JPH0350918B2 - - Google Patents
Info
- Publication number
- JPH0350918B2 JPH0350918B2 JP58032726A JP3272683A JPH0350918B2 JP H0350918 B2 JPH0350918 B2 JP H0350918B2 JP 58032726 A JP58032726 A JP 58032726A JP 3272683 A JP3272683 A JP 3272683A JP H0350918 B2 JPH0350918 B2 JP H0350918B2
- Authority
- JP
- Japan
- Prior art keywords
- stage
- compressor
- vanes
- vane
- flow rate
- 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 - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0269—Surge control by changing flow path between different stages or between a plurality of compressors; load distribution between compressors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、多段圧縮機の容量調節法に関し、特
に、段間に冷却器を有する多段遠心圧縮機、軸流
圧縮機と遠心圧縮機を有する複合圧縮機などの効
率向上に好適な容量調節方法に関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a method for adjusting the capacity of a multistage compressor, and in particular, a multistage centrifugal compressor having a cooler between stages, an axial flow compressor, and a centrifugal compressor. The present invention relates to a capacity adjustment method suitable for improving the efficiency of a compound compressor, etc.
近年の世界的な省資源、省エネルギー等で、圧
縮機の設計点効率のみならず、部分負荷効率の向
上が非常に重要になつてきた。すなわち、大形の
プラントにおいては、わずか１％程度の圧縮機効
率の違いが電力の大きな節約となつてあらわれ
る。
In recent years, with global efforts to conserve resources and energy, it has become extremely important to improve not only the design point efficiency but also the partial load efficiency of compressors. That is, in a large-scale plant, a difference in compressor efficiency of only about 1% results in a large saving in electric power.
ちなみに空気分離装置では、プラント動力の約
６割が圧縮機が占める。このようにプラント動力
に占める圧縮機の割合が大きいことからも圧縮機
の効率向上が要求される理由でもある。 By the way, in air separation equipment, the compressor accounts for about 60% of the plant power. The fact that the compressor accounts for such a large proportion of the plant power is also the reason why improvements in the efficiency of the compressor are required.
このような背景から、たとえば、多段遠心圧縮
機においては、各段入口にベーンを配置し、この
ベーンを操作することによつて容量調節が行なわ
れているが、更に効率の良い方法が要求されるよ
うになつてきた。その代表的な手法としては、本
願出願人が先に提案した特願昭54−27744号（特
開昭55−123394号）発明の名称「多段遠心圧縮機
の制御方法」がある。この制御方法は、複数段ベ
ーンを一回ずつ試行的に動かして効率の変化を確
認し、効率の頂点を見出す方法である。 Against this background, for example, in multi-stage centrifugal compressors, capacity is adjusted by placing vanes at the inlets of each stage and manipulating these vanes, but a more efficient method is required. It's starting to feel like this. As a typical method, there is a method for controlling a multi-stage centrifugal compressor, which was previously proposed by the applicant of the present application and is disclosed in Japanese Patent Application No. 54-27744 (Japanese Unexamined Patent Publication No. 55-123394). This control method is a method in which the multi-stage vanes are moved once at a time to confirm changes in efficiency, and the peak of efficiency is found.
しかしながら、この効率は流体効率を用いてお
り次のような欠点がある。 However, this efficiency uses fluid efficiency and has the following drawbacks.
すなわち、流体効率（η）は(1)式で表わされ
る。 That is, fluid efficiency (η) is expressed by equation (1).
η＝RTsloge（Pd／Ps）・Ｇ／Ls ……(1) ここで、 Ｒ：ガス定数 Ts：１段吸込温度 Ps・Pd：１段吸込圧力・圧縮機吐出圧力 Ｇ：圧縮機流量 Ls：駆動機動力 また、圧縮機流量(G)は(2)式から得る。 η=RT s loge(P d /P s )・G/L s ……(1) Here, R: Gas constant T s : 1st stage suction temperature P s・P d : 1st stage suction pressure/Compressor discharge Pressure G: Compressor flow rate L s : Drive machine power Also, the compressor flow rate (G) is obtained from equation (2).
ここで、
Ｋ：係数
ΔP：圧縮機最終段の吐出管路に設けたオリフイ
ス差圧
P0：圧縮機最終段の吐出管路に設けたオリフイ
ス前圧
T0：圧縮機最終段の吐出管路に設けたオリフイ
ス前温
(1)、(2)式から分かるようにん流体効率を得るに
は少なくともTs、Ps、Ls、ΔP、P0、T0の７つの
物理量を計測する必要がある。従つて、これらを
ベーンコントロールの制御装置に取込むセンサー
を必要とするばかりでなく、変換器、増幅器が必
要となる。これらの機器は必ず誤差が存在し、誤
差が集積されて効率の算出精度が悪くなる。たと
え、一般に用いられている工業計器よりも数段精
度の良いものを用いても流体効率の算出精度は±
１％程度になる。すわなち、これ以上の精度の省
エネルギー運転は流体効率を用いた効率評価では
困難である。 Here, K: Coefficient ΔP: Differential pressure of the orifice provided in the discharge pipe of the final stage of the compressor P 0 : Pressure before the orifice provided in the discharge pipe of the final stage of the compressor T 0 : Discharge pipe of the final stage of the compressor As can be seen from equations (1) and (2), it is necessary to measure at least seven physical quantities: T s , P s , L s , ΔP, P 0 , and T 0 There is. Therefore, not only a sensor is required to incorporate these into the vane control control device, but also a converter and an amplifier are required. These devices always have errors, and as the errors accumulate, the efficiency calculation accuracy deteriorates. Even if you use a meter that is several steps more accurate than commonly used industrial meters, the accuracy of calculating fluid efficiency will be ±
It will be around 1%. In other words, energy-saving operation with higher precision than this is difficult to achieve with efficiency evaluation using fluid efficiency.
更に、多段圧縮機の高効率運転を意図した方法
として、特開昭57−2497号公報に記載の例があ
る。しかし、この方法も結局ベーン動作を試行錯
誤させて最適制御を探るもので、プラントの要求
流量に変動をきたし、また、ベーン動作回数が多
くなるという問題があつた。 Furthermore, as a method intended for highly efficient operation of a multi-stage compressor, there is an example described in Japanese Patent Application Laid-Open No. 57-2497. However, this method also involves trial and error of vane operation in order to find the optimal control, which has the problem of causing fluctuations in the required flow rate of the plant and increasing the number of vane operations.
本発明の目的は、プラントから要求される流量
を満足し、かつ流量変動をできるだけ小さくする
と共に、ベーン動作回数の少ない圧縮機の容量調
節方法を提供し、併わせて、効率評価の精度向上
と物理量の計測を極力少なくした容量調節方法を
提供するところにある。
An object of the present invention is to provide a method for adjusting the capacity of a compressor that satisfies the flow rate required by a plant, minimizes flow rate fluctuations, and reduces the number of vane operations. The purpose of the present invention is to provide a capacity adjustment method that minimizes the measurement of physical quantities.
本発明の要旨は、複数段で構成される圧縮機の
少なくとも２個以上の圧縮段の入口に、開度調節
可能なベーンを配置し、第１段に配置したベーン
を前段グループとし、第２段以降に配置したベー
ンを後段グループとして、前記圧縮機の流量と目
標流量とを比較して該比較値の差が所定の許容偏
差内に達するまで、前記前段グループベーンと後
段グループベーンとの間で各ベーンの開度の調節
を行い、さらに該比較値の差が前記許容偏差内に
達したことを検知する検知工程と、該許容偏差内
で前記各ベーンの開度を調節する開度調節工程と
を備えてなる多段圧縮機の容量調節方法におい
て、前記許容偏差内の開度調節工程で、前記前段
グループのベーン開閉方向と前記後段グループの
ベーン開閉方向とを反対にし、且つ前段ベーンの
操作量を後段ベーンの操作量より少なくしたこと
を特徴とする多段圧縮機の容量調節方法、にあ
る。
The gist of the present invention is to arrange vanes whose opening degree can be adjusted at the inlets of at least two or more compression stages of a compressor composed of multiple stages, the vanes arranged in the first stage are set as a front stage group, and the vanes arranged in the first stage are set as a front stage group, and the vanes arranged in the first stage are The vanes arranged after the stage are treated as a rear stage group, and the flow rate of the compressor is compared with the target flow rate until the difference in the comparison value reaches a predetermined tolerance. a detection step of adjusting the opening degree of each vane, and further detecting that the difference between the comparison values has reached the tolerance deviation; and an opening adjustment step of adjusting the opening degree of each vane within the tolerance deviation. In the method for adjusting the capacity of a multi-stage compressor, the step of adjusting the opening within the allowable deviation reverses the opening/closing direction of the vanes of the preceding stage group and the opening/closing direction of the vanes of the latter stage group, and A method for adjusting the capacity of a multi-stage compressor, characterized in that the amount of operation is made smaller than the amount of operation of a rear stage vane.
上記構成によれば、第１段の前段グループと第
２段以降の後段グループとでベーン開閉方向を逆
にしたので、流量変化を小さくでき、流体効率が
向上する。又、最初の動作方向を圧縮機効率の良
くなる方向にすることができ、ベーン動作回数を
少なくすることができるので、摺動摩耗も減少す
る。更に、後段ベーン操作量を前段のそれより多
くしたので、同一流量になりやすく、流量変化を
小さくすることができる。 According to the above configuration, since the vane opening/closing direction is reversed between the front stage group of the first stage and the rear stage group after the second stage, the change in flow rate can be reduced and fluid efficiency is improved. Furthermore, since the initial operating direction can be set in a direction that improves compressor efficiency and the number of vane operations can be reduced, sliding wear is also reduced. Furthermore, since the amount of operation of the rear stage vane is made larger than that of the front stage, the flow rate can be easily maintained at the same level, and the change in flow rate can be reduced.
以下、本発明の一実施例を第１図ないし第５図
にもとづいて説明する。
An embodiment of the present invention will be described below with reference to FIGS. 1 to 5.
第１図は段間に冷却器４，５を、各段入口には
ベーン６〜８を有する多段圧縮の遠心圧縮機の容
量調節方法の系統図を示す。各段入口のベーンは
それぞれベーン駆動装置１７，１８を有する。ベ
ーン駆動装置１８は第２段、第３段のベーン７，
８のそれを共用している。このベーン駆動装置１
７，１８は制御装置１９からベーン開度指令信号
２１，２２をベーンを駆動するための機械的な力
に変換するものである。一方この圧縮機の流量は
吐出のオリフイス差圧、前温、前圧によつて計測
される。これらはそれぞれの変換器１１，１２，
１３によつて電気信号に変換され演算器にて吐出
流量に変換される。１０は吐出管路Ｂに設けたオ
リフイス、Ａは吸込管路、９は多段圧縮機の駆動
機である。また多段圧縮機の容量制御をつかさど
る制御装置１９は、第２図にその詳細を示したよ
うに中央処理装置２５、制御装置動作命令記憶装
置２６、記憶装置２７、入力装置２８、出力処理
装置２９、インターフエイス３０，３１とから構
成される。従つて、信号流量演算のためのオリフ
イス差圧１１、オリフイス前圧１２、同前温１
３、駆動機動力９Ａ、目標流量信号２０は制御装
置１９へ入力される。 FIG. 1 shows a system diagram of a method for adjusting the capacity of a multistage centrifugal compressor having coolers 4 and 5 between the stages and vanes 6 to 8 at the inlet of each stage. Each stage inlet vane has a vane drive 17, 18, respectively. The vane drive device 18 includes second-stage, third-stage vanes 7,
8 is shared. This vane drive device 1
7 and 18 convert vane opening command signals 21 and 22 from the control device 19 into mechanical force for driving the vanes. On the other hand, the flow rate of this compressor is measured by the discharge orifice differential pressure, pre-temperature, and pre-pressure. These are respective converters 11, 12,
13, it is converted into an electrical signal, and then converted into a discharge flow rate by a computing unit. 10 is an orifice provided in the discharge pipe B, A is a suction pipe, and 9 is a drive machine for the multistage compressor. Further, the control device 19 in charge of capacity control of the multi-stage compressor includes a central processing unit 25, a control device operation command storage device 26, a storage device 27, an input device 28, and an output processing device 29, as shown in detail in FIG. , and interfaces 30 and 31. Therefore, orifice differential pressure 11, orifice front pressure 12, and orifice front temperature 1 for calculating signal flow rate
3. The driving machine power 9A and the target flow rate signal 20 are input to the control device 19.
以上のように構成されたものにおいて圧縮機の
目標流量信号２０が制御装置１９に指示され、フ
イードバツクされた吐出流量信号として各ベーン
駆動装置１７，１８に指令することによつて圧縮
機の容量調節を行なう。 In the configuration as described above, the target flow rate signal 20 of the compressor is instructed to the control device 19, and the capacity of the compressor is adjusted by instructing each vane driving device 17, 18 as a feedback discharge flow rate signal. Do this.
ここまでの操作は、圧縮機流量を第３図に示す
ように要求する目標流量に対応するＡ点に対して
所定の許容流量偏差ε内に調節するものである。
同図中２３は、圧縮機の特性曲線、２４はプラン
トの抵抗ラインである。前述の所定の許容流量偏
差ε内に調節するとき、前段ベーンと後段ベーン
開度は第４図の直線ａのような関係で動く。この
直線ａは全ての位置で圧縮機効率の最高点と一致
することは不可能である。すなわち、第４図の等
効率曲線ｂの尾根と直線ａはほとんどの位置で同
じとはならない。従つて、目標流量到達後は、同
じ流量（許容範囲ε内で）を保ちながら前段ベー
ン６と後段ベーン７，８を試行操作しながら最高
効率点を探索する。 The operations up to this point are for adjusting the compressor flow rate within a predetermined allowable flow rate deviation ε with respect to point A corresponding to the required target flow rate as shown in FIG.
In the figure, 23 is a characteristic curve of the compressor, and 24 is a resistance line of the plant. When adjusting the flow rate within the predetermined permissible flow deviation ε, the openings of the front and rear vanes move in a relationship as shown by straight line a in FIG. 4. It is impossible for this straight line a to coincide with the highest point of compressor efficiency at all positions. That is, the ridge of the iso-efficiency curve b in FIG. 4 and the straight line a are not the same at most positions. Therefore, after the target flow rate is reached, the highest efficiency point is searched for while maintaining the same flow rate (within the allowable range ε) and trially operating the front vane 6 and the rear vanes 7 and 8.
この場合、本発明にあつては、駆動機動力の絶
体値の増減を判断して行なう。一般に駆動機動力
は流量に比例するので、流量が減れば当然駆動機
動力も減り見かけ上効率が良くなるという問題が
ある。従つて駆動機動力を効率変化の判定のバラ
メータとして用いるためには、各段ベーン６〜８
の試行動作において流量が変化しないようにしな
ければならない。この操作は、制御装置１９によ
つてなされる。 In this case, according to the present invention, the increase or decrease in the absolute value of the driving force is determined. Generally, the drive power is proportional to the flow rate, so if the flow rate decreases, the drive power also decreases, resulting in an apparent improvement in efficiency. Therefore, in order to use the driving force as a parameter for determining efficiency changes, it is necessary to
It shall be ensured that the flow rate does not change during the trial operation. This operation is performed by the control device 19.
すなわち、第２図において、流量演算のための
吐出流量信号を、インターフエイス３０を通して
入力装置２８により取込み、記憶装置２７に記憶
する。これらのデータから流量を演算し、同様に
入力し、記憶装置２７に記憶した目標流量と比較
し、その差が所定の許容値εより大きければ、ベ
ーン６〜８の動作量を決め出力装置２９によりイ
ンターフエイス３１を通してベーン駆動装置１
７，１８に動作信号が出る。最終的に上記偏差が
許容値内に入れば、そのときの軸動力を記憶す
る。入力記憶方法は上記の他の検出物理量と同じ
である。以降の動作は前・後段ベーン操作を２組
の方法に分け試行しその都度、駆動機動力を上述
の方法で取込み、駆動機動力が前回の試行時の値
より小さければさらにその方向に試行し、最終的
に駆動機動力最小位置を探索する。中央処理装置
２５では、上述の一連の動作命令を記憶した記憶
装置２６の内容を解読し、各装置に上述の動作を
行なわす。 That is, in FIG. 2, a discharge flow rate signal for calculating the flow rate is taken in by the input device 28 through the interface 30 and stored in the storage device 27. The flow rate is calculated from these data and compared with the target flow rate input in the same way and stored in the storage device 27. If the difference is larger than a predetermined tolerance value ε, the amount of operation of the vanes 6 to 8 is determined and the output device 29 through the interface 31 to the vane drive device 1.
Operation signals are output at 7 and 18. If the deviation finally falls within the allowable value, the shaft power at that time is stored. The input storage method is the same as for the other detected physical quantities described above. For subsequent operations, try to operate the front and rear vanes in two different ways, and each time, take in the driving force using the method described above, and if the driving force is smaller than the value from the previous trial, try again in that direction. , and finally searches for the minimum driving force position. The central processing unit 25 decodes the contents of the storage device 26 that stores the series of operation instructions described above, and causes each device to perform the operations described above.
この中央処理装置２５内演算処理作業をフロー
チヤートで示すと、第５図に示す通りである。第
５図において、第２図と同一物に同一符号を付し
てある。 The arithmetic processing work within the central processing unit 25 is shown in a flowchart as shown in FIG. In FIG. 5, the same parts as in FIG. 2 are given the same reference numerals.
以上説明したように本発明にあつては駆動機動
力の最小値を見い出すようにすれば良いのである
が、その最も良い方法について以下説明する。 As explained above, in the present invention, it is sufficient to find the minimum value of the drive force, and the best method for this will be explained below.
第４図に戻つて、同一流量曲線ｃは、前段ベー
ン開度大からなるときは後段ベーン開度小から大
なる方向にゆるやかな傾斜を持つ。そこでベーン
の試行操作を後段ベーン開度開操作なら前段ベー
ン開度閉操作、後段ベーン開度閉操作なら前段ベ
ーン開度開操作になるように前段と後段のベーン
操作を２組の方法に分け試行することにより流量
変化は小さくて流体効率の向上のみが得られる。
尚さらに上述のベーン操作では前段ベーン操作量
に比べ後段ベーン操作量を多くすると同一流量曲
線にのりやすく、流量変化を小さくして流体効率
の向上のみが得られるので、このようにすること
が本発明の特徴である。 Returning to FIG. 4, the same flow rate curve c has a gentle slope in the direction from small to large rear stage vane opening when the front stage vane opening is large. Therefore, the trial operation of the front and rear vanes is divided into two methods: if the rear stage vane opening is open, the front vane is closed, and if the rear vane is closed, the front vane is opened. By experimenting, the change in flow rate is small and only an improvement in fluid efficiency can be obtained.
Furthermore, in the above-mentioned vane operation, if the amount of operation of the rear vane is increased compared to the amount of operation of the front stage vane, it is easier to follow the same flow rate curve, and the only improvement in fluid efficiency can be achieved by reducing the change in flow rate, so it is essential to do this in this way. This is a feature of the invention.
以上述べたように本発明によれば、圧縮機第１
段の前段グループと第２段以降の後段グループの
ベーン開閉方向を逆にし、前段ベーンの操作量を
後段のそれより少なくすることにより、流量変動
が防止され、容量調節装置の寿命も延びる。その
ため、より高い効率で容量制御を達成することが
できるとともに、圧縮機効率が向上して長期運転
ができるようになつた。
As described above, according to the present invention, the compressor first
By reversing the opening and closing directions of the vanes in the front stage group and the rear stage group after the second stage, and by making the amount of operation of the front stage vanes smaller than that of the rear stages, flow rate fluctuations are prevented and the life of the capacity adjustment device is extended. As a result, capacity control can be achieved with higher efficiency, and compressor efficiency has improved, allowing long-term operation.
第１図は本発明の方法を実施するための多段遠
心圧縮機の系統図、第２図は第１図の制御装置の
詳細図、第３図は圧縮機の運転状態説明図、第４
図は本発明の方法の最良の態様を説明するための
動作説明図、第５図は本発明の制御方法に用いら
れる制御装置の演算処理作業のフローチヤートで
ある。
１〜３……１〜３段圧縮機、４，５……中間冷
却器、６〜８……ベーン、１７，１８……ベーン
駆動装置、１９……制御装置。
Fig. 1 is a system diagram of a multi-stage centrifugal compressor for implementing the method of the present invention, Fig. 2 is a detailed view of the control device shown in Fig. 1, Fig. 3 is an explanatory diagram of the operating state of the compressor, and Fig. 4 is a diagram illustrating the operating state of the compressor.
The figure is an operational explanatory diagram for explaining the best mode of the method of the present invention, and FIG. 5 is a flowchart of the arithmetic processing work of the control device used in the control method of the present invention. 1-3... 1-3 stage compressor, 4, 5... Intercooler, 6-8... Vane, 17, 18... Vane drive device, 19... Control device.
Claims (1)
以上の圧縮段の入口に、開度調節可能なベーンを
配置し、第１段に配置したベーンを前段グループ
とし、第２段以降に配置したベーンを後段グルー
プとして、前記圧縮機の流量と目標流量とを比較
して該比較値の差が所定の許容偏差内に達するま
で、前記前段グループベーンと後段グループベー
ンとの間で各ベーンの開度の調節を行い、さらに
該比較値の差が前記許容偏差内に達したことを検
知する検知工程と、該許容偏差内で前記各ベーン
の開度を調節する開度調節工程とを備えてなる多
段圧縮機の容量調節方法において、 前記許容偏差内の開度調節工程で、前記前段グ
ループのベーン開閉方向と前記後段グループのベ
ーン開閉方向とを反対にし、且つ前段ベーンの操
作量を後段ベーンの操作量より少なくしたことを
特徴とする多段圧縮機の容量調節方法。 ２ 前記多段圧縮機は各段間に中間冷却器を配置
してなる特許請求の範囲第１項記載の多段圧縮機
の容量調節方法。 ３ 前記多段圧縮機を３段で構成し、前記各段に
設けたベーンの駆動器の内、第２段、第３段の駆
動機を共用したことを特徴とする特許請求の範囲
第１項記載の多段圧縮機の容量調節方法。[Scope of Claims] 1. Vanes whose opening degree can be adjusted are arranged at the inlets of at least two or more compression stages of a compressor composed of multiple stages, and the vanes arranged in the first stage are set as a front stage group, and the vanes arranged in the first stage are set as a front stage group. The flow rate of the compressor is compared with the target flow rate, and the vanes arranged in the second stage and subsequent stages are treated as the latter group, and the flow rate of the first stage group vanes and the second stage group vanes are a detection step of adjusting the opening degree of each vane between the steps, and further detecting that the difference between the comparison values has reached the permissible deviation; and an opening degree of adjusting the opening degree of each vane within the permissible deviation. In the method for adjusting the capacity of a multi-stage compressor, the method for adjusting the capacity of a multi-stage compressor comprises: in the step of adjusting the opening within the tolerance, the opening/closing direction of the vanes in the front stage group and the opening/closing direction of the vanes in the rear stage group are reversed; A method for adjusting the capacity of a multi-stage compressor, characterized in that the amount of operation of the vane is made smaller than the amount of operation of a rear stage vane. 2. The method for adjusting the capacity of a multi-stage compressor according to claim 1, wherein the multi-stage compressor has an intercooler disposed between each stage. 3. Claim 1, characterized in that the multi-stage compressor is composed of three stages, and among the vane drivers provided in each stage, the second stage and third stage drivers are shared. The capacity adjustment method of the multistage compressor described.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3272683A JPS59160097A (en) | 1983-03-02 | 1983-03-02 | Capacity regulation of multi-stage compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3272683A JPS59160097A (en) | 1983-03-02 | 1983-03-02 | Capacity regulation of multi-stage compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59160097A JPS59160097A (en) | 1984-09-10 |
| JPH0350918B2 true JPH0350918B2 (en) | 1991-08-05 |
Family
ID=12366841
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3272683A Granted JPS59160097A (en) | 1983-03-02 | 1983-03-02 | Capacity regulation of multi-stage compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59160097A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008121451A (en) | 2006-11-09 | 2008-05-29 | Mitsubishi Heavy Ind Ltd | Turbo refrigeration device and method of controlling the same |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS572497A (en) * | 1980-06-04 | 1982-01-07 | Hitachi Ltd | Volume control method for centrifugal compressor |
-
1983
- 1983-03-02 JP JP3272683A patent/JPS59160097A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59160097A (en) | 1984-09-10 |
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