JPH0249904A - Turbine control device - Google Patents
Turbine control deviceInfo
- Publication number
- JPH0249904A JPH0249904A JP19953588A JP19953588A JPH0249904A JP H0249904 A JPH0249904 A JP H0249904A JP 19953588 A JP19953588 A JP 19953588A JP 19953588 A JP19953588 A JP 19953588A JP H0249904 A JPH0249904 A JP H0249904A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- section
- output
- steam
- input
- 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
- 238000000034 method Methods 0.000 claims abstract description 24
- 238000004364 calculation method Methods 0.000 claims description 21
- 238000010248 power generation Methods 0.000 claims description 15
- 238000010586 diagram Methods 0.000 description 6
- 238000000605 extraction Methods 0.000 description 4
- 208000019914 Mental Fatigue Diseases 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Landscapes
- 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、形式及び容量の異なる複数台のタービンを備
えた発電プラントに適用されるタービン制御装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a turbine control device applied to a power generation plant equipped with a plurality of turbines of different types and capacities.
形式及び容量の異なる複数台のタービンを備えた発電プ
ラントでは、これらのタービンを最も効率的に運用し、
蒸気消費量を最小にするために、■タービン出力やター
ビン蒸気流量を測定して運転員の経験則によって各ター
ビン毎に効率を最大にして運転する方法、あるいは■タ
ービンのバルブループに着目してタービンの蒸気加減弁
を測定し、全てのタービンの左点（タービン効率が最も
高い点）近傍で運転する方法などがとられている。In power plants with multiple turbines of different types and capacities, it is necessary to operate these turbines most efficiently and
In order to minimize steam consumption, there are two methods: - Measure the turbine output and turbine steam flow rate and operate each turbine to maximize efficiency based on the operator's rules of experience, or - Focus on the turbine valve loop. One method is to measure the steam control valves of the turbines and operate them near the left point of all turbines (the point where the turbine efficiency is highest).
ところが、実際にはタービンの形式が例えば多段抽気復
水タービン、抽気背圧タービン、背圧タービン、混圧抽
気タービン等と同一でなく、特に産業用蒸気タービンで
は電力需要と蒸気流量の両方を満足しながら運転しなけ
ればならない。しかし、電力需要と蒸気流量を満足しな
がら運転することは非常に困難なことであり、従来では
タービン容量の大きいものから順に左点近傍の運転を行
ない、容量の小さいタービンの蒸気加減弁はそのときの
電力重要と蒸気流量によって決まり、中間開度近傍の運
転となっていた。However, in reality, the types of turbines are not the same, such as multi-stage extraction condensation turbines, extraction back pressure turbines, back pressure turbines, mixed pressure extraction turbines, etc. Especially in industrial steam turbines, it is difficult to satisfy both electric power demand and steam flow rate. I have to drive while driving. However, it is extremely difficult to operate the turbine while satisfying the power demand and steam flow rate, and conventionally the turbines with the largest capacity are operated near the left point, and the steam control valve of the turbine with the smallest capacity is It was determined by the importance of electric power and steam flow rate at the time, and was operated near the middle opening.
第３図はタービンのバルブループを示す図で、同図にお
いて横軸は蒸気加減弁開度を示し、縦軸はタービン出力
を示したものである。一般に蒸気加減弁開度とタービン
出力とは第３図に示すような関係となり、直線とはなら
ない。また、タービン効率はＶ点において最も高く、Ｕ
点のように下に凸の部分では低くなる。さらに、蒸気加
減弁開度と蒸気流量とは一般的に比例関係にあるので、
蒸気ｌ１ｆＥ量とタービン出力とは第４図に示すような
関係となり、直線とはならない。FIG. 3 is a diagram showing the valve loop of the turbine, in which the horizontal axis shows the steam control valve opening, and the vertical axis shows the turbine output. Generally, the steam control valve opening degree and the turbine output have a relationship as shown in FIG. 3, which is not a straight line. Also, the turbine efficiency is highest at point V, and U
It is lower in areas that are convex downwards, such as points. Furthermore, since there is generally a proportional relationship between the steam control valve opening and the steam flow rate,
The amount of steam l1fE and the turbine output have a relationship as shown in FIG. 4, which is not a straight line.
従来技術では上述したように、形式及び容量の異なる複
数台のタービンを時々刻々と変化する電力需要と蒸気需
要を同時に満足しながら最も効率的に運転することは不
可能であった。また、運転員をタービン毎に配置して互
いに連絡をとりながらタービンの蒸気加減弁開度を測定
し、全てのタービンを左点近傍で運転することは非常に
困難で、万一実現したとしても精神的疲労が大き過ぎ、
この作業を長時間実施することは不可能であった。As described above, in the prior art, it has been impossible to operate a plurality of turbines of different types and capacities in the most efficient manner while simultaneously satisfying ever-changing electric power demand and steam demand. In addition, it would be extremely difficult to deploy operators to each turbine and communicate with each other to measure the opening of the turbine's steam control valve and operate all turbines near the left point, and even if it were possible to do so, it would be extremely difficult to do so. Too much mental fatigue
It was impossible to carry out this work for a long time.
本発明はこのような問題点に着目してなされたもので、
形式及び容量の異なる複数台のタービンからなる発電シ
ステム全体の効率を向上させることかできるタービン制
御装置を提供することを目的とするものである。The present invention was made by focusing on these problems.
It is an object of the present invention to provide a turbine control device that can improve the efficiency of the entire power generation system consisting of a plurality of turbines of different types and capacities.
上記課題を解決するために本発明は、形式及び容量の異
なる各タービンのプロセス量を入力するタービンプロセ
ス入力部と、このタービンプロセス入力部からの出力を
入力し時々刻々と変化する電力需要と蒸気需要を予Ｍ１
演算する需要予測演算部と、各タービンの蒸気加減弁の
特性を加味した蒸気流量とタービン出力の特性を設定す
るタービン特性設定部と、このタービン特性設定部から
の出力を入力し蒸気流量とタービン出力の特性を最小二
乗法で直線近似の演算を行なうタービン特性近似部と、
各タービンの運転制約条件を設定するタービン制約設定
部と、このタービン制約設定部と前記タービンプロセス
入力部および需要予測演算部からの各出力を入力し発電
システム全体としての効率が近似的に最大となる各ター
ビンの運転状態を演算する準最適解探索部と、この準最
適解探索部と前記タービン特性設定部およびタービン制
約設定部からの各出力を入力し発電システム全体として
効率が最大となる各タービンの運転状態を演算する最適
解探索部と、この最適解探索部からの出力を入力しター
ビン下位制御装置の設定を変更するタービン設定出力部
とを具備したことを特徴とするものである。In order to solve the above problems, the present invention has a turbine process input section that inputs the process amount of each turbine of different types and capacities, and an output from this turbine process input section that inputs the power demand and steam that changes from moment to moment. Predict demand M1
There is a demand forecast calculation section that calculates the demand forecast, a turbine characteristics setting section that sets the steam flow rate and turbine output characteristics that take into account the characteristics of the steam control valve of each turbine, and a turbine characteristics setting section that inputs the output from this turbine characteristics setting section and sets the steam flow rate and turbine output characteristics. a turbine characteristic approximation unit that performs a linear approximation calculation of the output characteristics using the least squares method;
A turbine constraint setting section sets operational constraints for each turbine, and each output from this turbine constraint setting section, the turbine process input section, and the demand forecasting calculation section is inputted, and the efficiency of the entire power generation system is approximately maximized. A sub-optimal solution search section calculates the operating state of each turbine, and inputs each output from this semi-optimum solution search section, the turbine characteristic setting section, and the turbine constraint setting section to calculate each output state that maximizes the efficiency of the entire power generation system. The present invention is characterized by comprising an optimal solution search section that calculates the operating state of the turbine, and a turbine setting output section that inputs the output from the optimal solution search section and changes the settings of the turbine lower-order control device.
本発明においては、タービンの左点を加味したタービン
特性を用いて蒸気加減弁の設定値の組合せを論理的に決
定しているので、運転員の能力に左右されることなく発
電プラント全体の最適運用が可能となる。In the present invention, the combination of setting values of the steam control valves is determined logically using the turbine characteristics that take into account the left point of the turbine. Therefore, the combination of setting values of the steam control valves is determined logically, so that the overall power generation plant is optimized without being influenced by the ability of the operator. Operation becomes possible.
以下、本発明の一実施例を図面を参照して説明する。 Hereinafter, one embodiment of the present invention will be described with reference to the drawings.
第１図は本発明の一実施例を示すタービン制御装置の概
略（ガ成図で、同図においてタービン制御装置１はター
ビンプロセス入力部２、需要予測演算部３、タービン特
性設定部４、タービン特性近似部５、タービン制約設定
部６、準最適解探索部７、最適解探索部８、タービン出
力設定部９を備えて構成されている。FIG. 1 is a schematic diagram of a turbine control device showing an embodiment of the present invention. It includes a characteristic approximation section 5, a turbine constraint setting section 6, a quasi-optimal solution search section 7, an optimum solution search section 8, and a turbine output setting section 9.
前記タービンプロセス入力部２は、入力群１０から各タ
ービンの蒸気流量と発電電力量を入力するためのもので
、このタービンプロセス入力部２こ入力されたプロセス
量はデジタル量に変換された後、需要予測演算部３およ
び準最適解探索部７に供給される。The turbine process input section 2 is for inputting the steam flow rate and power generation amount of each turbine from the input group 10, and after the process quantities inputted to the turbine process input section 2 are converted into digital quantities, It is supplied to the demand forecast calculation unit 3 and the semi-optimal solution search unit 7.
上記需要予測演算部３は、タービンプロセス入力部２か
らの出力信号をもとに時々刻々と変化する電力需要と蒸
気需要を予測するためのもので、この需要予測演算部３
で得られた電力需要と蒸気需要は準最適解探索部７およ
び最適解探索部８に１共給される。The demand prediction calculation unit 3 is for predicting the electric power demand and steam demand that change from time to time based on the output signal from the turbine process input unit 2.
The electric power demand and steam demand obtained in step 1 are co-supplied to the semi-optimal solution search section 7 and the optimum solution search section 8.
前記タービン特性設定部４は、各タービンの通過蒸気流
量と発生タービン出力から蒸気加減弁の特性を加味した
タービン特性をタービンの段毎に設定するためのもので
、このタービン特性設定部４で設定されたタービン特性
はタービン特性近似部５および最適解探索部８に供給さ
れる。The turbine characteristic setting section 4 is for setting turbine characteristics for each turbine stage, which takes into account the characteristics of the steam control valve based on the passing steam flow rate of each turbine and the generated turbine output. The determined turbine characteristics are supplied to the turbine characteristics approximation section 5 and the optimal solution search section 8.
上記タービン特性近似部５は、タービン特性設定部４で
設定されたタービン特性を最小二乗法で直線近似の演算
を行なうためのもので、このタービン特性近似部５で得
られた演算結果は準最適解探索部７に供給される。The turbine characteristic approximation unit 5 is for calculating the linear approximation of the turbine characteristics set by the turbine characteristic setting unit 4 by the least squares method, and the calculation results obtained by the turbine characteristic approximation unit 5 are suboptimal. It is supplied to the solution search unit 7.
前記タービン制約設定部６は、各タービンの制約条件（
例えばタービン出力の上限及び下限値、抽気流量の上限
及び下限値等）を設定するためのもので、このタービン
制約設定部６で設定された制約条件は準最適解探索部７
および最適解探索部８に供給される。The turbine constraint setting unit 6 sets constraint conditions (
For example, the upper and lower limits of the turbine output, the upper and lower limits of the extraction flow rate, etc.) are used to set the constraint conditions set by the turbine constraint setting section 6.
and is supplied to the optimal solution search unit 8.
前記準最適解探索部７は、タービンプロセス入力部２．
需要予測演算部３．タービン特性近似部５およびタービ
ン制約設定部６からの出力信号を受は取り、発電システ
ム全体として効率が近似的に最大となる各タービンの運
転状態を演算するためのもので、この準最適解探索部７
で得られた演算結果は最適解探索部８に供給される。The quasi-optimal solution search unit 7 includes a turbine process input unit 2.
Demand forecast calculation unit 3. It receives and receives output signals from the turbine characteristic approximation unit 5 and the turbine constraint setting unit 6, and calculates the operating state of each turbine that approximately maximizes the efficiency of the entire power generation system, and performs this quasi-optimal solution search. Part 7
The calculation results obtained are supplied to the optimal solution search section 8.
前記最適解探索部８は、需要予測演算部３．タービン特
性設定部５．タービン制約設定部６および準最適解探索
部７からの出力信号を受は取り、発電システム全体とし
ての効率が最大となる各タービンの運転状態を演算する
ためのもので、この最適解探索部８で得られた演算結果
はタービン出力設定部９に供給される。なお、準最適解
探索部７と最適解探索部８を別々に設けた理由は、複数
台のタービンからなる発電システム全体の効率を最大に
近づける演算をソフト的に高速に行ない、タービン運転
周期を短くできるようにし、時々刻々と変化する環境に
速やかに対応できるするためである。また、第４図に示
すように蒸気流量とタービン出力との関係は非線形のた
め、複数台のタービンからなる発電システム全体の効率
が最大となる点が多数存在し、どの効率最大点を選ぶか
によって演算の初期状態が左右され、タービン操作量が
不必要に大きくなる場合が生じるが、そのような現象を
回避し、タービンに悪影響を与えない安定した運転かで
きるようにするためである。The optimal solution search section 8 includes a demand forecast calculation section 3. Turbine characteristic setting section 5. This optimal solution search unit 8 receives and receives output signals from the turbine constraint setting unit 6 and the semi-optimal solution search unit 7, and calculates the operating state of each turbine that maximizes the efficiency of the entire power generation system. The calculation results obtained are supplied to the turbine output setting section 9. The reason why the quasi-optimal solution search section 7 and the optimum solution search section 8 are provided separately is that calculations that bring the efficiency of the entire power generation system consisting of multiple turbines close to the maximum are performed at high speed using software, and the turbine operation cycle can be shortened. This is to make it shorter and to be able to respond quickly to the ever-changing environment. Furthermore, as shown in Figure 4, since the relationship between steam flow rate and turbine output is non-linear, there are many points where the efficiency of the entire power generation system consisting of multiple turbines is maximum, and it is difficult to choose which point has the maximum efficiency. This is to avoid such a phenomenon and to enable stable operation that does not adversely affect the turbine, although the initial state of the calculation may be affected by this, and the amount of turbine operation may become unnecessarily large.
前記タービン出力設定部９は、最適解探索部８からの出
力信号を受は取り、タービン下位制御装置の設定を変更
するためのものである。The turbine output setting section 9 is for receiving and receiving an output signal from the optimum solution searching section 8 and changing the settings of the turbine lower-order control device.
第２図は第１図に示したタービン制御装置１を複数台の
タービンから構成される発電プラントに適用した場合の
実施例を示す図で、同図において１２８〜１２ｅはター
ビン下位制御装置、１３ａ〜１３ｅは蒸気加減弁駆動部
、１４ａ〜１４ｅは蒸気加減弁、１５ａ〜１５ｃはター
ビン、１６ａ〜１６ｄは流量検出器、１７ａ〜１７ｃは
電力検出器、１８は高圧蒸気母管、１９は低圧蒸気母管
である。FIG. 2 is a diagram showing an embodiment in which the turbine control device 1 shown in FIG. 1 is applied to a power generation plant consisting of a plurality of turbines. - 13e are steam control valve drive parts, 14a to 14e are steam control valves, 15a to 15c are turbines, 16a to 16d are flow rate detectors, 17a to 17c are power detectors, 18 is a high pressure steam main pipe, and 19 is a low pressure steam It is the mother pipe.
次にこのようなも■成される本実施例の作用について説
明する。Next, an explanation will be given of the operation of this embodiment, which is constructed as described above.
第２図に示すような構成によると、各タービン１５ａ〜
１５ｃの蒸気流量と発電電力量は流量検出器１６ａ〜１
６ｄおよび電力検出器１７ａ〜１７ｃによって検出され
、これらの検出器１６ａ〜１６ｄ及び１７ａ〜１７ｃよ
り出力された信号は第１図に示すタービン制御装置１の
タービンプロセス部２に入力される。このタービンプロ
セス部２では各検出器１６ａ〜１６ｄ及び１７ａ〜１７
ｃからの出力信号をデジタル信号に変換し、プロセスデ
ータとして需要予測演算部３およびゃ最適解探索部７に
出力する。そして、需要予測演算部３ではタービンプロ
セス部２からの出力信号をもとに電力需要Ｗを（１）式
から算出するとともに、高圧工場送気系統の蒸気需要Ｇ
Ｉ４と低圧工場送気系統の蒸気需要ＧＬを夫々（２）
及び（３）式から算出する。According to the configuration shown in FIG. 2, each turbine 15a to
The steam flow rate and generated power amount of 15c are determined by flow rate detectors 16a to 1.
6d and power detectors 17a to 17c, and the signals output from these detectors 16a to 16d and 17a to 17c are input to the turbine process section 2 of the turbine control device 1 shown in FIG. In this turbine process section 2, each detector 16a to 16d and 17a to 17
The output signal from c is converted into a digital signal and output as process data to the demand forecast calculation section 3 and the optimal solution search section 7. Then, the demand forecast calculation unit 3 calculates the electric power demand W from the equation (1) based on the output signal from the turbine process unit 2, and also calculates the steam demand G of the high-pressure factory air supply system.
Steam demand GL for I4 and low-pressure factory air supply system, respectively (2)
Calculated from equation (3).
ｗ−ｗａ ＋ｗｂ ＋Ｗｃ −（１）ＧＨ−Ｇａ ＋
Ｇｂ ＋Ｇｃ −（２）ＧＬ−Ｇｃ・・・（３）
ここで、Ｗａ 、 Ｗｂ 、 Ｗｅ ：電力検出器１７
ａ。w-wa +wb +Wc -(1)GH-Ga +
Gb + Gc - (2) GL - Gc... (3) Here, Wa, Wb, We: Power detector 17
a.
１７ｂ、１７ｃの出力信号に基づいた発電電力量、Ｇａ
、Ｇｂ、Ｇｃ ：流量検出器１６ａ、１６ｂ。The amount of power generated based on the output signals of 17b and 17c, Ga
, Gb, Gc: flow rate detectors 16a, 16b.
１６ｃの出力信号に基づいた蒸気流量である。This is the steam flow rate based on the output signal of 16c.
また、これと同時にタービン特性設定部４では各タービ
ン１５ａ〜１５ｃの通過蒸気流量と発生タービン出力か
ら蒸気加減弁１４ａ〜１４ｅの特性を加味したタービン
特性関数Ｆ ｎｉ （１＝１，５）を（４）式より作成
する。At the same time, the turbine characteristic setting unit 4 calculates a turbine characteristic function F ni (1=1,5) (1=1,5) which takes into consideration the characteristics of the steam control valves 14a to 14e from the passing steam flow rate and generated turbine output of each turbine 15a to 15c. 4) Create from the formula.
Ｗ−Ｆ 口１ （Ｇ） ・・・ （４）ただし、Ｗ
：タービン出力、Ｇ：タービンの段通遍蒸気流量、Ｆｎ
ｌ〜Ｆｎ５：各タービン１５ａ〜１５ｃのタービン特性
関数である。W-F mouth 1 (G) ... (4) However, W
: Turbine output, G: Steam flow rate across stages of the turbine, Fn
1 to Fn5: Turbine characteristic functions of each of the turbines 15a to 15c.
このようにして需要予ａｌｌ演算部３で得られた電力需
要Ｗと蒸気流Ｑ Ｇ １１ 、 Ｇ Ｌは、前述した如
く準最適解探索部７および最適解探索部８に入力され、
準最適解探索部７では需要予測演算部３で得られた電力
需要Ｗと蒸気流＝ｃＨ，ｃｒＬを同時に満たし、かつタ
ービン制約設定部６で設定された制約条件の範囲内で各
タービン１５ａ〜１５ｃの消費蒸気流量が最小となる蒸
気加減弁１４ａ〜１４ｅの設定値の組合せについてター
ビン特性近似部５で得られたタービン特性関数Ｆ ｅｊ
（ｉ−１，５）を用いて探索する。また、最適解探索
部８では準最適解探索部７で探索した蒸気加減弁１４ａ
〜１４ｅの設定値を初期状態として、需要予測演算部３
で得られた電力需要Ｗと蒸気流Ｑ Ｇ Ｈ、、Ｇ Ｌを
同時に満たし、かつタービン制約設定部６で設定された
制約条件の範囲内で各タービン１５ａ〜１５ｃの消費蒸
気流量が最小となる蒸気加減弁１４ａ〜１４ｅの設定値
の組合せについてタービン特性設定部４で得られたター
ビン特性関数Ｆｎｉ（１−１，５）を用いて探索する。The power demand W and steam flow Q G 11 , G L thus obtained by the demand forecast all calculation unit 3 are inputted to the semi-optimal solution search unit 7 and the optimal solution search unit 8 as described above,
The quasi-optimal solution search unit 7 simultaneously satisfies the power demand W and steam flow = cH, crL obtained by the demand prediction calculation unit 3, and operates each turbine 15a to 15a within the range of constraint conditions set by the turbine constraint setting unit 6. The turbine characteristic function F ej obtained by the turbine characteristic approximation unit 5 for the combination of setting values of the steam control valves 14a to 14e that minimizes the consumed steam flow rate of 15c
Search using (i-1, 5). In addition, the optimum solution search section 8 also uses the steam control valve 14a searched by the quasi-optimum solution search section 7.
With the setting values of ~14e as the initial state, the demand forecast calculation unit 3
The power demand W and the steam flow QGH, GL obtained in the above are simultaneously satisfied, and the consumed steam flow rate of each turbine 15a to 15c is minimized within the constraint conditions set by the turbine constraint setting unit 6. Combinations of set values for the steam control valves 14a to 14e are searched for using the turbine characteristic function Fni (1-1, 5) obtained by the turbine characteristic setting section 4.
そして、最適解探索部８で得られた蒸気加減弁１４ａ〜
１４ｅの設定値はタービン出力設定部９に入力される。Then, the steam control valves 14a~ obtained by the optimal solution search unit 8
The set value 14e is input to the turbine output setting section 9.
したがって、タービン出力設定部９では最適解探索部８
で得られた蒸気加減弁１４ａ〜１４ｅの設定値に基づい
てタービン下位制御装置１２ａ〜１２ｅの出力を変更す
る。Therefore, in the turbine output setting section 9, the optimum solution searching section 8
The outputs of the turbine lower control devices 12a to 12e are changed based on the set values of the steam control valves 14a to 14e obtained in .
このように本実施例においては、タービンの左点を加味
したタービン特性を用いて蒸気加減弁の設定値の組合わ
せを論理的に決定しているので、運転員の能力に左右さ
れることなく発電プラント全体の最適運用が可能となる
。In this way, in this example, the combination of steam control valve setting values is determined logically using the turbine characteristics that take into account the left point of the turbine, so it is not affected by the ability of the operator. This enables optimal operation of the entire power plant.
なお、本発明のタービン制御装置は第２図に示した発電
プラント以外についても適用可能であることは勿論であ
る。It goes without saying that the turbine control device of the present invention can also be applied to power plants other than those shown in FIG. 2.
以上説明したように本発明は、タービンの左点を加味し
たタービン特性を用いて蒸気加減弁の設定値の組合わせ
を論理的に決定しているので、運転員の能力に左右され
ることなく発電プラント全体の最適運用が可能となり、
発電プラントの高効率化および省エネルギ化が図れる。As explained above, the present invention logically determines the combination of set values for the steam control valves using the turbine characteristics that take into account the left point of the turbine, so it is not affected by the ability of the operator. This enables optimal operation of the entire power plant,
High efficiency and energy saving of power generation plants can be achieved.
第１図は本発明の一実施例を示すタービン制御装置の構
成図、第２図は第１図に示したタービン制御装置を複数
台のタービンから構成される発電プラントに適用した場
合の実施例を示す図、第３図はタービンのバルブループ
を示す図、第４図はタービンの出力特性曲線を示す図で
ある。
１・・・タービンＦＩＩ１１御装置ｕ１２・・・タービ
ンプロセス入力部、３・・・需要予測演算部、４・・・
タービン特性設定部、５・・・タービン特性近似部、６
・・・タービン制約設定部、７・・・儒最適解探索部、
８・・・最適解探索部、９・・・タービン出力設定部。
出願人代理人 弁理士 鈴江武彦FIG. 1 is a configuration diagram of a turbine control device showing one embodiment of the present invention, and FIG. 2 is an example in which the turbine control device shown in FIG. 1 is applied to a power generation plant consisting of a plurality of turbines. FIG. 3 is a diagram showing the valve loop of the turbine, and FIG. 4 is a diagram showing the output characteristic curve of the turbine. DESCRIPTION OF SYMBOLS 1...Turbine FII11 control device u12...Turbine process input section, 3...Demand forecast calculation section, 4...
Turbine characteristic setting section, 5...Turbine characteristic approximation section, 6
... Turbine constraint setting section, 7... Confucian optimal solution search section,
8... Optimum solution search unit, 9... Turbine output setting unit. Applicant's agent Patent attorney Takehiko Suzue
Claims (1)
るタービンプロセス入力部と、このタービンプロセス入
力部からの出力を入力し時々刻々と変化する電力需要と
蒸気需要を予測演算する需要予測演算部と、各タービン
の蒸気加減弁の特性を加味した蒸気流量とタービン出力
の特性を設定するタービン特性設定部と、このタービン
特性設定部からの出力を入力し蒸気流量とタービン出力
の特性を最小二乗法で直線近似の演算を行なうタービン
特性近似部と、各タービンの運転制約条件を設定するタ
ービン制約設定部と、このタービン制約設定部と前記タ
ービンプロセス入力部および需要予測演算部からの各出
力を入力し発電システム全体としての効率が近似的に最
大となる各タービンの運転状態を演算する準最適解探索
部と、この準最適解探索部と前記タービン特性設定部お
よびタービン制約設定部からの各出力を入力し発電シス
テム全体として効率が最大となる各タービンの運転状態
を演算する最適解探索部と、この最適解探索部からの出
力を入力しタービン下位制御装置の設定を変更するター
ビン設定出力部とを具備したことを特徴とするタービン
制御装置。a turbine process input section that inputs the process amount of each turbine of different type and capacity; a demand prediction calculation section that inputs the output from the turbine process input section and predicts and calculates ever-changing electric power demand and steam demand; There is a turbine characteristic setting section that sets the characteristics of steam flow rate and turbine output, taking into account the characteristics of the steam control valve of each turbine, and the output from this turbine characteristic setting section is input and the characteristics of steam flow rate and turbine output are determined by the least squares method. A turbine characteristic approximation unit that performs linear approximation calculations, a turbine constraint setting unit that sets operational constraints for each turbine, and inputs each output from this turbine constraint setting unit, the turbine process input unit, and the demand forecast calculation unit. A quasi-optimal solution search section that calculates the operating state of each turbine that approximately maximizes the efficiency of the entire power generation system, and each output from the quasi-optimum solution search section, the turbine characteristic setting section, and the turbine constraint setting section. an optimal solution search section that inputs the input and calculates the operating state of each turbine that maximizes the efficiency of the entire power generation system, and a turbine setting output section that inputs the output from this optimal solution search section and changes the settings of the turbine lower control device. A turbine control device comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19953588A JPH0814241B2 (en) | 1988-08-10 | 1988-08-10 | Turbine controller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19953588A JPH0814241B2 (en) | 1988-08-10 | 1988-08-10 | Turbine controller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0249904A true JPH0249904A (en) | 1990-02-20 |
| JPH0814241B2 JPH0814241B2 (en) | 1996-02-14 |
Family
ID=16409451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19953588A Expired - Lifetime JPH0814241B2 (en) | 1988-08-10 | 1988-08-10 | Turbine controller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0814241B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0450409A (en) * | 1990-06-19 | 1992-02-19 | Nippon Steel Corp | Steam pressure control device |
| US5309773A (en) * | 1990-09-13 | 1994-05-10 | Hajime Industries Ltd. | Powder and granule inspection apparatus |
| WO1996010219A1 (en) * | 1994-09-26 | 1996-04-04 | Kabushiki Kaisha Toshiba | Method and system for optimizing plant utility |
| JP2000078749A (en) * | 1998-08-31 | 2000-03-14 | Mitsubishi Chemicals Corp | Power plant optimization control method and optimization control device |
| JP2000078750A (en) * | 1998-08-31 | 2000-03-14 | Mitsubishi Chemicals Corp | Optimal operation control method and optimal operation control device for power plant |
| JP2008223702A (en) * | 2007-03-15 | 2008-09-25 | Tlv Co Ltd | Control device of process steam utilizing steam turbine |
| JP2008223701A (en) * | 2007-03-15 | 2008-09-25 | Tlv Co Ltd | Control device of process steam utilizing steam turbine |
| WO2010097891A1 (en) * | 2009-02-24 | 2010-09-02 | 株式会社 東芝 | Plant optimum-operation control system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5730833B2 (en) * | 2012-09-21 | 2015-06-10 | 株式会社日立製作所 | Turbine control device, turbine control method, and turbine control program |
-
1988
- 1988-08-10 JP JP19953588A patent/JPH0814241B2/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0450409A (en) * | 1990-06-19 | 1992-02-19 | Nippon Steel Corp | Steam pressure control device |
| US5309773A (en) * | 1990-09-13 | 1994-05-10 | Hajime Industries Ltd. | Powder and granule inspection apparatus |
| WO1996010219A1 (en) * | 1994-09-26 | 1996-04-04 | Kabushiki Kaisha Toshiba | Method and system for optimizing plant utility |
| US5886895A (en) * | 1994-09-26 | 1999-03-23 | Kabushiki Kaisha Toshiba | Plant utility optimizing method and an optimizing system |
| JP2000078749A (en) * | 1998-08-31 | 2000-03-14 | Mitsubishi Chemicals Corp | Power plant optimization control method and optimization control device |
| JP2000078750A (en) * | 1998-08-31 | 2000-03-14 | Mitsubishi Chemicals Corp | Optimal operation control method and optimal operation control device for power plant |
| JP2008223702A (en) * | 2007-03-15 | 2008-09-25 | Tlv Co Ltd | Control device of process steam utilizing steam turbine |
| JP2008223701A (en) * | 2007-03-15 | 2008-09-25 | Tlv Co Ltd | Control device of process steam utilizing steam turbine |
| WO2010097891A1 (en) * | 2009-02-24 | 2010-09-02 | 株式会社 東芝 | Plant optimum-operation control system |
| CN102057338A (en) * | 2009-02-24 | 2011-05-11 | 株式会社东芝 | Plant optimum-operation control system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0814241B2 (en) | 1996-02-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN114320867B (en) | A kind of intelligent operation method and system for variable frequency speed regulation of water supply pump set | |
| JP2020517227A (en) | A short-term practical scheduling method for ultra-large-scale hydropower plants | |
| CN105114242A (en) | Hydro governor parameter optimization method based on fuzzy self-adaptive DFPSO algorithm | |
| CN110070460A (en) | More set gas-steam combined cycle set thermoelectricity Optimal Load Dispatching Systems | |
| CN102242868B (en) | Steam pipe network optimized operation method of industrial device | |
| CN103745023A (en) | Coupling modeling method for hydropower station power generated output scheme making and optimal load distribution | |
| CN107420142B (en) | A kind of Turbine Cold Junction optimization progress control method following pump based on frequency conversion | |
| CN112613244B (en) | Steam transportation pipe network operation energy efficiency optimization method based on data analysis | |
| CN103020742A (en) | Short-term optimization scheduling method for cascade hydropower stations with multiple limited operation areas | |
| JPH0249904A (en) | Turbine control device | |
| Kim et al. | Design of incremental fuzzy PI controllers for a gas-turbine plant | |
| CN115263643B (en) | Water turbine primary frequency modulation control method and system based on self-adaptive control characteristics | |
| CN106089326A (en) | Dry coke quenching heat recovery steam electric turbine enters, steam discharge control method | |
| CN201292954Y (en) | Water pump and/or blower fan highly effective energy-conserving control system | |
| Makwana et al. | A novel approach for retrofit and operations management of existing total sites | |
| CN105065191A (en) | Method for stabilizing system after accelerating high-head hydro-power generating unit load reduction | |
| CN107525348B (en) | Multivariable predictive control method for air separation device | |
| CN112348414A (en) | Load distribution adjustment method based on the operation mode of circulating water system | |
| KR20230101320A (en) | Data processing method for energy saving of heat treatment furnance by artificial intelligence | |
| CN113339177A (en) | Method for analyzing and evaluating main parameters and performance indexes of large water turbine | |
| CN110048468B (en) | Load distribution method and device for thermal power plant units | |
| CN119195965A (en) | Water turbine speed control system and method with intelligent parameter adjustment | |
| CN111255532A (en) | Optimized operation control method for industrial self-contained power station | |
| CN118399490A (en) | Hydropower station unit load distribution method and system for improving dynamic planning algorithm | |
| CN114723104A (en) | Energy consumption optimization comprehensive modeling method and system for electrical equipment in engine room of wind turbine generator |