JPH0144905B2 - - Google Patents
Info
- Publication number
- JPH0144905B2 JPH0144905B2 JP59271611A JP27161184A JPH0144905B2 JP H0144905 B2 JPH0144905 B2 JP H0144905B2 JP 59271611 A JP59271611 A JP 59271611A JP 27161184 A JP27161184 A JP 27161184A JP H0144905 B2 JPH0144905 B2 JP H0144905B2
- Authority
- JP
- Japan
- Prior art keywords
- pump
- rotational speed
- motor
- speed
- guide vane
- 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.)
- Expired
Links
- 238000000034 method Methods 0.000 claims description 15
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 10
- 230000000694 effects Effects 0.000 description 5
- 230000010349 pulsation Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 238000013459 approach Methods 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B15/00—Controlling
- F03B15/02—Controlling by varying liquid flow
- F03B15/04—Controlling by varying liquid flow of turbines
-
- 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
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Water Turbines (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、可変速のポンプ水車もしくはポンプ
の運転停止方法に係り、特に解列時の入力の減少
方法を改良した可変速のポンプ水車またはポンプ
の停止方法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 method for stopping the operation of a variable-speed pump-turbine or a pump, and in particular to a variable-speed pump-turbine or a pump that has an improved method for reducing input when disconnecting from the train. This relates to a method of stopping the system.
〔発明の背景〕
従来この種の装置に関しては、特開昭56−
126675号公報に記載のように、回転速度を調節し
水力発電装置の効率向上を図ることは示されてい
るが、揚水運転停止時に、電力系統に与える衝撃
を緩和することについての記載は見当らない。[Background of the Invention] Conventionally, regarding this type of device,
As stated in Publication No. 126675, it is shown that the efficiency of hydroelectric power generation equipment can be improved by adjusting the rotation speed, but there is no mention of mitigating the impact on the power system when pumping operation is stopped. .
一般に、ポンプ水車のポンプ特性もしくはポン
プの特性は、ある揚程にて運転された場合に、横
軸にランナーの回転速度をとり縦軸にポンプ入力
及びガイドベーンの開口度をとつて示した揚程一
定の場合を示す本発明の実施例の第１図に示すよ
うな傾向を有している。第１図はポンプ入力の変
化が、回転数によつて変化する様子をガイドベー
ン開口度をパラメータとして示したものであり、
N0−ΔN〜N0＋ΔNは可変速機回転速度範囲であ
る。従来のポンプ水車もしくはポンプでは、回転
速度は定速機の定格回転速度N0であり、電力系
統に電動機が並列されている状態では変化しない
ので、図中の中線L0上だけが従来の定速機ポン
プの運転領域である。 In general, the pump characteristics of a pump-turbine or the characteristics of the pump are determined by the fact that when operated at a certain head, the head is constant, with the horizontal axis representing the rotational speed of the runner and the vertical axis representing the pump input and the opening degree of the guide vane. It has a tendency as shown in FIG. 1 of the embodiment of the present invention, which shows the case of . Figure 1 shows how the pump input changes with the rotation speed using the guide vane opening degree as a parameter.
N 0 −ΔN to N 0 +ΔN is the variable speed machine rotation speed range. In a conventional pump-turbine or pump, the rotational speed is the rated rotational speed N 0 of the constant-speed machine, and it does not change when electric motors are connected in parallel in the power system, so only the center line L 0 in the diagram is the rotation speed of the conventional pump. This is the operating range of a constant speed pump.
通常のポンプ運転状態は第１図のＡ点に相当
し、ランナー外周に配設されたガイドベーンの開
口度はポンプ揚水量を最も効率をよくする状態の
最適開口度GVO0にある。ここで、ポンプ運転停
止指令を受けるとガイドベーン開口度を小さく絞
つてゆき、揚水量とポンプ入口とを減少させた後
で電動機を電力系統から解列することが一般に行
なわれている。しかし、確かにガイドベーン開口
度を小さく絞るとポンプ入力は減少するものの、
その減少の限界は定格入力の数十％に相当する締
切運転時の入力にあり、これ以上解列時の入力を
減じるのは困難である。即ち、定速機で締切運転
に入つた後はランナーは水中で回転するのみであ
るからである。第４図は横軸にガイドベーン開口
度をとり縦軸にポンプ入力をとつて揚程一定、回
転速度一定の場合の通常のポンプ入力曲線であ
り、ガイドベーンの開口度を絞ることによつてど
の程度にポンプ入力が減少するかを示す一例であ
る。第４図から明からなように、ガイドベーン開
口度を適正開口度より減少しても、かなり絞り込
まぬと減少しないことが判る。 The normal pump operating state corresponds to point A in Fig. 1, and the opening degree of the guide vanes disposed around the runner's outer circumference is at the optimum opening degree GVO 0 , which makes the amount of pumped water most efficient. Here, when a pump operation stop command is received, the guide vane opening degree is narrowed down to reduce the amount of pumped water and the pump inlet, and then the electric motor is disconnected from the power system. However, although it is true that reducing the guide vane opening reduces the pump input,
The limit to this reduction lies in the input during shut-off operation, which corresponds to several tens of percent of the rated input, and it is difficult to reduce the input during disconnection any further. That is, after the constant speed machine starts the shut-off operation, the runner only rotates in the water. Figure 4 shows a normal pump input curve when the horizontal axis is the guide vane opening and the vertical axis is the pump input, and the head is constant and the rotation speed is constant. This is an example showing how much the pump input is reduced. As is clear from FIG. 4, even if the guide vane opening is reduced below the appropriate opening, it will not be reduced unless the guide vane is narrowed down considerably.
解列時のポンプ入力を減らすことは、遮断器の
負荷を軽減し寿命を長くする効果をもたらし、か
つ、電力系統に及ぼす解列時の衝撃を小さくする
ために、特に大容量のポンプ水車あるいはポンプ
の場合、極力ポンプ入力を減らすように望まれて
いる。一方、解列時の入力を減じるためにガイド
ベーン開口度を極端に絞りすぎると、ポンプ水車
あるいはポンプの運転状態が悪化する。最適ガイ
ドベーン開口度GVO0でのポンプ内部の流れ状態
はきわめて良好であり水圧脈動の大きさの程度も
小さいのに比べ、最適ガイドベーン開口度GVO0
から離れて第４図に示す締切運転（開口度全閉）
状態に近づくとポンプ内部の流れは著しく悪くな
り水圧脈動が増大し機器の振動騒音も大きくな
る。水圧脈動の増大はポンプ水車あるいはポンプ
本体各部の応力振幅増大をきたし、機器の疲労強
度上好ましくないものである。 Reducing the pump input during disconnection has the effect of reducing the load on the circuit breaker and extending its life, and also reduces the impact of disconnection on the power system, especially for large-capacity pump-turbine or In the case of pumps, it is desired to reduce pump input as much as possible. On the other hand, if the opening degree of the guide vane is excessively narrowed in order to reduce the input at the time of decoupling, the operating condition of the pump-turbine or the pump will deteriorate. At the optimum guide vane opening GVO 0 , the flow condition inside the pump is very good and the magnitude of water pressure pulsation is small.
Closed operation (opening degree fully closed) shown in Figure 4 away from
When this condition approaches, the flow inside the pump becomes significantly worse, the water pressure pulsation increases, and the vibration and noise of the equipment increases. An increase in water pressure pulsation causes an increase in stress amplitude in the pump waterwheel or in various parts of the pump body, which is unfavorable in terms of the fatigue strength of the equipment.
そのため、電動機を電力系統より解列するとき
のガイドベーン開口度は、解列時のポンプ入力が
極力小さいこと、解列時の機器の振動騒音及び応
力振幅が許容される最大であること、の２つの条
件によつて決定されるのが一般的である。第１
図、第４図のＢ点が解列時の運転点に相当し、こ
の場合、機器の振動騒音、強度的制限から締切運
転状態になるかなり手前で、入力が定格ポンプ入
力の約1/2にも相当するポンプ入力にて解列して
いる。電力系統が弱く、ポンプ水車に単機容量が
大きい場合には特に有害な衝撃を電力系統に与え
ることになる。 Therefore, the opening degree of the guide vane when disconnecting the motor from the power grid must be determined so that the pump input at the time of disconnection is as small as possible, and that the vibration noise and stress amplitude of the equipment at the time of disconnection are at the maximum allowable. It is generally determined by two conditions. 1st
Point B in Fig. 4 corresponds to the operating point at the time of disconnection, and in this case, the input is approximately 1/2 of the rated pump input, well before the shut-off operation is reached due to equipment vibration noise and strength limitations. The series is disconnected at the pump input corresponding to the same. If the power system is weak and the pump-turbine has a large single unit capacity, this can cause a particularly harmful shock to the power system.
第２図に横軸にポンプ水車またはポンプの運転
停止時の時間をとり、縦軸にガイドベーン開口度
GVO、回転速度Ｎ、ポンプ入力Ｐをとつて示し
た本発明の実施例であり、従来の場合を破線Ｅに
て示す。ポンプ運転停止命令（停止操作開始）時
点Tsにてポンプ運転停止指令を受けた後、ガイ
ドベーン開口度GVOを徐々に絞り始め、予め設
定したガイドベーン解列開口度GVOdに達した解
列時点Tdにて電動機が系統より解列される。定
速機であるため、解列前までは破線Ｅの如く定格
回転速度Ｎ。で回転しており、この間のポンプ入
力はガイドベーン開口度GVOを絞ることによつ
て破線Ｅの如く減少されている。従つて、第４図
に示すポンプ入力特性から判るようにガイドベー
ン開口度の絞り始めでは入力が余り変化しないの
で、かなり絞り込まぬとポンプ入力は減少しない
し、また、余り絞りすぎても機器の振動騒音は大
きくなる。即ち、定速機のポンプ水車もしくはポ
ンプの運転停止時には解列前のポンプ入力が大き
いため電力系統に悪影響を及ぼし、また、振動騒
音も大きいため機器の強度的環境は悪くならざる
を得なくなつていた。上記説明では、可動ガイド
ベーンを有するポンプもしくはポンプ水車を対象
に従来のポンプ運転停止について述べたが、可動
ガイドベーンの代りに吐出弁を有するポンプある
いはポンプ水車についても同様である。 In Figure 2, the horizontal axis shows the time when the pump turbine or pump stops operating, and the vertical axis shows the guide vane opening degree.
This is an embodiment of the present invention showing GVO, rotational speed N, and pump input P, and the conventional case is shown by a broken line E. After receiving the pump operation stop command at the pump operation stop command (stop operation start) time Ts, the guide vane opening degree GVO is gradually reduced, and the guide vane opening degree GVO reaches the preset guide vane alignment opening degree GVO d . The motor is disconnected from the grid at Td. Since it is a constant speed machine, the rated rotational speed is N as shown by the broken line E until it is disassembled. During this period, the pump input is reduced as shown by the broken line E by narrowing the guide vane opening degree GVO. Therefore, as can be seen from the pump input characteristics shown in Figure 4, the input does not change much when the guide vane opening begins to be narrowed down, so the pump input will not decrease unless the guide vane opening is narrowed considerably, and even if it is too narrow, the equipment Vibration noise becomes louder. In other words, when a fixed-speed pump turbine or pump is stopped, the pump input before disconnection is large, which has a negative impact on the power system, and the vibration and noise are also large, which inevitably worsens the equipment environment. was. In the above description, conventional pump operation stoppage has been described for a pump or pump-turbine having a movable guide vane, but the same applies to a pump or pump-turbine having a discharge valve instead of a movable guide vane.
本発明は上記の状況に鑑みなされたものであ
り、ポンプ運転停止の解列の際の電力系統からの
入力を小さくできる可変速のポンプ水車またはポ
ンプの停止方法を提供することを目的としたもで
ある。
The present invention was made in view of the above situation, and an object of the present invention is to provide a variable speed pump-turbine or a method for stopping a pump, which can reduce the input from the electric power system when disconnecting the pump to stop operation. It is.
本発明可変速ポンプ水車またはポンプの停止方
法は、吐出弁もしくはランナー外周に配設される
ガイドベーンと、電力系統に並列に接続される可
変速電動機もしくは可変速発電電動機とを設けた
ポンプ水車またはポンプを停止する場合に、上記
電力系統から上記電動機もしくは上記発電電動機
を解列する前に、該電動機もしくは該発電電動機
の回転速度を減じると共に上記ガイドベーンある
いは上記吐出弁の開口度を減じ、定格回転速度駆
動時に比較しポンプ入力を減少させる方法であ
る。電動機の回転数を減じると共にガイドベーン
または吐出弁の開口度を減少させてポンプ入力を
少なくすることにより遮断器負荷及び電力系統に
与える衝撃の影響を少なくできるようにしたもの
である。
The method for stopping a variable-speed pump-turbine or pump of the present invention is a pump-turbine or When stopping the pump, before disconnecting the electric motor or generator motor from the power system, reduce the rotational speed of the electric motor or generator motor, and reduce the opening degree of the guide vane or discharge valve so that the rated This method reduces pump input compared to when driving at rotational speed. By reducing the rotation speed of the motor and the opening degree of the guide vane or discharge valve to reduce the pump input, it is possible to reduce the impact of impact on the circuit breaker load and the power system.
以下本発明の可変速のポンプ水車またはポンプ
の停止方法を実施例を用い第１図、第２図により
説明する。第１図において本実施例のポンプ定常
運転から解列に至る過程を太い実線Ｃ―Ｄに示
し、斜線範囲は可変速運転範囲を示す。本実施例
は回転速度の可変なポンプ水車もしくはポンプを
対称としたものであるため、定常運転状態での回
転速度は必ずしも定格回路速度N0にあるわけで
はない。このため、例えば適正（最適）ガイドベ
ーン開度GVO0で、しかも定格回転速度N0より大
き目の回転速度Ｃ点にて定常ポンプ運転をしてい
たものが、ポンプ入力運転停止命令を受けた場
合、太い実線Ｃ―Ｄの如く経過する。従つて、ポ
ンプ運転停止命令を受けた後、ガイドベーン開口
度を徐徐に絞り込むと共に回転数を調整する手段
の速度制御装置を介し回転速度を徐々に低下させ
てゆく。回転速度が可変速度範囲最低回転速度で
電動機個有の最低回転速度以上の速度（N0―
ΔN）で、かつ、ガイドベーン開口度が解列開口
度GVOdとなつた点Ｄにて電動機を電力系統から
解列する。
DESCRIPTION OF THE PREFERRED EMBODIMENTS The variable speed pump turbine or the method for stopping a pump according to the present invention will be explained below using an embodiment with reference to FIGS. 1 and 2. In FIG. 1, the process from steady pump operation to disconnection of the pump in this embodiment is shown by a thick solid line CD, and the diagonally shaded range shows the variable speed operation range. Since this embodiment deals with a pump water turbine or a pump whose rotational speed is variable, the rotational speed in a steady operating state is not necessarily at the rated circuit speed N 0 . For this reason, for example, if a pump is being operated steadily at a rotational speed C point with an appropriate (optimum) guide vane opening GVO 0 and a rotational speed C that is larger than the rated rotational speed N 0 , and receives a pump input operation stop command. , progresses as shown by the thick solid line CD. Therefore, after receiving a command to stop the pump operation, the guide vane opening degree is gradually narrowed down and the rotational speed is gradually lowered via the speed control device of the means for adjusting the rotational speed. The rotation speed is the lowest rotation speed in the variable speed range and is higher than the minimum rotation speed unique to the electric motor (N 0 -
ΔN), and the motor is disconnected from the power system at point D where the guide vane opening becomes the disconnection opening GVO d .
このようにすることにより、解列時点でのポン
プ入力が、定速機の場合解列入力Pd１であつた
ことに比較し同じガイドベーン解列開口度GVOd
でありながら解列時には解列入力Pd２まで減少
できる。一方、解列時点近くでのポンプ水車の振
動騒音と強度的厳しさは可変速範囲の最低回転速
度（N0―ΔN）に近くなつているため緩和される
ことがわかる。即ち、ガイドベーン最適開口度
GVO0よりはるかに小さく、ほとんど締切運転状
態に近い運転状態において、ポンプ水車ランナ―
室内の水圧脈動、ひいてはポンプ水車各部品の応
力振幅は回転速度の小さい方が回転速度の大きい
場合に比べて小さくなるからである。 By doing this, the pump input at the time of unalignment is the same guide vane unaligned opening degree GVO d as compared to the unaligned input Pd1 in the case of a constant speed machine.
However, at the time of decoupling, the decoupling input can be reduced to Pd2. On the other hand, it can be seen that the vibration noise and severity of the pump-turbine near the point of decoupling are alleviated because it is close to the lowest rotational speed (N 0 - ΔN) in the variable speed range. In other words, the optimum opening degree of the guide vane
GVO is much lower than 0 and the pump-turbine runner is
This is because the water pressure pulsations in the room and, by extension, the stress amplitude in each part of the pump-turbine are smaller when the rotation speed is low than when the rotation speed is high.
このように本実施例の可変速のポンプ水車また
はポンプの停止方法は、電力系統から電動機を解
列する前に該電動機の回転速度を減じると共にガ
イドベーンの開度を減じるようにしたので解列時
のポンプ入力を小さくできるため、遮断器負器及
び電力系統へ与える衝撃を減じることができると
共に、例えば疲労強度上などの機器の強度的環境
を緩和できる。数値的には、ポンプ特性に基づい
た概算によれば、回転速度を定格回転速度の90％
に減じただけで解列時の入力を約60％に減じるこ
とができる。また、解列時点付近の水圧脈動振幅
は約80％に減じることができる。上記実施例はガ
イドベーン開口度を絞つた場合について述べたが
吐出弁の開口度を絞つた場合も全く同様の効果を
有する。 In this way, the variable speed pump-turbine or pump stopping method of this embodiment reduces the rotational speed of the motor and reduces the opening degree of the guide vane before disconnecting the motor from the power system. Since the pump input during operation can be reduced, the impact on the circuit breaker and the power system can be reduced, and the strength environment of the equipment, such as fatigue strength, can be alleviated. Numerically, according to a rough estimate based on pump characteristics, the rotation speed should be 90% of the rated rotation speed.
By simply reducing the number of inputs to 60%, the input required for uncoupling can be reduced to approximately 60%. In addition, the amplitude of water pressure pulsations near the time of train disconnection can be reduced to about 80%. In the above embodiment, the case where the opening degree of the guide vane is narrowed has been described, but the same effect can be obtained even when the opening degree of the discharge valve is narrowed down.
第３図は他の実施例を示し、上記実施例は、回
転速度の変化を、ポンプ運転停止指令を受けた直
後から行ない、丁度解列する解列入力Pd２にて
可変速範囲の最低値となるように制御している。
しかし、本発明の目的を達成するためには必ずし
も上記のようにのみ制御することを必要とするも
のではない。また、停止指令前の定常運転時の回
転速度が必ずしも定格回転速度N0にあるとは限
らず、可変速回転範囲の（N0＋ΔN）にて運転し
ていることもあり得る。第３図では解列時間Td
までに必ず可変速最低回転速度（N0−ΔN）に達
するような回転速度変化勾配にて制御している。
従つて、本実施例によれば可変速範囲内のどの回
転速度で運転していても解列時には速度制御装置
のポンプ入力の最低回転速度（N0−ΔN）の可能
最小回転速度とすることにより、解列時のポンプ
入力を確実に減じることができる。本実施例も上
記実施例と同様の作用効果を有する。 FIG. 3 shows another embodiment, and in the above embodiment, the rotational speed is changed immediately after receiving the pump operation stop command, and the rotation speed is changed to the lowest value of the variable speed range at the queue disassembly input Pd2 just when the pump operation is discontinued. It is controlled so that
However, in order to achieve the object of the present invention, it is not necessarily necessary to control only as described above. Furthermore, the rotational speed during steady operation before the stop command is not necessarily at the rated rotational speed N 0 , but may be operating at (N 0 +ΔN) in the variable speed rotation range. In Figure 3, the uncoupling time Td
The rotational speed change gradient is controlled so that the variable speed minimum rotational speed (N 0 −ΔN) is always reached by the time of the rotation.
Therefore, according to this embodiment, no matter what rotational speed within the variable speed range the pump is operating at, when the pump is disconnected, the rotational speed is set to the minimum possible rotational speed (N 0 −ΔN) of the pump input to the speed control device. This makes it possible to reliably reduce the pump input when disconnecting. This example also has the same effects as the above example.
以上記述した如く本発明の可変速のポンプ水車
またはポンプの停止方法は、解列時のポンプ入力
を小さくできるので、遮断器負荷及び電力系統へ
の衝撃を減じることができる効果を有するもので
ある。
As described above, the variable speed pump-turbine or pump stopping method of the present invention can reduce the pump input when the train is disconnected, so it has the effect of reducing the impact on the circuit breaker load and the power system. .
第１図は本発明の可変速のポンプ水車またはポ
ンプの停止方法を実施時の回転速度及びポンプ入
力の関係説明図、第２図、第３図はそれぞれ第１
図の停止方法を実施時のポンプ停止操作開始から
解列までの時間に対するガイドベーン開口度、回
転速度及びポンプ入力の開係説明図、第４図は通
常運転時のガイドベーン開口度とポンプ入力との
関係説明図である。
GVO0……最適開口度、GVOd……解列開口度、
N0……定格回転速度、N0―ΔN……可変速最低
回転速度、Pd２……解列入力、Td……解列時
点、Ts……停止操作開始時点。
FIG. 1 is an explanatory diagram of the relationship between rotational speed and pump input when implementing the variable speed pump-turbine or pump stopping method of the present invention, and FIGS.
Figure 4 is an explanatory diagram of the guide vane opening, rotation speed, and pump input relative to the time from the start of the pump stop operation to disassembly when the stopping method shown in the figure is implemented. Figure 4 shows the guide vane opening and pump input during normal operation. FIG. GVO 0 ...Optimum opening degree, GVO d ...Disconnected opening degree,
N 0 ... Rated rotational speed, N 0 - ΔN... Variable speed minimum rotational speed, Pd2... Queue disconnection input, Td... Time of disconnection, Ts... Point of start of stop operation.
Claims (1)
イドベーンと、電力系統に並列に接続される可変
速電動機もしくは可変速発電電動機とを設けたポ
ンプ水車またはポンプを停止させる方法におい
て、上記電力系統から上記電動機もしくは上記発
電電動機を解列する前に、該電動機もしくは該発
電電動機の回転速度を減じると共に上記ガイドベ
ーンあるいは上記吐出弁の開口度を減じ、定格回
転速度駆動時に比較しポンプ入力を減少させるこ
とを特徴とする可変速のポンプ水車またはポンプ
の停止方法。 ２ 上記電力系統から上記電動機もしくは上記発
電電動機を解列する時点の該電動機もしくは該発
電電動機の回転速度を、少なくとも該電動機もし
くは該発電電動機個有の最低回転速度で、かつ、
速度制御装置の制御可能最低回転速度とする特許
請求の範囲第１項記載の可変速のポンプ水車また
はポンプの停止方法。[Claims] 1. A method for stopping a pump water turbine or a pump provided with a discharge valve or a guide vane disposed on the outer periphery of a runner, and a variable speed electric motor or variable speed generator motor connected in parallel to an electric power system. , before disconnecting the electric motor or the generator motor from the electric power system, reduce the rotational speed of the electric motor or the generator motor, reduce the opening degree of the guide vane or the discharge valve, and compare it when operating at the rated rotational speed. A method for stopping a variable speed pump turbine or pump, characterized by reducing the pump input. 2. The rotational speed of the electric motor or the generator-motor at the time when the electric motor or the generator-motor is disconnected from the power system is at least the lowest rotational speed unique to the electric motor or the generator-motor, and
A method for stopping a variable speed pump-turbine or a pump according to claim 1, wherein the speed control device sets the controllable minimum rotational speed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59271611A JPS61149582A (en) | 1984-12-21 | 1984-12-21 | Stopping method for variable speed reversible pump-turbine or pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59271611A JPS61149582A (en) | 1984-12-21 | 1984-12-21 | Stopping method for variable speed reversible pump-turbine or pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61149582A JPS61149582A (en) | 1986-07-08 |
| JPH0144905B2 true JPH0144905B2 (en) | 1989-10-02 |
Family
ID=17502479
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59271611A Granted JPS61149582A (en) | 1984-12-21 | 1984-12-21 | Stopping method for variable speed reversible pump-turbine or pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61149582A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0768936B2 (en) * | 1986-11-12 | 1995-07-26 | 株式会社東芝 | How to stop pumping operation of variable speed pump |
| JPH0768937B2 (en) * | 1986-12-24 | 1995-07-26 | 株式会社東芝 | How to stop pumping operation of variable speed pump turbine |
| JPS63239376A (en) * | 1987-03-27 | 1988-10-05 | Toshiba Corp | Method of stopping variable speed pump or pump turbine |
| JP2614242B2 (en) * | 1987-10-23 | 1997-05-28 | 東京電力株式会社 | Pumping operation stop control method of AC excitation synchronous machine |
-
1984
- 1984-12-21 JP JP59271611A patent/JPS61149582A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61149582A (en) | 1986-07-08 |
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| EXPY | Cancellation because of completion of term |