with the cam surface 14b of the cam 14 turtle.
出力軸１３が角変位すると、カムｆ４ｍによってホロ７
１５ａが第２図の左右方向に変位する。When the output shaft 13 is angularly displaced, the holo 7 is moved by the cam f4m.
15a is displaced in the left-right direction in FIG.
このホロア１５ｍの変位に対応して、空気源Ｓから２イ
ン１６ｍを介する空気圧が、ホロ７１５ａの変位量に対
応した圧力に、変位／圧力変換器１５・
によって変換され、ライン１６ｂに与えられる。Corresponding to the displacement of the follower 15m, the air pressure from the air source S via the 2-in 16m is converted by the displacement/pressure converter 15 into a pressure corresponding to the amount of displacement of the follower 715a, and is applied to the line 16b.
ライン１６ｂの空気圧は、管路１６ａを介して混圧弁６
に与えられる。また管路１６ｍには、後述されるような
作動状態を有する緊急制御手段１７が介在される。The air pressure in the line 16b is transferred to the mixed pressure valve 6 through the conduit 16a.
given to. Further, an emergency control means 17 having an operating state as described later is interposed in the conduit 16m.
第３図は、第１図の調速弁４および混圧弁６のそれぞれ
の弁開度の関係を示すグラフである。したがって第１図
および第３図のカム機構１４の９７ト線図は、第３図の
フィン！２が達成されるように選ばれる。このライン！
２が示す混圧弁６および調速弁４のそれぞれの弁開度間
の関係は、後述するように第４図に示される調定率が、
可及的に一定になるよるに定められる。FIG. 3 is a graph showing the relationship between the valve openings of the regulating valve 4 and the mixed pressure valve 6 shown in FIG. Therefore, the 97-t diagram of the cam mechanism 14 in FIGS. 1 and 3 corresponds to the fin! 2 is chosen so that it is achieved. This line!
As will be described later, the relationship between the opening degrees of the mixed pressure valve 6 and the speed regulating valve 4 shown in 2 is such that the regulation rate shown in FIG.
determined to be as constant as possible.
第４図は第１図の混圧タービン１の制御装置２の作動状
態を説明するグツ７である。第１図〜第４図を参照して
、制御装置２の作動状態を説明する。第４図のライン１
３は、第１図において混圧弁６を遮断した状態で、調速
弁４のみによる制御によって、混圧タービン１を駆動し
たとき、交流発電機９によって発電される電力量の変化
を示す。FIG. 4 is a diagram 7 explaining the operating state of the control device 2 of the mixed pressure turbine 1 shown in FIG. The operating state of the control device 2 will be explained with reference to FIGS. 1 to 4. Line 1 in Figure 4
3 shows a change in the amount of electric power generated by the alternator 9 when the mixed pressure turbine 1 is driven under control only by the speed governor valve 4 with the mixed pressure valve 6 shut off in FIG.
電力量Ｗ１はこめときの発電量の最大値である。The electric power amount W1 is the maximum value of the electric power generation amount at the time of heating.
このとき調速弁４を制御する調速器１２には、第４図の
ライン１４で示される調定率が設定されでいる。At this time, the regulating rate shown by line 14 in FIG. 4 is set in the governor 12 that controls the regulating valve 4.
このような調速器１２によって制御される調速弁４に加
え、混圧弁６を用いて混圧タービン１を制御する動作を
説明する。混圧タービン１の出力軸８の回転速度は、調
速器１２によって検出される。調速器１２は、検出した
出力軸８の回転速度に対応した角変位を行ない、調速弁
４の開度を制御する。一方、調速ｅ１２の出力軸１３の
前述した角変位は、カム機構１４を介しで前述したよう
に変換されて、変位／圧力変換器１５に与えられる。変
位／圧力変換器１５による空気圧の変化は、管路１６を
介して混圧弁６に与えられ、途中段に混圧用作動流体が
与えられる混圧タービン１による発電量が、＃１４図の
ライン！５で示される変化と、最大値Ｗ２とを有するよ
うに、その弁開度が変化される。The operation of controlling the mixed pressure turbine 1 using the mixed pressure valve 6 in addition to the speed governor 4 controlled by the speed governor 12 will be described. The rotational speed of the output shaft 8 of the mixed pressure turbine 1 is detected by the governor 12 . The governor 12 controls the opening degree of the governor valve 4 by making an angular displacement corresponding to the detected rotational speed of the output shaft 8 . On the other hand, the aforementioned angular displacement of the output shaft 13 of the speed governor e12 is converted as described above via the cam mechanism 14 and is applied to the displacement/pressure converter 15. The change in air pressure caused by the displacement/pressure converter 15 is applied to the mixed pressure valve 6 via the pipe line 16, and the amount of power generated by the mixed pressure turbine 1, to which the working fluid for mixed pressure is applied to the intermediate stage, is the line shown in Figure #14! The valve opening degree is changed so as to have the change shown by 5 and the maximum value W2.
このような混圧弁６の弁開度は、調速弁４の弁開度の関
数であり、その関係は第３図のライン！２で示される。The opening degree of the mixed pressure valve 6 is a function of the opening degree of the regulating valve 4, and the relationship is as shown in the line ! of FIG. 2.
このライン１２の曲線の形状は、弁開度に関して上述し
た関係を有する調速弁４およＶ混圧弁６を共に用いで、
混圧タービン１の制御を行なうとき、第４図のフィン！
３で示される調定率が可及的に直線状になるように設定
される。The shape of the curve of this line 12 is determined by using both the governor valve 4 and the V mixed pressure valve 6, which have the above-mentioned relationship regarding the valve opening.
When controlling the mixed pressure turbine 1, the fins in Figure 4!
The adjustment rate indicated by 3 is set to be as linear as possible.
このようにしで制御される混圧タービン１による発電量
の変化は、ライン！５で示される。すなわちライン！３
で示される発電量と比較して、差Ｇを有する大きな発電
量を得ることができる。The change in the amount of power generated by the mixed pressure turbine 1 controlled in this way is the line! 5. In other words, the line! 3
A large amount of power generation with a difference G can be obtained compared to the amount of power generation shown by .
第５図は第１図の制御装置２の構成を説明するブロック
図である。調速器１２には、混圧ゝタービン１の出力軸
８の回転速度を設定する回転速度設定ｎ１Ｂと演算器１
９とが備えられる。混圧タービン１の出力軸８の回転速
度に関連する情報が、回転速度設定回路１８からの出力
と加減算器ＡＤ１で加算されて、演算器１９に与えられ
る。演算ｎ１９の出力は、フィン２０に出力される。こ
の出力はフィードバックされ、調定率設定機構２１に与
えられ、その出力は前記回転速度設定回路１８からの出
力などと加減算器ＡＤＩで加算゛されて演算器１９に与
えられる。この出力に基づく調速１１１２の出力が、調
速弁４に与えられ、その弁開度を制御する。FIG. 5 is a block diagram illustrating the configuration of the control device 2 shown in FIG. 1. The speed governor 12 includes a rotation speed setting n1B for setting the rotation speed of the output shaft 8 of the mixed pressure turbine 1, and a calculator 1.
9 is provided. Information related to the rotational speed of the output shaft 8 of the mixed pressure turbine 1 is added to the output from the rotational speed setting circuit 18 by an adder/subtractor AD1, and is provided to the arithmetic unit 19. The output of calculation n19 is output to the fin 20. This output is fed back and given to the adjustment rate setting mechanism 21, and its output is added to the output from the rotational speed setting circuit 18, etc. by an adder/subtractor ADI, and is given to the arithmetic unit 19. The output of the speed governor 1112 based on this output is given to the speed governor valve 4 to control its valve opening.
一方、この調速１ｓ１２の出力は、カムｆｉ？４１４を
介しで混圧弁６に与えられ、その開度を制御する。した
がって混圧タービン１には、調速弁４および混圧弁６か
らの作動流体が、７１１Ｉ算器ＡＤ２で加算されて与え
られる。On the other hand, the output of this speed governor 1s12 is cam fi? 414 to the mixed pressure valve 6 to control its opening degree. Therefore, the working fluid from the governor valve 4 and the mixed pressure valve 6 is added to the mixed pressure turbine 1 by the 711I calculator AD2.
このような制御装Ｗ１２において、混圧タービン１がト
リップ・′シ、図示されていない弁によ・つて主作動流
体が遮断され出力軸８の回転速度が低くなったとき、調
速弁４および混圧弁６の弁開度は、前述した作動に従っ
て、共に太き（なる、したがってこのようなトリップ時
には、混圧作動流体も遮断する必要がある。かかる状況
に於ては、緊急制御手段１７が能動化し、混圧弁６を遮
断する空気圧を出力する。すなわち混圧タービン１のシ
リツブ時であっても、混圧作動流体の過度の供給を防ぐ
ことができる。In such a control device W12, when the mixed pressure turbine 1 trips and the main working fluid is cut off by a valve (not shown) and the rotational speed of the output shaft 8 becomes low, the governor valve 4 and The opening degree of the mixed pressure valve 6 is widened in accordance with the above-described operation. Therefore, at the time of such a trip, it is necessary to shut off the mixed pressure working fluid as well. In such a situation, the emergency control means 17 It is activated and outputs air pressure that shuts off the mixed pressure valve 6. That is, even when the mixed pressure turbine 1 is in operation, excessive supply of the mixed pressure working fluid can be prevented.
−したがって上述のような制御装置２を用いて、混圧タ
ービン１を駆動したとき、第４図のフィン！３で示され
る調定率を、可及的に一定にすることができる。したが
って複数の混圧タービン１および制御！１１２を用いて
並列運啄を行なおうとするとき、負荷分担を有利に行な
うことができるとともに、この並列Ｍ献が可能になる。- Therefore, when the mixed pressure turbine 1 is driven using the control device 2 as described above, the fins shown in FIG. 4! The adjustment rate indicated by 3 can be made as constant as possible. Therefore multiple mixed pressure turbines 1 and control! When trying to perform parallel operation using 112, load sharing can be advantageously performed and this parallel M distribution becomes possible.
上述の実施例において、調速器１２の出力軸１３の角変
位を変位／圧力変゛換器１５に伝達するのは、カム機構
１４であったが、リンク機構であってもよい。In the above-described embodiment, the cam mechanism 14 transmits the angular displacement of the output shaft 13 of the speed governor 12 to the displacement/pressure converter 15, but a link mechanism may also be used.
効 果
以上のように本発明に従えば、混圧タービンの制御装置
は、混圧タービンに混圧用作動流体を供給する混圧弁と
、調速器の出力に応答し混圧弁の開度を調速弁の開度の
ｍ＋ａとして連続的に変化する手段とを含んで構成され
る。したがって、調速弁お上り混圧弁を共に用いて混圧
タービンの制御を行なったとき、調定率を可及的に一定
にすることができる。したがって、複数の混圧タービン
およびその制御装置を用いて並列運転を行なうときであ
っても、負荷分担を容易に行な）ことがで軽る。Effects According to the present invention as described above, the control device for a mixed pressure turbine includes a mixed pressure valve that supplies working fluid for mixed pressure to the mixed pressure turbine, and adjusts the opening degree of the mixed pressure valve in response to the output of the speed governor. and means for continuously changing the opening degree of the speed valve as m+a. Therefore, when controlling the mixed pressure turbine using both the speed governor and the mixed pressure valve, the regulation rate can be kept as constant as possible. Therefore, even when performing parallel operation using a plurality of mixed pressure turbines and their control devices, load sharing can be easily performed.
第１図は本発明の一実施例の混圧タービン１の制御装置
２の構成を示す回路図、第２図はカム機構１４に関連す
る構成を示すブロック図、第３図は調速弁４と混圧弁６
とのそれぞれの弁開度の関係を示すグラフ、第４図は制
御装置２の作動状態を説明するグラ・フ、第５図は制御
！１１１２の構成を示すブロック図、第６図は先行技術
の混圧タービンの制御動作を説明するグラフである。
１・・・混圧タービン、２・・・制御装置、４・・・調
速弁、６・・・混圧弁、１２・・・調速器、１４・・・
カム機構、１５・・・変位／圧力変換器
代理人 弁理士 画数 圭一部
第２図
第４図
ｆ４６図FIG. 1 is a circuit diagram showing the configuration of the control device 2 of the mixed pressure turbine 1 according to an embodiment of the present invention, FIG. 2 is a block diagram showing the configuration related to the cam mechanism 14, and FIG. 3 is the governor valve 4. and mixed pressure valve 6
4 is a graph illustrating the operating state of the control device 2, and FIG. 5 is a graph showing the relationship between the valve opening degrees and the control! 1112, and FIG. 6 is a graph explaining the control operation of the prior art mixed pressure turbine. DESCRIPTION OF SYMBOLS 1... Mixed pressure turbine, 2... Control device, 4... Speed governor valve, 6... Mixed pressure valve, 12... Speed governor, 14...
Cam mechanism, 15...Displacement/pressure transducer agent Patent attorney Number of strokes Keiichi 2nd figure 4th figure f46 figure
Claims (1)
械的変位を空気圧力に変換する変位圧力変換器と、空気
圧力によって連続的に開度が調節される混圧弁と、調速
器出力変位を同出力と一対一の関数関係を有する機械的
変位に変換するカム機構あるいはリンク機構とを有する
流圧タービンの制御装置において、 混圧タービンに流圧用作動流体を供給する混圧弁と、 調速器の出力に応答し、混圧弁の開度を調速弁の開度の
関数として連続的に変化する手段とを含むことを特徴と
する混圧タービンの制御装置。[Claims] A mechanical speed governor connected to the output shaft of the mixed pressure turbine, a displacement pressure converter that converts mechanical displacement into air pressure, and an opening degree that is continuously adjusted by the air pressure. In a control device for a fluid pressure turbine that includes a mixed pressure valve and a cam mechanism or link mechanism that converts a governor output displacement into a mechanical displacement that has a one-to-one functional relationship with the same output, the fluid pressure working fluid is supplied to the mixed pressure turbine. and means for continuously changing the opening degree of the mixed pressure valve as a function of the opening degree of the speed governor in response to the output of the speed governor. Device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60062633A JPH0678723B2 (en) | 1985-03-26 | 1985-03-26 | Controller for mixed pressure turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60062633A JPH0678723B2 (en) | 1985-03-26 | 1985-03-26 | Controller for mixed pressure turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61223202A true JPS61223202A (en) | 1986-10-03 |
| JPH0678723B2 JPH0678723B2 (en) | 1994-10-05 |
Family
ID=13205919
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60062633A Expired - Lifetime JPH0678723B2 (en) | 1985-03-26 | 1985-03-26 | Controller for mixed pressure turbine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0678723B2 (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5223006A (en) * | 1975-08-12 | 1977-02-21 | Mitsubishi Petrochem Co Ltd | Process for preparation of isoprene chain dimer |
| JPS54151706A (en) * | 1978-05-19 | 1979-11-29 | Fuji Electric Co Ltd | Turbine control device |
| JPS582402A (en) * | 1981-06-26 | 1983-01-08 | Fuji Electric Co Ltd | Control device of mixed pressure turbine |
-
1985
- 1985-03-26 JP JP60062633A patent/JPH0678723B2/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5223006A (en) * | 1975-08-12 | 1977-02-21 | Mitsubishi Petrochem Co Ltd | Process for preparation of isoprene chain dimer |
| JPS54151706A (en) * | 1978-05-19 | 1979-11-29 | Fuji Electric Co Ltd | Turbine control device |
| JPS582402A (en) * | 1981-06-26 | 1983-01-08 | Fuji Electric Co Ltd | Control device of mixed pressure turbine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0678723B2 (en) | 1994-10-05 |
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