JPS6236246B2 - - Google Patents
Info
- Publication number
- JPS6236246B2 JPS6236246B2 JP55026658A JP2665880A JPS6236246B2 JP S6236246 B2 JPS6236246 B2 JP S6236246B2 JP 55026658 A JP55026658 A JP 55026658A JP 2665880 A JP2665880 A JP 2665880A JP S6236246 B2 JPS6236246 B2 JP S6236246B2
- Authority
- JP
- Japan
- Prior art keywords
- speed
- rotation speed
- vibration
- calculate
- vibration amplitude
- 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 21
- 230000001133 acceleration Effects 0.000 claims description 3
- 238000012544 monitoring process Methods 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 6
- 229910000897 Babbitt (metal) Inorganic materials 0.000 description 5
- 230000005856 abnormality Effects 0.000 description 5
- 230000002159 abnormal effect Effects 0.000 description 4
- 238000009499 grossing Methods 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000012937 correction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000011017 operating method Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D13/00—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover
- G05D13/62—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover characterised by the use of electric means, e.g. use of a tachometric dynamo, use of a transducer converting an electric value into a displacement
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Control Of Turbines (AREA)
- Motor And Converter Starters (AREA)
- Control Of Velocity Or Acceleration (AREA)
Description
【発明の詳細な説明】
本発明は振動監視機能を有する回転機の速度制
御に係り、特に危険速度領域における軸振動の予
測に基づく回転機の昇速制御方法に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to speed control of a rotating machine having a vibration monitoring function, and more particularly to a speed increase control method for a rotating machine based on prediction of shaft vibration in a critical speed range.
回転機、特に蒸気タービンの昇速制御は、あら
かじめ定められた回転数上昇勾配にしたがつて昇
速、暖機を行ないつゝ目標回転速度に到達せしめ
る運転方法が採用されている。実際には起動スケ
ジユールにしたがつて主蒸気弁あるいはバイパス
弁等を操作して昇速させるが、この過程における
異常発生の対応処置は最も重要な課題のひとつで
ある。なかでも異常振動発生時は、その適切なる
処置とタイミングを失しないようにしないと、高
速回転体では重大な事故をひきおこすことにな
る。 The speed increase control of a rotating machine, particularly a steam turbine, employs an operating method in which the speed is increased and warmed up according to a predetermined rotation speed increase gradient to reach a target rotation speed. In reality, the main steam valve or bypass valve is operated to increase the speed according to the startup schedule, but one of the most important issues is how to deal with the occurrence of abnormalities during this process. In particular, when abnormal vibrations occur, if appropriate measures and timing are not taken, serious accidents can occur in high-speed rotating bodies.
これに対して従来からいろいろの方法が試みら
れている。古くから行なわれている方法の一つは
目標昇速運転中に異常振動が検知されると、運転
員の手操作による制御に切替えて昇速するやり方
である。しかしこの方法は全て運転員の判断に依
存するわけで、個人差がある上、果して適切な処
置がなされるかの問題があり好ましい方法ではな
い。 Various methods have been tried for this purpose. One method that has been used for a long time is to increase the speed by switching to manual control by the operator when abnormal vibrations are detected during target speed-up operation. However, this method depends entirely on the judgment of the operator, and there are individual differences, and there is the problem of whether appropriate measures can be taken, so it is not a preferable method.
また回転体の場合、固有振動周波数から定まる
危険速度領域があり、この危険速度領域では所謂
軸振動が増大することが知られている。第１図は
横軸に回転数Ｎ、縦軸に軸振動振幅Ａをプロツト
した場合の一般的な振動特性を示している。軸振
動が大きくなる領域ａを危険速度領域と呼ぶ。こ
の特性に関連して従来は次の２の方法で速度制御
を行なうことが知られている。その一つは危険速
度領域で振動を検知した場合、危険速度領域より
低く、振動に対して安定な回転数までタービン回
転数を降下させる方法である（特公昭52―32001
号）。しかしこの方法では、危険速度領域で振動
発生をを検知した場合速やかに回転数を降下させ
るかどうか、回転体の慣性などの影響で適切な処
置がとられないまゝ危険速度領域で回転を続けて
しまうおそれがある。大型の高速回転体の場合は
特にその可能性が大きい。 Furthermore, in the case of a rotating body, there is a critical speed region determined by the natural vibration frequency, and it is known that so-called shaft vibration increases in this critical speed region. FIG. 1 shows general vibration characteristics when the rotational speed N is plotted on the horizontal axis and the shaft vibration amplitude A is plotted on the vertical axis. Region a where the shaft vibration increases is called the critical speed region. In relation to this characteristic, it is conventionally known to perform speed control using the following two methods. One method is to reduce the turbine speed to a rotation speed that is lower than the dangerous speed range and stable against vibrations when vibration is detected in the dangerous speed range (Special Publication No. 52-32001).
issue). However, with this method, if vibration is detected in the dangerous speed range, it is difficult to immediately reduce the rotation speed, and due to the influence of the inertia of the rotating body, appropriate measures are not taken and the engine continues to rotate in the dangerous speed range. There is a risk that this may occur. This possibility is particularly large in the case of large, high-speed rotating bodies.
第２の方法は、危険速度領域における振動振幅
値の異常監視についてであつて、回転数信号を入
力とする関数発生器を用いて比較レベル信号を連
続的に変化させて振動異常を検出する方法である
（特公昭50―6886号）。この例ではさらに振動振幅
変化率を求めて所定値との比較によつて異常状態
を検知する方法が述べられている。しかしこの第
２の方法であつても、実測された振動振幅値の異
常を検出することにおいて前記の例と同様であつ
て、特に大型回転機の異常時の場合、遅滞なく適
切な処置がとられるかということに対して大きな
問題が残されている。比較的小形の回転機の場合
は速応処置が可能であるが、慣性が大きい回転機
の場合は、起動の途中で降速し、再び昇速するこ
とは避けなければいけない。 The second method is to monitor vibration amplitude abnormalities in the critical speed range, and detects vibration abnormalities by continuously changing a comparison level signal using a function generator that receives a rotation speed signal as input. (Special Publication No. 50-6886). This example further describes a method of detecting an abnormal state by determining the vibration amplitude change rate and comparing it with a predetermined value. However, even with this second method, it is similar to the above example in detecting an abnormality in the actually measured vibration amplitude value, and appropriate measures can be taken without delay, especially in the case of an abnormality in a large rotating machine. A big question remains as to whether it will be possible. In the case of a relatively small rotating machine, quick response measures can be taken, but in the case of a rotating machine with large inertia, it is necessary to avoid slowing down during startup and speeding up again.
本発明は前述の従来技術の問題点に鑑みてなさ
れたものであつて、危険速度領域における振動状
態をあらかじめ予測し、予測された結果に基づい
て回転体の速度制御を行なう速度制御方法を提供
することを目的とする。 The present invention has been made in view of the problems of the prior art described above, and provides a speed control method that predicts the vibration state in a critical speed range in advance and controls the speed of a rotating body based on the predicted result. The purpose is to
本発明の特徴は、回転体から定まる固有振動数
に対応する回転数ＮCと危険速度領域以外の回転
数に設定された昇速判定回転数ＮDとの差ΔＮを
演算し、この差ΔＮと実測した回転数Ｎとを用い
て前記回転数ＮCに達する所要時間ΔＴを演算
し、実測した振動振幅値Ａの変化率Ａ〓と前記所要
時間ΔＴを乗算して振動振幅の増分ΔＡを演算
し、この振動振幅の増分ΔＡと実測振幅値Ａとの
和Ａと予め設定された前記回転数ＮCにおける振
幅のしきい値ＡBとを比較演算し、前記和Ａがし
きい値ＡBを越えたかどうかによつて回転機の回
転数を保持又は変化させる軸振動監視による回転
機の速度制御方法にある。 The feature of the present invention is to calculate the difference ΔN between the rotation speed N C corresponding to the natural frequency determined from the rotating body and the acceleration determination rotation speed N D set to a rotation speed outside the critical speed area, and calculate the difference ΔN Calculate the time ΔT required to reach the rotation speed N C using the measured rotation speed N, and multiply the rate of change A〓 of the measured vibration amplitude value A by the required time ΔT to obtain the increment ΔA of the vibration amplitude. The sum A of this vibration amplitude increment ΔA and the measured amplitude value A is compared with the preset amplitude threshold value A B at the rotation speed N C , and the sum A is calculated as the threshold value A. A method of controlling the speed of a rotating machine by monitoring shaft vibration, which maintains or changes the rotational speed of the rotating machine depending on whether B is exceeded.
以下図面により本発明の実施例について詳細に
説明する。 Embodiments of the present invention will be described in detail below with reference to the drawings.
第２図は本発明の一実施例を示す。図において
２は回転体軸受部、３は振動検出器、４は平滑回
路、５は軸受部に取付けられた熱電対、６は増幅
器、７は回転パルスギア、８は電磁ピツクアツ
プ、９は増幅器、１は本発明の要部である昇速判
定装置、２５はこの昇速判定装置１の出力信号に
より回転体の速度を制御する速度制御装置であ
る。 FIG. 2 shows an embodiment of the invention. In the figure, 2 is a rotating body bearing, 3 is a vibration detector, 4 is a smoothing circuit, 5 is a thermocouple attached to the bearing, 6 is an amplifier, 7 is a rotating pulse gear, 8 is an electromagnetic pickup, 9 is an amplifier, 1 Reference numeral 25 denotes a speed increase determination device which is a main part of the present invention, and 25 a speed control device that controls the speed of the rotating body based on the output signal of the speed increase determination device 1.
さらに昇速判定装置１の詳細について述べる。
振動検出器３からの信号を平滑した振動信号Ａを
入力する。信号Ａは微分器１１により微分され、
変化率信号dA／dt＝Ａ〓が得られる。 Further, details of the acceleration determination device 1 will be described.
A vibration signal A obtained by smoothing the signal from the vibration detector 3 is input. Signal A is differentiated by a differentiator 11,
A rate of change signal dA/dt=A is obtained.
一方軸受メタル温度信号Mから固有振動周波
数に対応した回転数ＮCを演算する。１４は関数
発生器でMとＮCとの関係を設定しておく。回転
体の固有振動数はある一定温度条件では一定であ
るが、実際には軸受メタル温度によつて変動する
ことをわれわれは経験的に把握している。これら
の補正を行ない当該運転条件における真の固有振
動周波数に対応する回転数ＮCを求める。それは
例えば第３図に示すようなものである。第３図で
横軸はM、縦軸は回転数である。，はそれ
ぞれＮCであるが、は軸受メタル温度によりＮC
は変動しないとした場合、はMにより真のＮC
は変動する場合を示している。基準MOに対し
Ｍの値により真のＮCは変動していることを第３図
は示している。 On the other hand, the rotation speed N C corresponding to the natural vibration frequency is calculated from the bearing metal temperature signal M. 14 is a function generator that sets the relationship between M and N C. We know from experience that the natural frequency of a rotating body is constant under certain temperature conditions, but it actually varies depending on the bearing metal temperature. These corrections are made to find the rotational speed N C corresponding to the true natural vibration frequency under the operating conditions. For example, it is as shown in FIG. In Fig. 3, the horizontal axis is M and the vertical axis is the number of rotations. , are N C respectively, but N C depends on the bearing metal temperature.
If it is assumed that does not change, then is the true N C due to M
indicates a case where it fluctuates. With respect to standard MO
Figure 3 shows that the true N C varies depending on the value of M.
１５は予測を行なうべき回転数ＮDの設定器で
ある。１７は加算器でＮDとＮCの差ΔＮを演算す
る。この関係は第３図からも理解することが出来
るであろう。また第４図に横軸に回転数をとつた
場合のＮC，ＮDの関係、さらに第１図と同様にａ
は危険速度領域である。 Reference numeral 15 is a setting device for the rotational speed N D at which prediction should be performed. 17 is an adder which calculates the difference ΔN between N D and N C. This relationship can also be understood from Figure 3. Figure 4 also shows the relationship between N C and N D when the horizontal axis represents the number of rotations, and the same as in Figure 1.
is the critical speed area.
一方周波数―電圧の変換を行うＦ／Ｖ変換器１
０で回転数信号Ｎが演算される。１６は微分器で
Ｎ〓を演算する。１８は割算器でΔＮ／Ｎ〓を演算し
ΔＴを求める。ΔＴはＮ〓で昇速を続けた場合のＮ
Cに到達する所要時間である。乗算器１２でＡ〓×
ΔＴすなわち振動振幅の増分ΔＡが演算される。
加算器１３ではＡ＋ΔＡ＝Ａが演算されＮCにお
けるしきい値、設定値ＡBと加算器２０で演算さ
れ、ΔＡCが求まる。ΔＡC０であるときステツ
プ信号発生器２１の出力がONされる。ΔＡC＞０
はＮC時点において振動振幅値Ａがしきい値ＡBを
越えたことを意味し、警報などの処理を行なう
か、現時点ＮDにおける運転制御を変更しなけれ
ばいけない。 On the other hand, F/V converter 1 that performs frequency-voltage conversion
0, the rotational speed signal N is calculated. 16 is a differentiator that calculates N〓. Reference numeral 18 uses a divider to calculate ΔN/N and obtain ΔT. ΔT is N when the speed continues to increase at N〓
This is the time required to reach C. A〓× in multiplier 12
ΔT, that is, the vibration amplitude increment ΔA is calculated.
The adder 13 calculates A+ΔA=A, and the adder 20 calculates the threshold value at N C and the set value A B to find ΔA C. When ΔAC is 0, the output of the step signal generator 21 is turned on. ΔAC >0
means that the vibration amplitude value A exceeds the threshold A B at the time N C , and it is necessary to perform processing such as a warning or change the operation control at the current N D.
２３は接点でＮ―ＮD≦０の時出力信号がONと
なる比較器２２の出力信号が印加される。２４は
アンド回路でＮとＮDとの関係が満足されたとき
のみ速度制御装置ＳNを速度制御装置２５に入力
される。 23 is a contact to which the output signal of the comparator 22 is applied, the output signal being ON when N-N D ≦0. 24 is an AND circuit which inputs the speed control device S N to the speed control device 25 only when the relationship between N and N D is satisfied.
第４図から明らかなようにΔＡC０の時はそ
のまゝ昇速を続けることが出来ない場合、ΔＡC
＜０の時はＮDの時点における昇速率で昇速を行
なつてもよい場合である。同図ｂはMにより変
動するであろうＮCの変動範囲を示している。 As is clear from Fig. 4, when ΔA C is 0, if it is not possible to continue increasing the speed, ΔA C
When <0, the speed may be increased at the speed increase rate at the time of N D. Figure b shows the variation range of N C that will vary depending on M.
こゝでＮDは危険速度領域以外の速度領域に設
けられた判定回転数であつてあらかじめ定められ
た回転数である。 Here, N D is a predetermined rotation speed that is set in a speed range other than the critical speed range.
第５図はタービン昇速過程を横軸に時間をとつ
た場合について示した。(i)は振動振幅特性、(ii)は
昇速状態を示している。t1時点でＮDに達し、ＮC
におけるＡすなわちＡを予測したところＡ―ＡB
０となり退避速度Ｎdへ一旦退避させる。ｄは
Ａ−ＡB＜０となるまで退避運転が必要であるこ
とを示している。 FIG. 5 shows the turbine speed-up process with time plotted on the horizontal axis. (i) shows the vibration amplitude characteristics, and (ii) shows the speed increase state. At time t 1 , N D is reached, and N C
When predicting A, that is, A, A-A B
0 and is temporarily evacuated to the evacuation speed N d . d indicates that evacuation operation is necessary until A-A B <0.
ある定められた時間退避運転を再び昇速をはじ
めt2においてＮ＝ＮDとなり再びＮCにおけるＡを
予測した結果Ａ―ＡB０を満足し、昇速が可能
になつた場合を示している。Ｕは振動振幅の余裕
値を示している。ｂは第４図と同様に軸受メタル
温度による固有振動周波数の変動に対応した回転
数変動領域を示す。この実施例ではt1時点からＮ
dに退避させる運転を行なつているが、必らずし
も退避速度に降速させる必要もなく、ＮDを持続
する方法であつてもよい。Ｎdを保持しつつ第４
図との関係で云えばΔＡCを監視し、ΔＡCが昇速
条件を満足した時点で昇速を再び開始すればよ
い。ＮD一定保持後ＮDへ降速させる方法でもよ
い。 The following shows the case where the evacuation operation for a certain period of time begins to accelerate again, and at t 2 , N = N D , and A at N C is predicted again, and as a result, A - A B 0 is satisfied, and it is possible to increase the speed. There is. U indicates the margin value of vibration amplitude. Similarly to FIG. 4, b shows the rotational speed fluctuation region corresponding to the fluctuation of the natural vibration frequency due to the bearing metal temperature. In this example, from time t 1 , N
Although the vehicle is operated to evacuate to d , it is not necessarily necessary to reduce the speed to the evacuating speed, and a method of maintaining N D may be used. 4th while holding N d
In relation to the diagram, it is sufficient to monitor ΔA C and restart speed increase when ΔA C satisfies the speed increase condition. A method of decreasing the speed to N D after keeping N D constant may also be used.
またＮC＝一定の場合、すなわちMによるＮC
のシフト分が小さいときは例えば第６図に示すよ
うに加算器１７′でＮとＮDとの偏差ΔN′を求め
て、割算器１８′でΔＴを求める方法であつても
よい。 Also, when N C = constant, that is, N C due to M
When the shift amount is small, for example, as shown in FIG. 6, an adder 17' may be used to obtain the deviation ΔN' between N and N D , and a divider 18' may be used to obtain ΔT.
また第２図においてMにより真のＮCを求める
ために関数発生器１４を用いているが、ＮCの変
動に応じてＮDを補正する方式であつてもよい。
例えば第７図に示すように信号ＮCを係数器ｋを
介して乗算器７０で乗算しＮDを補正しN′Dと
し、N′Dを判定回転数として演算に使用する。こ
の方法では真のＮCの変動に応じてＮDを補正する
のでＮCに対応した最適な判定ができるという効
果がある。 Further, in FIG. 2, the function generator 14 is used to obtain the true N C from M , but a method may be used in which N D is corrected according to fluctuations in N C.
For example, as shown in FIG. 7, the signal N C is multiplied by a multiplier 70 via a coefficient unit k, N D is corrected to N' D , and N' D is used as the determination rotation speed in the calculation. This method has the effect of correcting N D in accordance with the fluctuation of the true N C , so that it is possible to make an optimal determination corresponding to N C.
第１図に示した危険速度領域ａはＮCに対する
あらかじめ定めた割合で定めてもよい。ＮCの値
にかゝわらず一定割合の領域が危険速度領域とし
て特定できる特徴がある。 The critical speed region a shown in FIG. 1 may be determined by a predetermined ratio to N C . It has the characteristic that a certain percentage of the area can be identified as a critical speed area regardless of the value of N C.
また第４図においてＮCにおける振動振幅値を
予測するための速度上昇率をＮDを含む複数の回
転数において演算しその平均値を用いる方法であ
つてもよい。この場合は何回かの平均値を用いる
ので、ＮCにおける予測精度がより向上し、信頼
性の高い予測結果が得られる特徴がある。 Alternatively, in FIG. 4, the speed increase rate for predicting the vibration amplitude value at N C may be calculated at a plurality of rotational speeds including N D , and the average value thereof may be used. In this case, since the average value of several times is used, the prediction accuracy in N C is further improved and a highly reliable prediction result can be obtained.
本発明によればあらかじめ固有振動数に対応し
た回転数における軸振動振幅の予測値に基いて昇
速するので回転機を異常振動状態にすることがな
い。 According to the present invention, since the speed is increased in advance based on the predicted value of the shaft vibration amplitude at the rotation speed corresponding to the natural frequency, the rotating machine is not brought into an abnormal vibration state.
第１図は回転数と振動振幅の関係を示す図、第
２図は本発明の具体的実施例のブロツク構成図、
第３図は軸受メタル温度と固有振動周波数に対応
した回転数との関係を示す図、第４図は昇速判定
説明図、第５図は昇速過程の説明図、第６図、第
７図は本発明の他の実施例を示す。
３……振動検出器、４……平滑回路、５……熱
電対、７……回転パルスギア、８……電磁ピツク
アツプ、１５……ＮD設定器、１７……加算器、
１８……割算器、２５……速度制御装置。
Fig. 1 is a diagram showing the relationship between rotation speed and vibration amplitude, Fig. 2 is a block configuration diagram of a specific embodiment of the present invention,
Figure 3 is a diagram showing the relationship between the bearing metal temperature and the rotational speed corresponding to the natural vibration frequency, Figure 4 is an explanatory diagram of speed increase determination, Figure 5 is an explanatory diagram of the speed increase process, and Figures 6 and 7. The figures show other embodiments of the invention. 3... Vibration detector, 4... Smoothing circuit, 5... Thermocouple, 7... Rotating pulse gear, 8... Electromagnetic pickup, 15... N D setting device, 17... Adder,
18...Divider, 25...Speed control device.
Claims (1)
数ＮCと危険速度領域以外の回転数に設定された
昇速判定回転数ＮDとの差ΔＮを演算し、この差
ΔＮと実測した回転数Ｎとを用いて前記回転数Ｎ
Cに達する所要時間ΔＴを演算し、実測した振動
振幅値Ａの変化率Ａ〓と前記所要時間ΔＴを乗算し
て振動振幅の増分ΔＡを演算し、この振動振幅の
増分ΔＡと実測振幅値Ａとの和Ａと予め設定され
た前記回転数ＮCにおける振幅のしきい値ＡBとを
比較演算し、前記和Ａがしきい値ＡBを越えたか
どうかによつて回転機の回転数を保持又は変化さ
せることを特徴とする軸振動監視による回転機の
速度制御方法。1 Calculate the difference ΔN between the rotation speed N C corresponding to the natural frequency determined from the rotating body and the acceleration judgment rotation speed N D set to a rotation speed outside the dangerous speed area, and calculate the difference ΔN and the actually measured rotation speed. N and the rotational speed N
Calculate the required time ΔT to reach C , multiply the rate of change A of the actually measured vibration amplitude value A by the required time ΔT to calculate the vibration amplitude increment ΔA, and calculate the vibration amplitude increment ΔA and the actually measured amplitude value A. The sum A is compared with a preset amplitude threshold A B at the rotation speed N C , and the rotation speed of the rotating machine is determined depending on whether the sum A exceeds the threshold value A B. A method for controlling the speed of a rotating machine by monitoring shaft vibration, characterized by holding or changing the speed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2665880A JPS56124918A (en) | 1980-03-05 | 1980-03-05 | Speed controlling method of rotary machine by monitoring axial vibration |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2665880A JPS56124918A (en) | 1980-03-05 | 1980-03-05 | Speed controlling method of rotary machine by monitoring axial vibration |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56124918A JPS56124918A (en) | 1981-09-30 |
| JPS6236246B2 true JPS6236246B2 (en) | 1987-08-06 |
Family
ID=12199517
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2665880A Granted JPS56124918A (en) | 1980-03-05 | 1980-03-05 | Speed controlling method of rotary machine by monitoring axial vibration |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS56124918A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2644841A1 (en) | 2012-03-29 | 2013-10-02 | Alstom Technology Ltd | Method of operating a turbine engine after flame off |
| CN113682937A (en) * | 2021-08-30 | 2021-11-23 | 日立电梯（广州）自动扶梯有限公司 | Escalator vibration reduction system and escalator vibration reduction method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5080874A (en) * | 1973-11-15 | 1975-07-01 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5242124Y2 (en) * | 1972-10-06 | 1977-09-24 |
-
1980
- 1980-03-05 JP JP2665880A patent/JPS56124918A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5080874A (en) * | 1973-11-15 | 1975-07-01 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56124918A (en) | 1981-09-30 |
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