JPS6232393A - Turbine controller for nuclear reactor plant - Google Patents
Turbine controller for nuclear reactor plantInfo
- Publication number
- JPS6232393A JPS6232393A JP60171064A JP17106485A JPS6232393A JP S6232393 A JPS6232393 A JP S6232393A JP 60171064 A JP60171064 A JP 60171064A JP 17106485 A JP17106485 A JP 17106485A JP S6232393 A JPS6232393 A JP S6232393A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- turbine
- bypass valve
- nuclear reactor
- valve
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E30/00—Energy generation of nuclear origin
Landscapes
- Control Of Turbines (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、原子炉プラントのタービン制御装置に関する
ものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a turbine control device for a nuclear reactor plant.
従来の原子炉プラントのタービン制御装置としては、特
開昭６０−５３８９５号公報の第１図に示すものが知ら
れている。すなわち、沸騰水型原子炉の原子炉圧力容器
にて発生した蒸気は、主蒸気管を通ってタービンに供給
される。主蒸気管には。As a conventional turbine control device for a nuclear reactor plant, one shown in FIG. 1 of Japanese Patent Application Laid-Open No. 60-53895 is known. That is, steam generated in a reactor pressure vessel of a boiling water reactor is supplied to a turbine through a main steam pipe. In the main steam pipe.
タービンへの蒸気流量を調節する蒸気加減弁が設けられ
ている。バイパス管が蒸気加減弁の上流側で主蒸気管に
接続され、さらに復水器に接続される。バイパス弁がバ
イパス管に設けられる。A steam control valve is provided to adjust the steam flow rate to the turbine. A bypass pipe is connected to the main steam pipe upstream of the steam control valve and further connected to the condenser. A bypass valve is provided on the bypass pipe.
蒸気力旧威弁は、プラントの通常運転時には、蒸気圧力
に塙づいて制御信号を出力する圧力調整器の出力信号Ｖ
Ｃ基づいて開度を制御されている。しか［−２電力系統
の負荷が急激に減少すると、タービンの回転数が上昇す
る。この場合には、タービン回転数を入力して制御信号
を出力するタービン速度制御器の出力信号が圧力調整器
の出力信号に優先され、タービン速度制御器の出力信号
により蒸気加減弁の開度が制御される。During normal operation of the plant, the steam power regulator outputs the output signal V of the pressure regulator that outputs a control signal based on the steam pressure.
The opening degree is controlled based on C. However, [-2 When the load on the power system decreases rapidly, the rotational speed of the turbine increases. In this case, the output signal of the turbine speed controller, which inputs the turbine speed and outputs the control signal, has priority over the output signal of the pressure regulator, and the output signal of the turbine speed controller controls the opening degree of the steam control valve. controlled.
バイパス弁は１通常運転時には圧力調整器の出力信号に
基づいてサーボアンプにより緩やかに開度が制御される
。電力系統の負荷が恐、激に減少した場合には、圧力調
整器の出力信号を入力して電磁急開弁が動作し、バイパ
ス弁の開度が急開する。During normal operation, the opening degree of the bypass valve is gently controlled by a servo amplifier based on the output signal of the pressure regulator. When the load on the power system suddenly decreases, the output signal from the pressure regulator is input to operate the electromagnetic quick-open valve, and the opening of the bypass valve is suddenly opened.
このような原子炉プラントのタービン制御装置では、蒸
気加減弁の開度の増減とバイパス弁の開度の減増が１対
１に対応しない。In such a turbine control device for a nuclear reactor plant, the increase/decrease in the opening degree of the steam control valve does not correspond one-to-one with the decrease/increase in the opening degree of the bypass valve.
本発明の目的は、信頼性が高くしかも電力系統にじよう
乱が生じた場合でも原子炉を継続して運転することので
きる原子炉プラントのタービン制御装置を提供すること
にある。SUMMARY OF THE INVENTION An object of the present invention is to provide a turbine control device for a nuclear reactor plant that has high reliability and is capable of continuously operating a nuclear reactor even when a disturbance occurs in the power system.
本発明の特徴は、蒸気加減弁の開度を検出する手段と、
圧力調整器及び前記開度検出手段の出力信号に基づいて
バイパス弁の開度を制御する制御手段を備えたことにあ
る。The features of the present invention include means for detecting the opening degree of the steam control valve;
The present invention further includes a control means for controlling the opening degree of the bypass valve based on the output signal of the pressure regulator and the opening degree detection means.
従来の原子炉プラントのタービン制御装置のバイパス弁
サーボの機能を以下に示す。このバイパス弁サーボ２７
０ロ路の機能を第２図に基づいて説明する。The functions of the bypass valve servo in a conventional nuclear reactor plant turbine control device are shown below. This bypass valve servo 27
The function of the 0-ro road will be explained based on FIG.
一般にバイパス弁は複数個設けられている。プラントの
通常運転では／−ケンンヤルにバイパス弁１５ ａ、
１５ ｂ、・・・、１５ｎの順に開くようにバイパス
弁閉バイアス設定器３９ａｌ ３９ｂ、・・・３９ｎ
の値を段階的に設定しておく。もしバイパス弁が８個で
あり、全容量が１００％であれば。Generally, a plurality of bypass valves are provided. In normal operation of the plant/-bypass valve 15 a,
Bypass valve closing bias setting device 39al to open in order of 15b,...,15n 39b,...39n
Set the values in stages. If there are 8 bypass valves and the total capacity is 100%.
増幅器４０のゲインは、入力１００チで８００チ（＝１
ｏｏｓｘｓ弁）のイ；号がでるように８倍（＝Ｂｏｏ％
÷１００幅）とする。そして。The gain of the amplifier 40 is 800chi (=1) with an input of 100chi.
oosxs valve)'s A; 8 times (=Boo%) so that the number appears
÷100 width). and.
バイアス設定器３９ａに０％
バイアス設定器３９ｂに８００係÷８＝１００多バイア
ス設定？５３９Ｃに２００幅
バイアス設定器３９ｈに７００％
のバイアスをそれぞれかケテオく。0% in bias setting device 39a 800 coefficient ÷ 8 = 100 multi-bias setting in bias setting device 39b? Set a 700% bias to the 200 width bias setter 39h on the 539C.
第６図に示すごとく、バイパス弁開度要求信号が０〜１
００％まで徐々に変化すると、増巾器４０の出力け０〜
８００％まで徐々に変化する。As shown in Figure 6, the bypass valve opening request signal is 0 to 1.
When it gradually changes to 00%, the output of the amplifier 40 becomes 0~
It gradually changes up to 800%.
これにより、まずバイパス弁１５ａがｔｏｏｓ開度にな
り、その次にバイパス弁１５ｂが開き始めて、２００チ
信号にて
２００％−Ｚｏｏチ＝１００係
開度となる。As a result, the bypass valve 15a first becomes the too opening degree, and then the bypass valve 15b starts to open, and at the 200-chi signal, the opening degree becomes 200%-Zoo-chi=100.
以下同様にして、８００％信号にて、最後である８番目
のバイパス弁１５ｈの開度が
８００チ一７００％＝１００チ
開度になる。Similarly, at the 800% signal, the opening of the eighth and final bypass valve 15h becomes 800 - 700% = 100.
との間の動作を第７図に示す、バイパス弁開度要求信号
の変化が緩慢な場合には、バイパス弁開度要求信号とバ
イパス弁１５ａ、・・・、１５ｈの開度を示す変位検出
器３６ａ、・・・、３６ｈの出力信号との各偏差信号が
大きくならない（５％以内）。When the bypass valve opening request signal changes slowly, displacement detection indicating the bypass valve opening request signal and the opening of the bypass valves 15a, . . . , 15h is shown in FIG. The deviation signals from the output signals of the devices 36a, . . . , 36h do not become large (within 5%).
従って偏差検出器３７ａ、・・・、３７ｈけ動作せず。Therefore, the deviation detectors 37a, . . . did not operate for 37 hours.
バイパス弁開度要求信号を入力するサーボアンプ３３ａ
、−，３３ｈのみによってサーボ弁３４ａ。Servo amplifier 33a that inputs the bypass valve opening request signal
, -, 33h only by the servo valve 34a.
・・・、３４ｈが動作して、油圧シリンダ３５ａ、・・
・。..., 34h operates, and the hydraulic cylinders 35a, ...
・.
３５ｈが動作する。油圧シリンダ３５ａ、・・・。35h works. Hydraulic cylinder 35a,...
３５ｈに直結されたバイパス弁１５ａ、・・・、１５ｈ
は、対応する油圧シリンダ３５ａ、・・・、３５ｈの動
作により開く。Bypass valves 15a, ..., 15h directly connected to 35h
are opened by the operation of the corresponding hydraulic cylinders 35a, . . . , 35h.
バイパス弁開度要求信号の増加速度が急激な場合には、
前述の動作に加えて偏差検出器３７ａ。If the bypass valve opening request signal increases rapidly,
In addition to the operations described above, a deviation detector 37a.
・・・、３７ｈが動作する。これＫよって電磁急開弁３
８ａ、・・・、３８ｈが動作して油圧シリンダ３５ａ。..., 37h operates. Due to this K, electromagnetic quick opening valve 3
8a, . . . , 38h are activated and the hydraulic cylinder 35a is activated.
・・・、３５ｈに作動油を急速に注入し、バイパス弁１
５ａ、・・・、１５ｈを急開する。..., 35h, rapidly inject hydraulic oil, bypass valve 1
Rapidly open 5a,..., 15h.
さて、ここで蒸気加減弁とバイパス弁１５の開閉特性お
よびそれに伴う蒸気流量特性について説明する。Now, the opening/closing characteristics of the steam control valve and the bypass valve 15 and the accompanying steam flow characteristics will be explained.
第８図に通常信号による蒸気加減弁の開閉特性と全蒸気
流量特性を示す。蒸気加減弁は４個設けられており、制
御信号に之ってそれらの４弁とも同時に開閉する。蒸気
加減弁の全閉から全開までに要する最短時間は約１０秒
程度である。弁開度と蒸気ｊ［ｆＬの特性は、第１０図
に示す様になって訃り、１００％蒸気流量を流すのには
蒸気加減弁の開度を約５０％すればよい。それ以上の開
度では、非線形特性によって、蒸気流Ｏはせいぜい５チ
位しか増加しない。そのため、蒸気加減弁の開度と全蒸
気流徒との関係は第７図に示すようになる。FIG. 8 shows the opening/closing characteristics of the steam control valve and the total steam flow rate characteristics according to the normal signal. Four steam control valves are provided, and all four valves open and close simultaneously in response to a control signal. The minimum time required from fully closing to fully opening the steam control valve is about 10 seconds. The characteristics of the valve opening and steam j[fL are as shown in FIG. 10, and in order to flow 100% steam flow, the opening of the steam control valve should be set to about 50%. If the opening is larger than that, the steam flow O will increase by about 5 inches at most due to nonlinear characteristics. Therefore, the relationship between the opening degree of the steam control valve and the total steam flow is as shown in FIG.
第８図に０通常の緩慢な制御信号によるバイパス弁１５
の開閉特性と全蒸気流量特性を示し、８個のバイパス弁
１５ａ、・・・、１５ｈで１００％の蒸気流量を流す場
合を示す。１弁であるバイパス弁１５ａから８弁である
バイパス弁１５ｈｔでは前述のようにシーケンシャルに
順番に動作する。Bypass valve 15 with normal slow control signal in Figure 8
The opening/closing characteristics and the total steam flow rate characteristics are shown, and the case where 100% steam flow is caused to flow through eight bypass valves 15a, . . . , 15h is shown. The bypass valves 15a, which are one valve, to the bypass valves 15ht, which are eight valves, operate sequentially as described above.
バイパス弁開度と蒸気流量との関係は線形であるので、
全蒸気ｉｔは全開のバイパス弁の個数に応じて第８図の
ように変化する。Since the relationship between bypass valve opening and steam flow rate is linear,
The total steam it changes as shown in FIG. 8 depending on the number of fully open bypass valves.
プラントの通常運転時におけるバイパス弁の最短開閉時
間は、哨７図の蒸気加減弁の全蒸気流量の変化速度とバ
イパス弁のそれとがほぼ同程度になるように憫節されて
いる。The shortest opening/closing time of the bypass valve during normal operation of the plant is determined so that the rate of change in the total steam flow rate of the steam control valve shown in Figure 7 is approximately the same as that of the bypass valve.
第９図に急開信号にＬ乙バイパス弁の特性及び蒸気流１
に特性を示す。これは、大きな急開要求信号が瞬時に加
わったものと想定し、結果的に＆１〜８のすべてのバイ
パス弁１５ａ、−・・、１５ｈが同時に急開した場合を
示している。バイパス弁が閉じる場合には、急閉動作機
能は不要であり、制御信号によって閉じる。Figure 9 shows the characteristics of L2 bypass valve and steam flow 1 for the sudden opening signal.
The characteristics are shown below. This shows a case where it is assumed that a large sudden opening request signal is instantaneously applied, and as a result, all the bypass valves 15a, . . . , 15h of &1 to 8 suddenly open simultaneously. When the bypass valve is closed, the quick-closing function is not necessary and the bypass valve is closed by the control signal.
バイパス弁１５ａ、・・・、１５ｈの通常側（２）時サ
ーボ弁３４ａ、・・・、３４ｈによる開速度と、電磁急
開弁３８ａ、・・・、３８ｈによる急開特性とを比較す
ると第６図のように異っている。Comparing the opening speed of the bypass valves 15a, . . . , 15h on the normal side (2) by the servo valves 34a, . They are different as shown in Figure 6.
以上述べてきた従来例のタービン制御系を有する原子炉
プラントにおいて、第１１図（ａ）に示すように時間ｔ
１〜ｔ！の間で電力系統の一時的な部分負荷急減が生じ
るものとする。In a nuclear reactor plant having the conventional turbine control system described above, as shown in FIG. 11(a), the time t
1~t! It is assumed that a temporary partial load drop occurs in the power system between
この場合、第１１図中）のようにタービン速度（タービ
ン回転数）が一時的に上昇する。これを回転速度計は、
このタービン速度を検出してタービン速度制御器に出力
する。タービン速度制御器の出力信号Ｓ１は小さくなり
、０．５％以上タービン速度が上昇すると、 Ｓ １＜
Ｐ ＋ となる（Ｐｔ は圧力調整器の出力信号）。In this case, the turbine speed (turbine rotation speed) temporarily increases as shown in FIG. 11). This is the tachometer,
This turbine speed is detected and output to a turbine speed controller. The output signal S1 of the turbine speed controller becomes small, and when the turbine speed increases by more than 0.5%, S1<
P + (Pt is the output signal of the pressure regulator).
従って、信号Ｓｔが低値選択回路を通り、加減弁サーボ
２４に伝達されてる。加減弁サーボは、信号Ｓ１に基づ
いて蒸気加減弁の開度を減少させるので、蒸気加減弁を
通過する蒸気流ｆｉ（以下、加減弁流量という）が減少
しはじめる。第１１図（ａ）のように電力系統の負荷急
減が時間ｔ１で発生すると、Ｓ＋−Ｐ＋ となる時間ｔ
、以降に第１１図（Ｃ）に示すように加減弁流量要求信
号が減少しはじめる。これとほぼ時を同じくして、第１
１図（ｅ） Ｋ示すようにバイパス弁開度要求信号（Ｐ
＋ Ｃｔ）が増加する。なお。Therefore, the signal St passes through the low value selection circuit and is transmitted to the control valve servo 24. Since the control valve servo reduces the opening degree of the steam control valve based on the signal S1, the steam flow fi passing through the steam control valve (hereinafter referred to as control valve flow rate) begins to decrease. As shown in Fig. 11(a), when a sudden load drop in the power system occurs at time t1, the time t at which S+ - P+ is reached.
, thereafter, the regulating valve flow rate request signal begins to decrease as shown in FIG. 11(C). Around the same time, the first
As shown in Figure 1(e), the bypass valve opening request signal (P
+Ct) increases. In addition.
Ｃ１は低値選択回路の出力信号である。第１１図（Ｃ）
に示す二うに加減弁流量要求信号は、急激に減少するが
１時間ｔ３にて第１１図（ａ）に示すように電力系統負
荷が復帰すると、タービン速度が第１１図（ｂ）の如く
減少に転じるので、加減弁流量要求信号は増加に転じる
。第１１図（ｄ）に示す加減弁流量の変化速度は、加減
弁サーボによって、第７図に示すような開閉速度制限が
あるために第１１図（ｄ）に示すように比較的緩やかに
減少し、その後。C1 is the output signal of the low value selection circuit. Figure 11 (C)
As shown in Figure 11(a), the regulator valve flow rate request signal rapidly decreases, but when the power system load returns at 1 hour t3 as shown in Figure 11(a), the turbine speed decreases as shown in Figure 11(b). Therefore, the control valve flow rate request signal starts to increase. The rate of change in the flow rate of the control valve shown in Fig. 11(d) decreases relatively slowly as shown in Fig. 11(d) because there is an opening/closing speed limit as shown in Fig. 7 due to the control valve servo. And then.
第１１図（ｅ）の加減弁流量要求信号の大きさ相当にな
った時間ｔ４にて減少から増加に転じる。第１１図（ｅ
）のように時間ｔ２からバイパス弁開度要求信号が急増
すると、バイパス弁急開機構が動作して第１１図（０の
ようにバイパス弁の必要個数が１つずつわずかな時間差
を以って急開する。このとき時間ｔ３にて第１１図（Ｃ
）に示すように加減弁流量要求信号が増加に転じたこと
により、第１１図（ｅ）に示すようにバイパス弁開度要
求信号は減少に転じる。これに応じて第１１図（ｆ）の
よりにバイパス弁流量も減少に転じる。At time t4, when the magnitude of the control valve flow rate request signal in FIG. 11(e) becomes equivalent, the decrease changes to an increase. Figure 11 (e
) When the bypass valve opening request signal rapidly increases from time t2, the bypass valve rapid opening mechanism operates and the required number of bypass valves is increased one by one with a slight time difference as shown in FIG. 11 (0). At this time, at time t3, as shown in Fig. 11 (C
) As the control valve flow rate request signal starts to increase, the bypass valve opening degree request signal starts to decrease as shown in FIG. 11(e). Correspondingly, the bypass valve flow rate also begins to decrease as shown in FIG. 11(f).
第１１図（ａ）に示すように時間ｔ３にて電力系統負荷
が復帰したこと及び第１１図（ｄ）のように加減弁流量
が一時的に減少したことにより、タービン速度は第１１
図中）に示すように元の速度に向けて降下して時間ｔ５
にて整定する。はぼこの時点でＱｎ減弁流４要求信号は
第１１図（Ｃ）の如く元の値に戻り、バイパス弁開度要
求信号も第１１図（ｅ）のように零にもどる。加減弁サ
ーボおよびバイパス弁サーボには、第７図及び第８図に
示すような開閉速度変化制限があるので加減弁流量は、
’ｇｌ１図（ｄ）のように時間ｔ、より遅れた時間ｔ６
にて元の値に戻り、バイパス弁流量も第１１図（ｆ）の
よりに時間ｔ７にて零に戻る。このように、加減弁流量
とバイパス弁流量の応答特性に差があるために、タービ
ン入口圧力は第１１図（ｇ）に示すように一時的に減少
してから元の状態に回復する。この圧力変化け２時間１
γれをもって原子炉圧力容器内に伝播され、原子炉圧力
容器内で減衰させられて第１１図中）のような変化とな
る。As shown in FIG. 11(a), the power system load was restored at time t3, and as shown in FIG. 11(d), the flow rate of the regulator valve temporarily decreased, so that the turbine speed decreased to the 11th
As shown in (in the figure), the vehicle descends to its original speed at time t5.
Set it at . At the point of the gap, the Qn valve reduction flow 4 request signal returns to its original value as shown in FIG. 11(C), and the bypass valve opening request signal also returns to zero as shown in FIG. 11(e). Since the control valve servo and bypass valve servo have opening/closing speed change limits as shown in Figures 7 and 8, the control valve flow rate is
'gl1 As shown in figure (d), time t, later time t6
The bypass valve flow rate also returns to zero at time t7 as shown in FIG. 11(f). As described above, since there is a difference in response characteristics between the control valve flow rate and the bypass valve flow rate, the turbine inlet pressure temporarily decreases as shown in FIG. 11(g), and then recovers to its original state. This pressure change is 2 hours 1
It is propagated into the reactor pressure vessel with a γ deviation, and is attenuated within the reactor pressure vessel, resulting in a change as shown in Fig. 11).
原子炉圧力容器内の炉には蒸気泡が存在しており、この
圧力変化によって蒸気泡の体積が変化する。これによっ
て炉心反応度が変わり、中性子束が変化する。すなわち
、減圧過程では中性子束減少となり、増圧過程では中性
子束増加となる。負荷急減量およびその継続時間（ｔ３
ｔｌ）の大きさによっては、中性子束が第１１図（ｉ）
のようにスクラム設定哨（１２０％）以上となり、原子
炉プラントが停止に至る可能性がある。Steam bubbles exist in the reactor inside the reactor pressure vessel, and the volume of the steam bubbles changes as the pressure changes. This changes the core reactivity and changes the neutron flux. That is, the neutron flux decreases during the pressure reduction process, and the neutron flux increases during the pressure increase process. Sudden load reduction and its duration (t3
Depending on the size of tl), the neutron flux will be
If the scram setting exceeds (120%), the reactor plant may be shut down.
本発明は、上記のニラな検討結果に基づいてなされたも
のである。The present invention has been made based on the above-mentioned preliminary findings.
沸樟水形原子力発電プラントに適用した本発明の好適な
一実施例であるタービン制＃Ｊ装置を、第１図及び第２
図に基づいて説明する。A turbine #J device, which is a preferred embodiment of the present invention applied to a boiling camphor water nuclear power plant, is shown in Figures 1 and 2.
This will be explained based on the diagram.
原子炉圧力容器４内を循環する冷却水の一部は。A portion of the cooling water circulating inside the reactor pressure vessel 4.
可変周波数電源装置７により、駆動される再循環ポンプ
８によって再循環配管９を通ってジェットポンプ３の駆
動水となる。ジェットポンプ３の吸コみ口にて吸引した
冷却水と駆動水とが混合されて炉心１に送りこまれる。The water passes through the recirculation pipe 9 by the recirculation pump 8 driven by the variable frequency power supply 7 and becomes the driving water for the jet pump 3 . Cooling water and driving water sucked into the suction port of the jet pump 3 are mixed and sent into the reactor core 1.
炉心１では冷却水が燃料の核反応によって発生した熱を
吸収して沸騰し。In the reactor core 1, the cooling water absorbs the heat generated by the nuclear reaction of the fuel and boils.
ボイド責蒸気泡）を発生しつつ上昇する。気水分離器２
によって飽和水と蒸気ＶＣ分けられ、ｒｊ！和水は原子
炉圧力容器４内を降下してふたたび給水（図示せず）と
混合してジェットポンプ３より炉心１内に供給される。It rises while generating voids (steam bubbles). Steam water separator 2
Saturated water and steam VC are separated by rj! The Japanese water descends within the reactor pressure vessel 4, mixes with feed water (not shown) again, and is supplied into the reactor core 1 from the jet pump 3.
蒸気は原子炉圧力容器４から主蒸気管１０に吐出され、
蒸気加減弁１１を通ってタービン１２内に供給される。Steam is discharged from the reactor pressure vessel 4 to the main steam pipe 10,
The steam is supplied into the turbine 12 through the steam control valve 11 .
タービン１２から排気された蒸気は、復水器１４にで凝
縮された後に再び原子炉圧力容器４内に給水される。タ
ービン１２け、蒸気によって回転され１発電機１３を回
す。発電機１３にて発生した電気出力は、電力系統に送
電される。The steam exhausted from the turbine 12 is condensed in a condenser 14 and then fed into the reactor pressure vessel 4 again. Twelve turbines are rotated by steam and turn one generator 13. The electrical output generated by the generator 13 is transmitted to the power grid.
原子炉出力を制御する方法としては、制御棒駆動装置５
によって制御棒６を炉心１内に挿入し。As a method of controlling the reactor output, the control rod drive device 5
Insert the control rod 6 into the reactor core 1.
または炉心１から引抜く方法と、再循環ポンプ８の回転
数を変えて炉心１を流れる冷却水流量を増減する方法と
がある。的者は起動・停止のように大巾な出力変更を行
なう場合に用い、ｔｌｋ者は運転中の出力変更に用いる
。Alternatively, there is a method of withdrawing the cooling water from the core 1, and a method of increasing or decreasing the flow rate of cooling water flowing through the core 1 by changing the rotation speed of the recirculation pump 8. The tlk type is used when making large output changes such as starting and stopping, and the tlk type is used for changing the output while driving.
つぎにタービン蒸気流量であるが、蒸気加減弁１１は、
タービン入口の蒸気圧力（圧力計１６にて検出）を一定
に保つように、その開度を制御されている。圧力調整器
２０がこの制御を行なう。Next, regarding the turbine steam flow rate, the steam control valve 11 is
Its opening degree is controlled to keep the steam pressure (detected by pressure gauge 16) at the turbine inlet constant. A pressure regulator 20 performs this control.
たとえば、再循ｆｌＪａｔを制御して原子炉出力を増加
（減少）させ九結果、蒸気圧力が設定値よ抄も上がる（
下がる）と、蒸気加減弁１１の開度が開かれ（閉じられ
）、蒸気圧力を一定に保とうとする。この間にタービン
出力は、増加（減少）する、ことになる。蒸気圧力が更
に上昇して、蒸気加減弁′１１にて調節しきれない場合
には、バイパス弁１５を開いて蒸気を直接復水器１４に
排出し、蒸気圧の上昇を抑えるようにしている。For example, by controlling the recirculation flJat to increase (decrease) the reactor power, the steam pressure will rise above the set value (
(lowering), the opening degree of the steam control valve 11 is opened (closed) to try to keep the steam pressure constant. During this time, the turbine output will increase (decrease). If the steam pressure rises further and cannot be adjusted by the steam control valve '11, the bypass valve 15 is opened to discharge the steam directly to the condenser 14 to suppress the rise in steam pressure. .
以上のように蒸気加減弁１１は、プラントの通常運転時
には圧力調整器２０の出力信号によってその開度を制御
されているが、急激な負荷減少が生じて、タービン１２
０回転数が上昇すると回転速度計１７の出力を入力した
タービン速度制御器２３の出力信号が圧力ｆＡ整器２０
の出力信号に優先して蒸気加減弁１１の開度を減少させ
、タービンの過速を防止する。As described above, the opening degree of the steam control valve 11 is controlled by the output signal of the pressure regulator 20 during normal operation of the plant, but when a sudden load decrease occurs, the turbine 12
When the zero rotation speed increases, the output signal of the turbine speed controller 23 which inputs the output of the tachometer 17 changes to the pressure fA regulator 20.
The opening degree of the steam control valve 11 is reduced in priority to the output signal of , thereby preventing overspeed of the turbine.
このことを詳細に説明する。This will be explained in detail.
主蒸気管１０に取付けられた圧力検出器１６で検出され
たタービン入口の蒸気圧力信号は圧力設定器１８の設定
圧力信号と比較される。これらの圧力信号の偏差信号は
、圧力調整器２０に伝えられる。圧力調整器２０の出力
信号ＰＩけ、低値選択回路２１に伝えられる。低値選択
回路２１は。A steam pressure signal at the turbine inlet detected by a pressure detector 16 attached to the main steam pipe 10 is compared with a set pressure signal of a pressure setting device 18 . Deviation signals of these pressure signals are transmitted to the pressure regulator 20. The output signal PI of the pressure regulator 20 is transmitted to the low value selection circuit 21. The low value selection circuit 21 is.
、タービン速度制御器２３の出力信号Ｓ１ と前述の伊
号Ｐｓ とのうちで低値の信号を選択してその信号を信
号Ｃ１として出力する。信号Ｃ１は、関数発生器３２に
入力される。関数発生器３２は、蒸気加減弁の開度対流
量の非線形特性を補償するため、第３図に示すような関
数を内蔵している。関数発生器２４の出力信号が、加減
弁サーボ２４に入力される。加減弁サーボ２４け、この
入力信号に基づいて蒸気加減弁１１の開度を調節する。, the signal with the lowest value is selected between the output signal S1 of the turbine speed controller 23 and the above-mentioned number Ps, and outputs the selected signal as the signal C1. Signal C1 is input to function generator 32. The function generator 32 incorporates a function as shown in FIG. 3 in order to compensate for the nonlinear characteristic of the opening degree versus flow rate of the steam control valve. The output signal of the function generator 24 is input to the control valve servo 24. The control valve servo 24 adjusts the opening degree of the steam control valve 11 based on this input signal.
一方、プラントの通常運転時にタービン速度制御器２３
の出力信号Ｓ１が蒸気加減弁１１の開度を制御しないよ
うに、速度／負荷設定器２２によりタービン速度の設定
値が与えられている。すなわち、タービン１２及び発電
機１３が定格速度で回転しているときには１ タービン
速度制御器２３の出力信号Ｓ＋が負荷にして１１０慢の
値になるように、１０％高めに速度／負荷設定５２２Ｖ
Ｃで１０チ高めの設定値が与えられている。速度調定率
は、タービンの速度上昇５％が加減弁流１ｉ１００慢変
化に対応するように定められているので、喧洟のように
１０チ高めの負荷は、タービン速度に換算して０．５’
Ａに対応する。従って負荷設定１１０″％は、速度換算
で１００．５％となっている。従って。On the other hand, during normal operation of the plant, the turbine speed controller 23
A set value for the turbine speed is given by the speed/load setter 22 so that the output signal S1 does not control the opening degree of the steam control valve 11. That is, when the turbine 12 and the generator 13 are rotating at the rated speed, the speed/load setting is set 10% higher to 522V so that the output signal S+ of the turbine speed controller 23 becomes a load value of 110V.
A setting value of 10 inches higher is given for C. The speed regulation rate is determined so that a 5% increase in turbine speed corresponds to a 1i100 rapid change in the regulator valve flow, so a load that is 10 inches higher, such as the one in the case, will be converted to 0.5 in turbine speed. '
Corresponds to A. Therefore, the load setting of 110''% is equivalent to 100.5% in terms of speed.
プラントの通常運転時に）いて、信号５ｌＩ−ｉ圧力調
整器２０の出力信号Ｐ亀 よりも大きく、低値選択回路
２１を通過できない。このため、プラントの通常運転時
に蒸気加減弁１１の開度は、圧力調整器２０の出力信号
Ｐ、によって制御される。(during normal operation of the plant), the signal 5lI-i is larger than the output signal P of the pressure regulator 20, and cannot pass through the low value selection circuit 21. Therefore, the opening degree of the steam control valve 11 is controlled by the output signal P of the pressure regulator 20 during normal operation of the plant.
電力系統の負荷が部分的に喪失すると、タービン２３の
負荷が軽くなるため、一時的にタービン速度が上昇する
。タービン速度の上昇量が０．５％を越えると、回転速
変針１７の出力信号を入力するタービン速度制御器２３
の出力信号Ｓ１は、圧力調整器２０の出力信号Ｐ１ よ
りも小さくなり。When the load on the power system is partially lost, the load on the turbine 23 becomes lighter, causing a temporary increase in turbine speed. When the amount of increase in turbine speed exceeds 0.5%, the turbine speed controller 23 inputs the output signal of the rotation speed change direction 17.
The output signal S1 of the pressure regulator 20 becomes smaller than the output signal P1 of the pressure regulator 20.
信号Ｓ１が低値選択回路２１を通過して信号Ｃ１となる
。すなわち、蒸気加減弁１１は信号Ｓ１によって制御さ
れ、タービン速度上昇が制御される。The signal S1 passes through the low value selection circuit 21 and becomes the signal C1. That is, the steam control valve 11 is controlled by the signal S1, and the turbine speed increase is controlled.
前述のよつに操作される蒸気加減弁１１の開度が検出さ
れる。この開度は、飼えば、蒸気加減弁１１に設けられ
た弁***置検出器４１によって検出される。弁***置検
出器４１の出力信号は、第１０図に示す１関数を内蔵し
た関数発生器４２に入力される。加算器２６け、信号Ｐ
ｌｔ関数発生器４２の出力信号及びバイアス設定器２５
の出力信号を入力してバイパス弁開度要求信号を出力す
る。The opening degree of the steam control valve 11 operated as described above is detected. This opening degree is detected by the valve body position detector 41 provided in the steam control valve 11 once the pet is fed. The output signal of the valve body position detector 41 is input to a function generator 42 containing one function shown in FIG. 26 adders, signal P
Output signal of lt function generator 42 and bias setting device 25
inputs the output signal and outputs a bypass valve opening request signal.
バイパス弁サーボ２７は、バイパス弁開度要求信号を入
力してバイパス弁１５の開閉操作を行う。The bypass valve servo 27 receives the bypass valve opening request signal and opens and closes the bypass valve 15 .
バイパス弁サーボ２７の詳細構成は、第２図に示される
。バイパス弁サーボ２７の構成及び機能は。The detailed configuration of the bypass valve servo 27 is shown in FIG. The structure and function of the bypass valve servo 27 are as follows.
従来例と同じである。本実施例では、バイパス弁１’；
：＝ｌ：、弁***置検出器４１の出力信号により信号Ｐ
＋を補正して得られたバイパス弁開度要求信号に基づい
て操作される。This is the same as the conventional example. In this embodiment, the bypass valve 1';
:=l:, the signal P is generated by the output signal of the valve body position detector 41.
It is operated based on the bypass valve opening request signal obtained by correcting +.
本実施例における電力系統じよう乱時のプラント応答特
性を第４図に示す。第１１図に示す従来例と比較して異
なる部分け、第４図の（ｅ）〜（ｉ）の部分である。す
なわち、第４図（ｄ）に示す加減弁流凌の減少分が、バ
イパス弁開度要求信号となる。FIG. 4 shows the plant response characteristics during power system disturbances in this example. The parts that are different from the conventional example shown in FIG. 11 are parts (e) to (i) in FIG. 4. That is, the decrease in the control valve flow shown in FIG. 4(d) becomes the bypass valve opening request signal.
このバイパス弁開度要求信号の立ち上がり（時間ｔ２か
ら時間ｔ４の間）が緩やかなので、バイパス弁サーボ２
７内のバイパス弁急開機構は動作しない。さらにバイパ
ス弁１５の開閉速度は、バイパス弁サーボ２７の特性に
よって第８図に示すような変化速度制限があるので、バ
イパス弁１５を通過する流量（バイパス弁流量という）
は、第４図（ｆ）に示されるように第４図（ｅ）よりも
ピーク値が多少小さくなり１元の状態に戻る時間も多少
擾くなるように変化する。バイパス弁１５は０時間ｔ６
より多少遅れた時間ｔ７で全閉となる。この間における
タービン入口の蒸気圧力の変化（第４図値）参照）は、
従来の第１１図（ｇ）に比べてはるかに緩やかなものと
なる。従って１本実施例では。Since the rise of this bypass valve opening request signal (from time t2 to time t4) is gradual, the bypass valve servo 2
The bypass valve quick opening mechanism in 7 does not operate. Furthermore, the opening/closing speed of the bypass valve 15 has a speed limit as shown in FIG. 8 depending on the characteristics of the bypass valve servo 27, so the flow rate passing through the bypass valve 15 (referred to as bypass valve flow rate)
As shown in FIG. 4(f), the peak value changes to be somewhat smaller than that in FIG. 4(e), and the time to return to the original state changes somewhat. Bypass valve 15 is at 0 time t6
It becomes fully closed at time t7, which is slightly delayed. During this period, the change in steam pressure at the turbine inlet (see Figure 4 values) is as follows:
It is much gentler than the conventional figure 11(g). Therefore, in this embodiment.
多少の時間遅れをもって変化する原子炉圧力の変化（第
４図（ｈ）参照）も緩やかなものとなる。このため、中
性子束の変化も、第４図（ｉ）Ｋ示すようだ従来例に比
べてわずかなものとなり、中性子束高によるスクラム（
プラント停止）Ｋ至ることなく原子炉プラントの運転を
続行できる。The change in reactor pressure that changes with some time delay (see FIG. 4(h)) also becomes gradual. For this reason, the change in neutron flux is also slight compared to the conventional example as shown in Figure 4 (i) K, and the scram due to high neutron flux (
The nuclear reactor plant can continue operating without reaching K (plant shutdown).
なし、特開昭６０−５３８９５号公報の第４図には、無
負荷設定器を有するバイパス弁サーボの構成が示されて
いる。この例は、パワーロードアンバランスリレーが作
動しない程度の電力系統の負荷変動が生じた場合に、パ
ワーロードアンバランスリレーの不作動をもってバイパ
ス弁サーボのバイパス弁急開機構の機能を働らかせない
ようにしたものである。このようにある条件のもとてバ
イパス弁サーボのバイパス弁急開機構の動作を阻止する
機能を新たに付加することは、パワーロードアンバラン
スリレーが作動する二うな電力系統の大１冨な負荷変動
が生じた場合においてバイパス弁１５の急開失敗の故障
要因を増加させることにつながり、タービン制御装置の
信頼性を低くすることになる。本実施例では、特開昭６
０−５３８９５号公報の第４図のようなバイパス弁急開
機構の動作を阻止する機能を有していないので、パワー
ロードアンバランスリレーが作動した場合でもバイパス
弁１５を確実に急開させることができ、信頼性が著しく
高くなる。また、特開昭６０−５３８９５号公報の第４
図に示すバイパス弁サーボを用いた場合であっても、蒸
気加減弁の開閉速度とバイパス弁の開閉速度を可能な限
り一致させる二うＫそれらの弁の駆動機構を調整しなけ
ればならなかった。しかし１本実ｍ例では、蒸気加減弁
の弁***置信号を用いてバイパス弁１５を開閉制御を行
っているので、バイパス弁１５の開閉速度を蒸気加減弁
１１の開閉速度に一致させる必要はない。従って、蒸気
加減弁１１及びバイパス弁１５の駆動機構の製作、ｖ！
４整が極めて容易になる。None. Figure 4 of Japanese Patent Application Laid-Open No. 60-53895 shows the configuration of a bypass valve servo having a no-load setting device. In this example, when there is a load fluctuation in the power system to the extent that the power load unbalance relay is not activated, the function of the bypass valve quick opening mechanism of the bypass valve servo is not activated due to the inactivation of the power load unbalance relay. This is how it was done. Adding a new function that prevents the bypass valve servo from operating the bypass valve quick-opening mechanism under certain conditions is one of the major loads in the power system where the power load unbalance relay operates. When fluctuations occur, this increases the number of failure factors that may cause sudden opening failure of the bypass valve 15, reducing the reliability of the turbine control device. In this example,
Since it does not have a function to prevent the operation of the bypass valve quick opening mechanism as shown in Figure 4 of Publication No. 0-53895, the bypass valve 15 can be reliably opened suddenly even when the power load imbalance relay is activated. , and reliability is significantly increased. Also, No. 4 of Japanese Unexamined Patent Publication No. 60-53895
Even when using the bypass valve servo shown in the figure, it was necessary to adjust the drive mechanisms of these valves to match the opening and closing speeds of the steam control valve and the bypass valve as much as possible. . However, in the one example, since the opening and closing of the bypass valve 15 is controlled using the valve body position signal of the steam regulating valve, it is not necessary to make the opening and closing speed of the bypass valve 15 match the opening and closing speed of the steam regulating valve 11. do not have. Therefore, the production of the drive mechanism for the steam control valve 11 and the bypass valve 15, v!
4 adjustment becomes extremely easy.
本発明によれば、ｆｌｔｌ暴力にじよう乱が発生しても
、プラントのプロセス量の変動を最小に抑えることがで
き、プラント停止を回避することがたやすくなってプラ
ントの稼動率が向上する。さらに制御装置の信頼性が著
しく向上する。According to the present invention, even if a fltl violent storm occurs, fluctuations in the process amount of the plant can be minimized, making it easier to avoid plant stoppages and improving the operating rate of the plant. . Furthermore, the reliability of the control device is significantly improved.
第１図は本発明の好適な一実施例である原子炉プラント
のタービン制御装置の系統図、第２図は第１図のバイパ
ス弁サードの詳細系統図、第３図は第１図の関数発生器
４２内に内蔵されている関数の特性図、第４図（ａ）〜
（ｉ）は第１図に示す本発明の実施例における制御特性
を示す説明図、有５図はバイパス弁開度要求信号とバイ
パス弁流量との関係を示す特性図、第６図はバイパス弁
開度特性を示す説明図、第７図は蒸気加減弁の開度及び
蒸気流量の変化を示す特性図、第８図はプラントの通常
運転時におけるバイパス弁開度及び蒸気流量の変化を示
す特性図、第９図はバイパス弁急開時におけるバイパス
弁開度及び蒸気流量の変化を示す特性図、＠１０図は第
２図の関数発生器４０に内蔵されている関数の特性図、
第１１図（ａ）〜（ｉ）は従来例の制御特性を示す説明
図である。
４・・・原子炉圧力容器、１１・・・蒸気加減弁、１２
・・・タービン、１５・・バイパス弁、１６・・・圧力
計。
値選択回路、２３・・タービン速度制御器、２７・・・
バイパス弁サーボ、４０・・・弁***置検出器、４１・
・・関数発生器。FIG. 1 is a system diagram of a turbine control device for a nuclear reactor plant that is a preferred embodiment of the present invention, FIG. 2 is a detailed system diagram of the bypass valve third shown in FIG. 1, and FIG. Characteristic diagrams of functions built in the generator 42, FIG. 4(a)-
(i) is an explanatory diagram showing the control characteristics in the embodiment of the present invention shown in FIG. 1, FIG. 5 is a characteristic diagram showing the relationship between the bypass valve opening request signal and the bypass valve flow rate, and FIG. An explanatory diagram showing the opening degree characteristics, Figure 7 is a characteristic diagram showing changes in the opening degree of the steam control valve and steam flow rate, and Figure 8 is a characteristic diagram showing changes in the bypass valve opening degree and steam flow rate during normal operation of the plant. Figure 9 is a characteristic diagram showing changes in the bypass valve opening degree and steam flow rate when the bypass valve is suddenly opened; Figure @10 is a characteristic diagram of the function built in the function generator 40 of Figure 2;
FIGS. 11(a) to 11(i) are explanatory diagrams showing control characteristics of a conventional example. 4... Reactor pressure vessel, 11... Steam control valve, 12
... Turbine, 15... Bypass valve, 16... Pressure gauge. Value selection circuit, 23...Turbine speed controller, 27...
Bypass valve servo, 40... Valve body position detector, 41.
...Function generator.
Claims (1)
た蒸気が供給されるタービンと、前記原子炉と前記ター
ビンとを連絡する主蒸気管と、前記タービンから排気さ
れた蒸気を凝縮する復水器と、前記主蒸気管に設置され
た蒸気加減弁と、前記蒸気加減弁より上流側で前記主蒸
気管に接続され、しかも他端が前記復水器に接続される
バイパス管と、前記バイパス管に設置されたバイパス弁
とを有する原子炉プラントのタービン制御装置において
、前記原子炉で発生した蒸気の圧力を検出する手段と、
前記タービンの回転数を検出する手段と、前記圧力検出
手段の出力信号を入力する圧力調整器と、前記回転数検
出手段の出力信号を入力するタービン速度制御器と、前
記圧力調整器及び前記タービン速度制御器の出力信号の
うち低いレベルの出力信号を選択して出力する低値選択
回路と、前記低値選択回路の出力信号に基づいて前記蒸
気加減弁の開度を制御する第１制御手段と、前記蒸気加
減弁の開度を検出する手段と、前記圧力調整器及び前記
開度検出手段の出力信号に基づいて前記バイパス弁の開
度を制御する第２制御手段とを備えたことを特徴とする
原子炉プラントのタービン制御装置。1. A nuclear reactor that generates steam, a turbine to which steam discharged from the nuclear reactor is supplied, a main steam pipe that connects the nuclear reactor and the turbine, and a main steam pipe that condenses the steam exhausted from the turbine. a condenser, a steam control valve installed in the main steam pipe, and a bypass pipe connected to the main steam pipe upstream of the steam control valve and whose other end is connected to the condenser; In a turbine control device for a nuclear reactor plant having a bypass valve installed in the bypass pipe, means for detecting the pressure of steam generated in the nuclear reactor;
means for detecting the rotation speed of the turbine; a pressure regulator for inputting an output signal of the pressure detection means; a turbine speed controller for inputting an output signal of the rotation speed detection means; the pressure regulator and the turbine. a low value selection circuit that selects and outputs a low level output signal from among the output signals of the speed controller; and a first control means that controls the opening degree of the steam control valve based on the output signal of the low value selection circuit. and a second control means for controlling the opening degree of the bypass valve based on the output signals of the pressure regulator and the opening detection means. Features of a turbine control device for a nuclear reactor plant.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60171064A JPH0631813B2 (en) | 1985-08-05 | 1985-08-05 | Turbine controller for nuclear reactor plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60171064A JPH0631813B2 (en) | 1985-08-05 | 1985-08-05 | Turbine controller for nuclear reactor plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6232393A true JPS6232393A (en) | 1987-02-12 |
| JPH0631813B2 JPH0631813B2 (en) | 1994-04-27 |
Family
ID=15916381
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60171064A Expired - Lifetime JPH0631813B2 (en) | 1985-08-05 | 1985-08-05 | Turbine controller for nuclear reactor plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0631813B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63285205A (en) * | 1987-05-15 | 1988-11-22 | Hitachi Ltd | Load setting device for turbine control device |
| EP0594384A1 (en) * | 1992-10-19 | 1994-04-27 | General Electric Company | System and method for controlling a nuclear reactor upon steam flow control valve failure |
| CN103000241A (en) * | 2012-12-03 | 2013-03-27 | 中广核工程有限公司 | System and method for loading and unloading turbine device for nuclear power station emergency diesel engine |
| CN104018894A (en) * | 2014-05-28 | 2014-09-03 | 中广核核电运营有限公司 | Checking processing method of steam turbine electric hydraulic control system pulse impact |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6198904A (en) * | 1984-10-19 | 1986-05-17 | Toshiba Corp | Control device for nuclear power plant |
-
1985
- 1985-08-05 JP JP60171064A patent/JPH0631813B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6198904A (en) * | 1984-10-19 | 1986-05-17 | Toshiba Corp | Control device for nuclear power plant |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63285205A (en) * | 1987-05-15 | 1988-11-22 | Hitachi Ltd | Load setting device for turbine control device |
| EP0594384A1 (en) * | 1992-10-19 | 1994-04-27 | General Electric Company | System and method for controlling a nuclear reactor upon steam flow control valve failure |
| CN103000241A (en) * | 2012-12-03 | 2013-03-27 | 中广核工程有限公司 | System and method for loading and unloading turbine device for nuclear power station emergency diesel engine |
| CN104018894A (en) * | 2014-05-28 | 2014-09-03 | 中广核核电运营有限公司 | Checking processing method of steam turbine electric hydraulic control system pulse impact |
| CN104018894B (en) * | 2014-05-28 | 2016-02-03 | 中广核核电运营有限公司 | The check processing method of electrohydraulic steam turbine controlling system pulsatile impact |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0631813B2 (en) | 1994-04-27 |
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