JP2001082380A - Method and device for controlling volume of gas force feeding device - Google Patents
Method and device for controlling volume of gas force feeding deviceInfo
- Publication number
- JP2001082380A JP2001082380A JP25488699A JP25488699A JP2001082380A JP 2001082380 A JP2001082380 A JP 2001082380A JP 25488699 A JP25488699 A JP 25488699A JP 25488699 A JP25488699 A JP 25488699A JP 2001082380 A JP2001082380 A JP 2001082380A
- Authority
- JP
- Japan
- Prior art keywords
- gas
- surging
- pumping device
- signal
- gas pumping
- 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
Landscapes
- Control Of Positive-Displacement Air Blowers (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は一般製造、組立工場
等で空気源や昇圧窒素の如き原料用気体源として用いる
遠心圧縮機や送風機等の気体圧送装置の容量制御方法及
び装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method and an apparatus for controlling the capacity of a gas pumping device such as a centrifugal compressor or a blower used as an air source or a gas source for a raw material such as pressurized nitrogen in a general manufacturing or assembly plant. .
【０００２】[0002]
【従来の技術】一例として、無負荷運転とすることによ
り使用量がサージング限界風量以下となったときサージ
ング回避を行うようにした従来の圧縮機の容量制御につ
いて示すと、図９に示す如く、遠心式の圧縮機１に吸入
される気体の吸入側配管２の途中に吸入弁３を設け、
又、圧縮機１から吐出された圧縮気体をレシーバ４へ送
る吐出側配管５の途中に分岐配管６を接続して、該分岐
配管６に排気のための放風弁（排気弁）７を設け、更
に、該分岐配管６以降の吐出側配管５の途中に逆止弁８
を設けた構成において、レシーバ４内の気体の圧力、す
なわち、負荷側となる工場での使用量と圧縮機の吐出量
とのバランス状況によってきまる吐出圧力を検出する圧
力伝送器９と、該圧力伝送器９からの信号を測定入力と
して吐出圧力を一定にするように作用する定風圧調節計
（下限スイッチ付圧力指示調節計）１０と、圧縮機１の
駆動電動機へ供給する電流（又は電力）を検出する電流
（又は電力）変換器１１と、該変換器１１からの信号を
測定入力として電動機の定格をこえないように作用する
過負荷防止調節計（下限スイッチ付電流又は電力指示調
節計）１２と、該過負荷防止調節計１２からの出力信号
（調節信号）の値と上記定風圧調節計１０からの出力信
号（調節信号）の値とを比較して常に小さい方の値を基
に吸入弁３に開度位置調節信号αを送るようにしたロー
セレクタ１３とを備えた構成とし、圧縮気体の使用量が
減少してくると、図１０に動作特性曲線を示す如く、ロ
ーセレクタ１３を介しサージング領域に近くなるまで吸
入弁３を絞って定風圧制御を維持するようにし、更に電
流値（又は電力値）が下がって所定の下限値に達したこ
とを検知すると、過負荷防止調節計１２の下限スイッチ
からの制御指令で、直ちに吸入弁３を閉、放風弁７を全
開にして無負荷運転を行わせるようにしてある。図１０
において、ａは機械性能上のサージングライン、ｂはサ
ージング防止ライン、ｃは動作線、ｄは負荷点、ｅは無
負荷点を示す。又、ＳＰ１２は過負荷防止調節計１２の
電流調節目標設定値、ＳＰ１２Ｌは同じく電流下限スイ
ッチ設定値、ＳＰ１０は定風圧調節計１０の圧力調節目
標設定値、ＳＰ１０Ｌは同じく圧力下限スイッチ設定値
を示す。2. Description of the Related Art As an example, a capacity control of a conventional compressor in which no-load operation is performed to avoid surging when the usage amount becomes equal to or less than a surging limit air volume is shown in FIG. A suction valve 3 is provided in the middle of a suction-side pipe 2 for the gas sucked into the centrifugal compressor 1,
A branch pipe 6 is connected in the middle of a discharge pipe 5 for sending the compressed gas discharged from the compressor 1 to the receiver 4, and a blow-off valve (exhaust valve) 7 for exhaust is provided in the branch pipe 6. Further, a check valve 8 is provided in the middle of the discharge side pipe 5 after the branch pipe 6.
A pressure transmitter 9 for detecting the pressure of the gas in the receiver 4, that is, a discharge pressure determined by the balance between the amount used in the factory on the load side and the discharge amount of the compressor. A constant wind pressure controller (pressure indicating controller with a lower limit switch) 10 acting to make the discharge pressure constant by using a signal from the transmitter 9 as a measurement input, and a current (or electric power) supplied to a drive motor of the compressor 1. (Or power) converter 11 for detecting the load, and an overload prevention controller (current or power indicating controller with a lower limit switch) that operates so as not to exceed the rating of the motor by using a signal from the converter 11 as a measurement input. 12 and the value of the output signal (adjustment signal) from the overload prevention controller 12 and the value of the output signal (adjustment signal) from the constant wind pressure controller 10, based on the smaller value. Opening of suction valve 3 And a row selector 13 for transmitting the position adjustment signal α. When the usage of the compressed gas decreases, as shown in the operation characteristic curve in FIG. The constant air pressure control is maintained by squeezing the suction valve 3 until the current value (or the electric power value) decreases and reaches a predetermined lower limit value. When the lower limit switch of the overload prevention controller 12 is detected. With the above control command, the suction valve 3 is immediately closed and the blow-off valve 7 is fully opened to perform the no-load operation. FIG.
In a, a indicates a surging line on mechanical performance, b indicates a surging prevention line, c indicates an operation line, d indicates a load point, and e indicates a no-load point. SP12 is a current adjustment target set value of the overload prevention controller 12, SP12L is a current lower limit switch set value, SP10 is a pressure adjustment target set value of the constant wind pressure controller 10, and SP10L is a pressure lower switch set value. .
【０００３】なお、図９において、分岐配管６及び放風
弁７を設けることに代えて、二点鎖線で示す如く、圧縮
機１の出側と吸入弁３の入側との間に、バイパス弁１４
を備えたバイパス配管１５を設けて、電流値（又は電力
値）が下限値に達したときに、圧縮空気をバイパス配管
１５を通して吸入側へ戻すようにする方式もある。In FIG. 9, instead of providing the branch pipe 6 and the blow-off valve 7, a bypass is provided between the outlet side of the compressor 1 and the inlet side of the suction valve 3 as shown by a two-dot chain line. Valve 14
There is also a method in which a compressed air is returned to the suction side through the bypass pipe 15 when the current value (or the electric power value) reaches the lower limit value by providing the bypass pipe 15 provided with.
【０００４】又、図９に示す構成において、サージング
検出を流量で行う場合は、過負荷防止調節計１２の下限
スイッチからの制御指令で吸入弁３を閉、放風弁７を開
とするように制御することに代えて、図１１に示す如
く、圧縮機１の吐出側配管５内を流れる圧縮気体の流量
を流量伝送器１６で検出し、その流量値が所定の下限値
に達したときに、下限スイッチ付流量指示計１７の流量
下限スイッチからの制御指令で上記吸入弁３を閉、放風
弁７を開とするように制御することが行われている。In the configuration shown in FIG. 9, when the surging is detected by the flow rate, the suction valve 3 is closed and the blow-off valve 7 is opened by a control command from the lower limit switch of the overload prevention controller 12. 11, the flow rate of the compressed gas flowing in the discharge side pipe 5 of the compressor 1 is detected by the flow rate transmitter 16 as shown in FIG. 11, and when the flow rate value reaches a predetermined lower limit value. In addition, control is performed such that the suction valve 3 is closed and the blow-off valve 7 is opened by a control command from the flow rate lower limit switch of the flow indicator 17 with the lower limit switch.
【０００５】一方、サージング回避を、サージング限界
風量以下にならないようにしつつ、放風運転することに
より行うようにした方式もある。すなわち、図９に示す
構成において、過負荷防止調節計１２からの指令で吸入
弁３と放風弁７を開閉制御することに代えて、図１２に
示す如く、ローセレクタ１３からの指令で吸入弁３の絞
り開度を調節する絞り開度リミッタ（折線関数演算器）
１８と、同じくローセレクタ１３からの指令で放風弁７
の開度を調節する開度調節器（折線関数演算器）１９と
を設けた構成とし、予め絞り開度リミッタ１８で吸入弁
３の絞り開度をたとえば５０％に固定し、サージング限
界風量以下にならないようにした上で、圧力上昇等によ
り放風弁７を部分開としてサージング突入を防止するよ
うにしたものである。なお、図１３は図１２に示す装置
の動作特性曲線図であり、ｆは放風弁開領域、ｇは吸入
弁絞り領域を示す。[0005] On the other hand, there is also a system in which surging avoidance is performed by blowing air while keeping the surging limit air volume below the surging limit. That is, in the configuration shown in FIG. 9, instead of controlling the opening and closing of the suction valve 3 and the blow-off valve 7 by a command from the overload prevention controller 12, as shown in FIG. Throttle opening limiter for adjusting the throttle opening of valve 3 (linear function calculator)
18 and the blow-off valve 7 in response to a command from the low selector 13.
And an opening adjuster (linear function calculator) 19 for adjusting the opening of the suction valve 3. The throttle opening of the suction valve 3 is fixed to, for example, 50% by a throttle opening limiter 18 in advance, and is equal to or less than the surging limit airflow. The blowout valve 7 is partially opened due to a rise in pressure or the like to prevent surge intrusion. FIG. 13 is an operating characteristic curve diagram of the device shown in FIG. 12, where f indicates the blow-off valve open region and g indicates the suction valve throttle region.
【０００６】[0006]
【発明が解決しようとする課題】ところが、サージング
領域に近付くと直ちに無負荷運転に入れサージング回避
を行う前者の方式の場合、負荷変動の激しい一般工場等
では、サージング領域近傍の負荷に対して、定風圧調節
信号による吸入弁の絞り込み動作が早過ぎるため、本来
バランス整定できるような負荷でも電流や流量等の下限
値にすぐ達して無負荷になってしまう等、省エネルギー
の観点（放風ロスの増大）や制御弁類の寿命の点（開閉
頻度の増大）で問題が多い。However, in the case of the former method, in which no-load operation is performed immediately after approaching the surging area to avoid surging, in a general factory or the like where the load fluctuates drastically, the load near the surging area is reduced. Since the throttle operation of the suction valve by the constant wind pressure adjustment signal is too early, even if the load can be settled, the load reaches the lower limit of the current or flow rate immediately and becomes no load. Increase) and the life of control valves (increase in opening and closing frequency) is problematic.
【０００７】一方、吸入弁の絞り限界開度を固定する後
者の方式の場合、吸入する気体の温度変化により流量が
大幅に変化するため、絞り限界開度にどうしても裕度を
もたさざるを得なく、絞り込み限界に達しない時点での
放風運転となることから、やはり省エネルギーの観点
（動力ロス）で問題がある。On the other hand, in the case of the latter method in which the throttle limit opening of the suction valve is fixed, the flow rate greatly changes due to a change in the temperature of the gas to be sucked, so that the throttle limit opening must have a margin. Since it is not possible to perform the operation and the air blow operation is performed at the time when the narrowing limit is not reached, there is still a problem from the viewpoint of energy saving (power loss).
【０００８】そこで、本発明は、サージング領域近傍の
負荷でもバランス整定できるようにすると共に、吸入気
体の温度の影響も殆ど受けずに機械性能上のサージング
ラインにできるだけ接近させたサージング限界風量を確
保できるようにしようとするものである。Therefore, the present invention enables the balance to be set even with a load in the vicinity of the surging region, and secures a surging limit airflow as close as possible to the surging line on the mechanical performance without being largely affected by the temperature of the intake gas. To make it possible.
【０００９】[0009]
【課題を解決するための手段】本発明は、上記課題を解
決するために、負荷側での気体使用量の減少に伴い、気
体圧送装置の吸入側配管に設けられている吸入弁の開度
を定風圧調節信号で絞ることにより気体圧送装置の気体
吐出量を気体使用量に合わせるようにする気体圧送装置
の容量制御方法及び装置において、上記気体圧送装置の
駆動電動機へ供給する電流又は電力、あるいは、気体圧
送装置の気体吐出側での通過流量を測定し、その信号を
測定入力とする減量限界調節計によりサージング領域へ
の接近とともに出力を増大させる調節信号を演算し、該
調節信号により上記吸入弁の開度の絞りを阻止してサー
ジング限界風量以下とならないように制御する気体圧送
装置の容量制御方法及び装置とする。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, according to the present invention, as the amount of gas used on the load side decreases, the opening of a suction valve provided on a suction side pipe of a gas pumping device is increased. In the capacity control method and device of the gas pumping device that adjusts the gas discharge amount of the gas pumping device to the gas usage amount by squeezing with a constant wind pressure adjustment signal, current or power supplied to the drive motor of the gas pumping device, Alternatively, the flow rate at the gas discharge side of the gas pumping device is measured, and a control signal for increasing the output with approaching to the surging area is calculated by a weight loss limit controller using the signal as a measurement input, and the above-mentioned control signal is used to calculate the control signal. A capacity control method and apparatus for a gas pumping device for controlling the opening of an intake valve so as not to be below the surging limit air volume by preventing the throttle from opening.
【００１０】運転点がサージング領域に接近するまで
は、定風圧調節信号で吸入弁の開度が絞られる制御が行
われるが、運転点がサージング領域に接近すると、減量
限界調節計からの調節信号により吸入弁のそれ以上の絞
りが阻止されるため、サージング限界風量以下に抑えら
れる。Until the operating point approaches the surging area, the opening of the suction valve is controlled to be reduced by the constant wind pressure adjustment signal. However, when the operating point approaches the surging area, the control signal from the reduction limit controller is provided. As a result, further restricting of the suction valve is prevented, so that the surging limit airflow is suppressed to below the limit.
【００１１】又、気体の負荷側への使用量がサージング
限界風量よりも小さいときに、気体の使用量からサージ
ング限界風量を差し引いた残りの余剰分だけを放出又は
吸入側へバイパスさせるようにする場合でも、定圧領域
の拡大によって放風ロスを低減することができるように
なる。When the amount of gas used on the load side is smaller than the surging limit air flow, only the remaining surplus obtained by subtracting the surging limit air flow from the amount of gas used is discharged or bypassed to the suction side. Even in this case, the blowout loss can be reduced by expanding the constant pressure region.
【００１２】[0012]
【発明の実施の形態】以下、本発明の実施の形態を図面
を参照して説明する。Embodiments of the present invention will be described below with reference to the drawings.
【００１３】図１は本発明の実施の一形態を示すもの
で、圧縮機１に吸入される気体の吸入側配管２の途中に
吸入弁３を設け、又、圧縮機１から吐出された圧縮気体
をレシーバ４へ送る吐出側配管５の途中に放風弁７を備
えた分岐配管６を接続し、更に、該分岐配管６以降の吐
出側配管５の途中に逆止弁８を設け、且つレシーバ４で
の吐出圧力を検出する圧力伝送器９と、該圧力伝送器９
からの信号を測定入力として吐出圧力を一定にするよう
に作用する定風圧調節計１０と、圧縮機１の電動機へ供
給する電流（又は電力）を検出する電流（又は電力）変
換器１１と、該変換器１１からの信号を測定入力として
電動機の定格をこえないように作用する過負荷防止調節
計（指示調節計）１２と、該過負荷防止調節計１２から
の出力信号（調節信号）の値と上記定風圧調節計１０か
らの出力信号（調節信号）の値とを比較して常に小さい
方の値を基に吸入弁３に開度位置調節信号αを送るよう
にしたローセレクタ１３とを備えた構成を有する圧縮機
の容量制御装置において、レシーバ４内の気体の圧力に
応じて図２に示す動作特性曲線の機械性能上のサージン
グラインａに平行に必要最小の余裕をみたサージング防
止ラインｂを設定するようにした比率変換器２０と、電
流（又は電力）変換器１１からの信号を測定入力とする
ようにし且つ上記比率変換器２０による設定値としての
サージング防止ラインｂに接近するにつれてその出力信
号（調節信号）を増大させるようにした減量限界調節計
としての電流（又は電力）指示調節計２１と、該電流指
示調節計２１の出力信号（調節信号）βと上記ローセレ
クタ１３を介し送られる調節信号αとを比較して常に大
きい側の信号を優先して出力するようにしたハイセレク
タ２２とを備え、該ハイセレクタ２２を介して出力され
た調節信号βによってサージング限界風量以下にならな
いように吸入弁３の絞り開度を制御できるようにする。FIG. 1 shows an embodiment of the present invention, in which a suction valve 3 is provided in the middle of a suction side pipe 2 for a gas to be sucked into a compressor 1, and a compressor discharged from the compressor 1 is provided. A branch pipe 6 having a blow-off valve 7 is connected in the middle of the discharge pipe 5 for sending gas to the receiver 4, and a check valve 8 is further provided in the discharge pipe 5 after the branch pipe 6, and A pressure transmitter 9 for detecting a discharge pressure at the receiver 4;
A constant wind pressure controller 10 acting to make the discharge pressure constant using the signal from the compressor as a measurement input, a current (or power) converter 11 for detecting a current (or power) supplied to the electric motor of the compressor 1, A signal from the converter 11 is used as a measurement input and an overload prevention controller (indicating controller) 12 acting so as not to exceed the rating of the motor, and an output signal (adjustment signal) from the overload prevention controller 12 are output. A low selector 13 which compares the value with the value of the output signal (control signal) from the constant wind pressure controller 10 and sends the opening position control signal α to the suction valve 3 based on the smaller value at all times. In the capacity control device for a compressor having a configuration including: a surging prevention device which has a minimum necessary margin parallel to the surging line a on the mechanical performance of the operating characteristic curve shown in FIG. 2 according to the pressure of the gas in the receiver 4. Set line b The ratio converter 20 and the signal from the current (or power) converter 11 are used as a measurement input, and the output signal thereof approaches the surging prevention line b as a set value by the ratio converter 20. The current (or power) indicating controller 21 as a reduction limit controller for increasing the (control signal), an output signal (adjustment signal) β of the current indicating controller 21 and the low selector 13 are sent. A high selector 22 which always compares the adjustment signal α with the larger signal and outputs the higher priority signal, and the adjustment signal β output via the high selector 22 prevents the surging limit air volume from being reduced below the surging limit air volume. Thus, the opening degree of the throttle of the suction valve 3 can be controlled.
【００１４】なお、図２において、ＳＰ２１は電流指示
調節計２１の電流調節目標設定値、ＳＰ１０Ｈは定風圧
調節計１０の圧力上限スイッチ設定値を示し、他は図１
０に示したものと同じである。In FIG. 2, SP21 indicates a current adjustment target set value of the current indicating controller 21, SP10H indicates a pressure upper limit switch set value of the constant wind pressure controller 10, and the others are those of FIG.
It is the same as that shown in FIG.
【００１５】今、圧縮気体の使用量が減少してくると、
ローセレクタ１３にて選択された調節信号αにより、圧
力が一定に保たれるように吸入弁３が徐々に閉じられ、
図２に示す動作曲線Ｃの如く、その運転点が気体使用量
に一致するように移動調節させられる。この際、減量限
界調節計としての電流指示調節計２１の出力信号βとロ
ーセレクタ１３を介し送られた調節信号αとは、ハイセ
レクタ２２によってその大小が連続的に比較されている
が、電流指示調節計２１の出力信号βは、運転点がサー
ジング防止ラインｂに接近するにつれて増大するように
なっているので、この時点ではローセレクタ１３を介し
送られた調節信号αが選択されて吸入弁３の開度が制御
されることになる。Now, as the amount of the compressed gas used decreases,
With the adjustment signal α selected by the low selector 13, the suction valve 3 is gradually closed so that the pressure is kept constant,
As shown by an operation curve C shown in FIG. 2, the movement is adjusted so that the operating point coincides with the gas usage. At this time, the magnitude of the output signal β of the current indicating controller 21 as the weight reduction controller and the adjustment signal α sent through the low selector 13 are continuously compared by the high selector 22. Since the output signal β of the indicating controller 21 increases as the operating point approaches the surging prevention line b, the adjustment signal α sent via the low selector 13 is selected at this time, and the suction valve 3 is controlled.
【００１６】上記において、圧縮気体の使用量が更に減
少して行くと、繰り返し行われる上記調節操作により、
設定されている吐出圧一定線（圧力調節目標設定値ＳＰ
１０）上で運転点がサージング防止ラインｂに接近して
くることになる。このサージング接近に伴い電流指示調
節計２１の出力信号βが増大し、調節信号αよりも大き
くなると、ハイセレクタ２２により電流指示調節計２１
の出力信号βが選択されるため、吸入弁３は、調節信号
αによる絞り制御が阻止され、電流指示調節計２１の出
力信号βによって制御されることになる。この際、電流
指示調節計２１はサージング防止ラインｂ上に運転点を
留めるように作動するため、サージング限界風量以下に
はならない。このことから、圧縮気体の使用量が更に減
少しても、サージング防止ラインｂに沿って圧力が上昇
することになる。更に、圧力が定風圧調節計１０の圧力
上限スイッチ設定値のＳＰ１０Ｈまで上昇したところで
圧力上限スイッチからの制御指令で吸入弁３を閉、放風
弁７を開にして無負荷運転とするようにする。[0016] In the above, when the usage of the compressed gas further decreases, the above-mentioned adjustment operation is repeatedly performed,
Set discharge pressure constant line (pressure adjustment target set value SP
10) Above, the operating point approaches the surging prevention line b. When the output signal β of the current indicating controller 21 increases with the approach of the surging and becomes larger than the adjusting signal α, the current indicating controller 21 is controlled by the high selector 22.
Is selected, the throttle control of the suction valve 3 by the adjustment signal α is blocked, and the suction valve 3 is controlled by the output signal β of the current indicating controller 21. At this time, since the current indicating controller 21 operates so as to keep the operating point on the surging prevention line b, the airflow does not fall below the surging limit airflow. From this, even if the usage of the compressed gas further decreases, the pressure increases along the surging prevention line b. Further, when the pressure rises to SP10H of the pressure upper limit switch set value of the constant wind pressure controller 10, the suction valve 3 is closed and the blow-off valve 7 is opened by a control command from the pressure upper limit switch to perform a no-load operation. I do.
【００１７】これにより、サージング領域近傍でもバラ
ンス整定できるようになり、吸入気体温度の影響も殆ど
受けずに機械性能上のサージングラインにできるだけ接
近させたサージング限界風量を確保することができる。As a result, the balance can be set even in the vicinity of the surging area, and the surging limit airflow as close as possible to the surging line on the mechanical performance can be secured without being affected by the temperature of the intake gas.
【００１８】次に、図３は本発明の実施の他の形態を示
すもので、サージング検出を流量で行う場合について示
す。すなわち、図１に示したと同様な構成において、電
流（又は電力）変換器１１からの信号を測定入力とする
ようにした電流（又は電力）指示調節計２１を減量限界
調節計として用いることに代えて、圧縮機１の吐出側配
管５に設けた流量伝送器１６からの信号を測定入力とす
るようにした流量指示調節計２３を減量限界調節計とし
て用いたものである。Next, FIG. 3 shows another embodiment of the present invention, in which surging detection is performed by a flow rate. That is, in the configuration similar to that shown in FIG. 1, instead of using the current (or power) indicating controller 21 in which the signal from the current (or power) converter 11 is used as the measurement input, as the weight reduction limit controller, Further, a flow rate indicating controller 23 in which a signal from a flow rate transmitter 16 provided in a discharge side pipe 5 of the compressor 1 is used as a measurement input is used as a reduction limit controller.
【００１９】図３に示すような構成としても、図１に示
したものと同様な作用効果を発揮することができる。The configuration shown in FIG. 3 can provide the same operation and effect as those shown in FIG.
【００２０】次いで、図４は本発明の実施の更に他の形
態を示すもので、使用量がサージング限界風量以下とな
って圧力上昇時にサージング回避を放風運転とする場合
の例であり、図１に示したと同様な構成において、圧力
上限スイッチのかわりに圧力伝送器９の信号を測定入力
とする放風定圧調節計としての圧力指示調節計２４を設
け、図５に示す如く、定風圧調節計１０の設定値ＳＰ１
０から一定圧力差をもったところに、該圧力指示調節計
２４の設定値ＳＰ２４を設けて、圧力指示調節計２４か
らの出力信号（調節信号）で放風弁７の開度を制御でき
るようにしたものである。Next, FIG. 4 shows still another embodiment of the present invention, in which the surging avoidance operation is performed when the usage amount falls below the surging limit air volume and the pressure rises. In the same configuration as shown in FIG. 1, instead of the pressure upper limit switch, there is provided a pressure indicating controller 24 as a blower constant pressure controller which receives a signal of the pressure transmitter 9 as a measurement input, and as shown in FIG. A total of 10 setting values SP1
A set value SP24 of the pressure indicating controller 24 is provided at a position having a certain pressure difference from 0, so that the opening degree of the blow-off valve 7 can be controlled by an output signal (adjustment signal) from the pressure indicating controller 24. It was made.
【００２１】図４に示すようにすると、圧力上昇時のサ
ージング回避が放風運転となり、気体の工場での使用量
がサージング限界風量よりも小さくなると、工場使用量
からサージング限界風量を差し引いた残りの余剰分だけ
を、放風弁７で逃がすことができてサージング限界風量
が機械性能上のサージングラインに接近しているため放
風ロスを減少させることができる。As shown in FIG. 4, surging avoidance at the time of pressure rise is a blow-off operation. When the amount of gas used in the factory becomes smaller than the surging limit air volume, the surging limit air volume is subtracted from the factory usage amount. Can be released by the blow-off valve 7 and the surging limit air flow is close to the surging line for mechanical performance, so that the blow-off loss can be reduced.
【００２２】又、図６は本発明の実施の更に別の形態を
示すもので、サージング検出を電流（又は電力）で行う
図４の実施の形態を変化させて、サージング検出を流量
で行うようにしたものである。すなわち、図３に示した
と同様な構成において、圧力伝送器９の信号を測定入力
とする放風定圧調節計としての圧力指示調節計２４を図
４の場合と同様に設けて、該圧力指示調節計２４からの
出力信号（調節信号）で放風弁７の開度を制御できるよ
うにしたものである。FIG. 6 shows still another embodiment of the present invention. The embodiment shown in FIG. 4 in which surging detection is performed by current (or power) is changed so that surging detection is performed by flow rate. It was made. That is, in a configuration similar to that shown in FIG. 3, a pressure indicating controller 24 as a blower constant pressure controller using the signal of the pressure transmitter 9 as a measurement input is provided in the same manner as in FIG. The opening degree of the blow-off valve 7 can be controlled by an output signal (adjustment signal) from the total 24.
【００２３】図６に示すようにしても、図４の実施の形
態の場合と同様な作用効果が奏し得られる。The same operation and effect as those of the embodiment of FIG. 4 can be obtained by the arrangement shown in FIG.
【００２４】因に、図７は使用量がサージング限界風量
以下となって圧力上昇したときのサージング回避を無負
荷運転とした場合の図１〜図３で示した本発明と図９〜
図１１で示した従来方式とを動力性能比較するものであ
り、又、図８は使用量がサージング限界風量以下となっ
て圧力上昇したときのサージング回避を放風運転とした
場合の図４〜図６で示した本発明と図１２、図１３で示
した従来方式とを動力性能比較するものである。図７及
び図８中、ｈは定格点ｉから機械性能上の減量限界点ｊ
までの吸入絞り動作線、ｋは理想線、ｌは本発明による
場合の動作線、ｍは従来方式による場合の動作線を示
す。FIG. 7 shows the present invention shown in FIGS. 1 to 3 and FIGS. 9 to 9 when the no-load operation is performed to avoid surging when the pressure rises due to the amount of use being equal to or less than the surging limit air volume.
FIG. 8 compares the power performance with the conventional system shown in FIG. 11, and FIG. 8 shows the case where the surging is avoided when the amount of use falls below the surging limit air volume and the pressure rises. The power performance of the present invention shown in FIG. 6 is compared with that of the conventional system shown in FIGS. In FIGS. 7 and 8, h is the limiting point j on the machine performance from the rated point i.
, K indicates an ideal line, l indicates an operation line according to the present invention, and m indicates an operation line according to a conventional method.
【００２５】図７及び図８から明らかなように、本発明
による動作線ｌの方が従来方式による動作線ｍよりも理
想線ｋに近付いており、サージング限界点での実運用運
転が可能となることがわかる。すなわち、動力低減を伴
う定圧領域の拡大を図ることができる（□印→○印）と
共に、放風ロスの低減を図ることができ（斜線部）、特
に、サージング回避を無負荷運転で行う場合は、吸入
弁、放風弁の開閉切り替わり時に発生する放風ロスをよ
り低減できることになる。更に、サージング領域近傍で
のバランス整定のチャンスが多く生まれることになり、
弁の開閉頻度を低減できて弁の寿命を延ばすことができ
るようになる。As is apparent from FIGS. 7 and 8, the operation line 1 according to the present invention is closer to the ideal line k than the operation line m according to the conventional method, and the actual operation at the surging limit point is possible. It turns out that it becomes. In other words, it is possible to expand the constant pressure region with a reduction in power (square mark → circle mark) and to reduce the blow-off loss (shaded area), especially when surging is avoided by no-load operation. Thus, it is possible to further reduce the blow-off loss generated when the intake valve and the blow-off valve are switched between open and closed. Furthermore, there will be many chances of balance setting near the surging area,
The frequency of opening and closing the valve can be reduced, and the life of the valve can be extended.
【００２６】なお、上記各実施の形態では、圧縮機１の
吐出側配管５に放風弁７を備えた分岐配管６が接続して
ある場合について示したが、図９や図１１等において二
点鎖線で示したのと同様に、放風弁７を備えた分岐配管
６に代えて、バイパス弁１４を備えたバイパス配管１５
が組み込まれているライン構成についても適用できるこ
と、又、実施の形態では、減量限界調節計としての電流
指示調節計２１、流量指示調節計２３とは別に比率変換
器２０を独立させて設けた場合を示したが、比率変換器
２０の機能を組み込ませた減量限界調節計を用いるよう
にしてもよいこと、その他本発明の要旨を逸脱しない範
囲内において種々変更を加え得ることは勿論である。In each of the above embodiments, the case where the branch pipe 6 provided with the blow-off valve 7 is connected to the discharge pipe 5 of the compressor 1 is shown. In the same manner as indicated by the dotted line, a bypass pipe 15 having a bypass valve 14 is replaced by a bypass pipe 15 having a bypass valve 14.
Can be applied to the line configuration in which the ratio converter 20 is provided independently of the current indicating controller 21 and the flow rate indicating controller 23 as the reduction limit controller in the embodiment. However, it goes without saying that a weight loss limit controller incorporating the function of the ratio converter 20 may be used, and various other changes may be made without departing from the gist of the present invention.
【００２７】[0027]
【発明の効果】以上述べた如く、本発明によれば、負荷
側での気体使用量の減少に伴い、気体圧送装置の吸入側
配管に設けられている吸入弁の開度を定風圧調節信号で
絞ることにより気体圧送装置の気体吐出量を気体使用量
に合わせるようにする気体圧送装置の容量制御方法及び
装置において、上記気体圧送装置の駆動電動機へ供給す
る電流又は電力、あるいは、気体圧送装置の気体吐出側
での通過流量を測定し、その信号を測定入力とする減量
限界調節計によりサージング領域への接近とともに出力
を増大させる調節信号を演算し、該調節信号により上記
吸入弁の開度の絞りを阻止してサージング限界風量以下
とならないように制御する気体圧送装置の容量制御方法
及び装置としてあるので、機械性能上のサージングライ
ンにできるだけ接近させた動力低減を伴う定圧領域の拡
大を図ることができて、サージング限界点での実運用運
転が可能となると共に、サージング領域近傍でのバラン
ス整定のチャンスが多く生まれることになって、弁の開
閉頻度を低減できて、弁の寿命の延命化を図ることがで
き、又、気体の負荷側への使用量がサージング限界風量
よりも小さいときに、気体の使用量からサージング限界
風量を差し引いた残りの余剰分だけを放出又は吸入側へ
バイパスさせるようにする場合でも、定圧領域の拡大に
よって放風ロスを低減することができる、等の優れた効
果を発揮する。As described above, according to the present invention, as the amount of gas used on the load side decreases, the opening of the suction valve provided on the suction side pipe of the gas pumping device is controlled by the constant wind pressure control signal. In the capacity control method and apparatus of the gas pumping apparatus for adjusting the gas discharge amount of the gas pumping apparatus to the gas usage amount by squeezing, the current or power supplied to the drive motor of the gas pumping apparatus or the gas pumping apparatus The flow rate on the gas discharge side is measured, and a control signal for increasing the output with approaching the surging area is calculated by a weight loss limit controller using the signal as a measurement input, and the opening degree of the suction valve is calculated based on the control signal. The method and apparatus for controlling the capacity of the gas pumping device that prevents the throttle from restricting the air volume so that the air volume does not fall below the surging limit air volume are as close as possible to the surging line in terms of mechanical performance. As a result, the constant pressure region can be expanded with the reduced power, which enables actual operation at the surging limit point, and also provides many opportunities for balance setting near the surging region, and the valve The frequency of opening and closing can be reduced, the life of the valve can be prolonged, and the surging limit airflow is subtracted from the gas usage when the gas usage on the load side is smaller than the surging limit airflow. Even in the case where only the remaining surplus is bypassed to the discharge or suction side, excellent effects such as reduction of the blow-off loss by expansion of the constant pressure region are exhibited.
【図１】本発明の気体圧送装置の容量制御装置の実施の
一形態を示す概略図である。FIG. 1 is a schematic view showing one embodiment of a capacity control device of a gas pressure feeding device of the present invention.
【図２】図１に示す装置による場合の動作特性曲線図で
ある。FIG. 2 is an operation characteristic curve diagram in the case of using the device shown in FIG.
【図３】本発明の実施の他の形態を示す概略図である。FIG. 3 is a schematic view showing another embodiment of the present invention.
【図４】本発明の実施の更に他の形態を示す概略図であ
る。FIG. 4 is a schematic diagram showing still another embodiment of the present invention.
【図５】図４に示す装置による場合の動作特性曲線図で
ある。FIG. 5 is an operating characteristic curve diagram for the device shown in FIG.
【図６】本発明の実施の更に別の形態を示す概略図であ
る。FIG. 6 is a schematic view showing still another embodiment of the present invention.
【図７】サージング回避を無負荷運転とした場合の本発
明と従来方式とを比較する特性曲線図である。FIG. 7 is a characteristic curve diagram comparing the present invention and a conventional system when surging avoidance is set to no-load operation.
【図８】サージング回避を放風運転とした場合の本発明
と従来方式とを比較する特性曲線図である。FIG. 8 is a characteristic curve diagram comparing the present invention and the conventional system when the surging avoidance is the blow-off operation.
【図９】従来の圧縮機の容量制御装置の一例を示す概略
図である。FIG. 9 is a schematic diagram showing an example of a conventional compressor capacity control device.
【図１０】図９に示す装置による動作特性曲線図であ
る。10 is an operation characteristic curve diagram of the device shown in FIG.
【図１１】従来の圧縮機の容量制御装置の他の例を示す
概略図である。FIG. 11 is a schematic diagram showing another example of a conventional capacity control device for a compressor.
【図１２】従来の圧縮機の容量制御装置の更に他の例を
示す概略図である。FIG. 12 is a schematic diagram showing still another example of a conventional capacity control device for a compressor.
【図１３】図１２に示す装置の動作特性曲線図である。13 is an operating characteristic curve diagram of the device shown in FIG.
１ 圧縮機（気体圧送装置） ２ 吸入側配管 ３ 吸入弁 ５ 吐出側配管 ７ 放風弁 １０ 定風圧調節計 ２１ 電流指示調節計（減量限界調節計） ２２ ハイセレクタ ２３ 流量指示調節計（減量限界調節計） ２４ 圧力指示調節計（放風定圧調節計） DESCRIPTION OF SYMBOLS 1 Compressor (gas pressure feeder) 2 Suction-side piping 3 Suction valve 5 Discharge-side piping 7 Blow-off valve 10 Constant wind pressure controller 21 Current indicator controller (reduction limit controller) 22 High selector 23 Flow indicator controller (reduction limit) Controller) 24 Pressure indicating controller (Blow-off constant pressure controller)
───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3H021 AA01 BA05 BA12 BA20 BA23 BA25 CA01 CA03 CA07 CA10 DA10 DA14 DA15 EA07 EA19 3H045 AA06 AA12 AA25 AA26 BA19 BA41 CA02 CA06 CA21 CA29 DA13 DA18 DA19 EA34 EA45 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3H021 AA01 BA05 BA12 BA20 BA23 BA25 CA01 CA03 CA07 CA10 DA10 DA14 DA15 EA07 EA19 3H045 AA06 AA12 AA25 AA26 BA19 BA41 CA02 CA06 CA21 CA29 DA13 DA18 DA19 EA34 EA45
Claims (4)
体圧送装置の吸入側配管に設けられている吸入弁の開度
を定風圧調節信号で絞ることにより気体圧送装置の気体
吐出量を気体使用量に合わせるようにする気体圧送装置
の容量制御方法において、上記気体圧送装置の駆動電動
機へ供給する電流又は電力、あるいは、気体圧送装置の
気体吐出側での通過流量を測定し、その信号を測定入力
とする減量限界調節計によりサージング領域への接近と
ともに出力を増大させる調節信号を演算し、該調節信号
により上記吸入弁の開度の絞りを阻止してサージング限
界風量以下とならないように制御することを特徴とする
気体圧送装置の容量制御方法。In accordance with a decrease in the amount of gas used on the load side, the opening of a suction valve provided on a suction side pipe of the gas pumping device is reduced by a constant air pressure control signal to thereby reduce the gas discharge amount of the gas pumping device. In the capacity control method of the gas pumping device to match the amount of gas used, the current or power to be supplied to the drive motor of the gas pumping device, or, measure the passing flow rate on the gas discharge side of the gas pumping device, An adjustment signal for increasing the output with approaching the surging area is calculated by a weight reduction controller using the signal as a measurement input, and the adjustment signal is used to prevent the opening of the suction valve from being throttled so that the air volume does not fall below the surging limit airflow. A method for controlling the capacity of a gas pumping device, characterized in that:
界風量よりも小さいときに、気体の使用量からサージン
グ限界風量を差し引いた残りの余剰分だけを放出又は吸
入側へバイパスさせるようにする請求項１記載の気体圧
送装置の容量制御方法。2. When the amount of gas used on the load side is smaller than the surging limit airflow, only the surplus obtained by subtracting the surging limit airflow from the gas usage is bypassed to the discharge or suction side. The method for controlling the capacity of a gas pumping device according to claim 1.
体圧送装置の吸入側配管に設けられている吸入弁の開度
を定風圧調節信号で絞ることにより気体圧送装置の気体
吐出量を気体使用量に合わせるようにする気体圧送装置
の容量制御装置において、上記気体圧送装置の駆動電動
機へ供給する電流又は電力、あるいは、気体圧送装置の
気体吐出側での通過流量を測定入力とし且つサージング
領域へ接近するにつれてその出力を増大させるようにし
た減量限界調節計と、該減量限界調節計の出力信号と上
記定風圧調節信号とを比較して大きい方を優先して出力
するようにしたハイセレクタとを備え、該ハイセレクタ
を介して出力された信号により、サージング限界風量以
下にならないように上記吸入弁の開度を制御できるよう
にした構成を有することを特徴とする気体圧送装置の容
量制御装置。3. The gas discharge amount of the gas pumping device is reduced by reducing the opening of a suction valve provided on the suction side pipe of the gas pumping device with a constant air pressure control signal in accordance with a decrease in the amount of gas used on the load side. In the capacity control device of the gas pumping device that adjusts to the gas usage, the current or power supplied to the drive motor of the gas pumping device, or the passing flow rate on the gas discharge side of the gas pumping device as a measurement input and A weight loss limit controller whose output is increased as it approaches the surging area, and an output signal of the weight loss limit controller is compared with the constant wind pressure control signal to output a larger one with priority. A high selector, and a signal output through the high selector can control the opening of the suction valve so as not to be below the surging limit airflow. A capacity control device for a gas pumping device.
用の設定値よりも高い所要の設定値をもった放風定圧調
節計を備え、該放風定圧調節によって、気体の使用量か
らサージング限界風量を差し引いた残りの余剰分だけ
を、放出又は吸入側へバイパスさせるようにした請求項
３記載の気体圧送装置の容量制御装置。4. An air discharge constant pressure controller having a discharge pressure as a measurement input and having a required set value higher than a set value for constant air pressure adjustment, and surging from a gas consumption by said air discharge constant pressure adjustment. 4. The capacity control device for a gas pumping device according to claim 3, wherein only the surplus remaining after subtracting the limit air volume is bypassed to the discharge or suction side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25488699A JP4487339B2 (en) | 1999-09-08 | 1999-09-08 | Capacity control method and apparatus for gas pumping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25488699A JP4487339B2 (en) | 1999-09-08 | 1999-09-08 | Capacity control method and apparatus for gas pumping device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001082380A true JP2001082380A (en) | 2001-03-27 |
| JP4487339B2 JP4487339B2 (en) | 2010-06-23 |
Family
ID=17271214
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25488699A Expired - Fee Related JP4487339B2 (en) | 1999-09-08 | 1999-09-08 | Capacity control method and apparatus for gas pumping device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4487339B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007023821A (en) * | 2005-07-13 | 2007-02-01 | Yamatake Corp | Controller, program, and compressor system |
| WO2013051559A1 (en) * | 2011-10-03 | 2013-04-11 | 株式会社Ihi | Centrifugal compressor machine and method for preventing surge therein |
| US10514029B2 (en) * | 2015-02-16 | 2019-12-24 | Tti (Macao Commercial Offshore) Limited | Air inlet control for air compressor |
| CN114876846A (en) * | 2022-06-01 | 2022-08-09 | 西安陕鼓动力股份有限公司 | Full-automatic constant pressure control system and control method for centrifugal compressor unit |
| WO2023131186A1 (en) * | 2022-01-10 | 2023-07-13 | 重庆美的通用制冷设备有限公司 | Surge detection method and apparatus for compressor, and electronic device |
-
1999
- 1999-09-08 JP JP25488699A patent/JP4487339B2/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007023821A (en) * | 2005-07-13 | 2007-02-01 | Yamatake Corp | Controller, program, and compressor system |
| WO2013051559A1 (en) * | 2011-10-03 | 2013-04-11 | 株式会社Ihi | Centrifugal compressor machine and method for preventing surge therein |
| JP2013079586A (en) * | 2011-10-03 | 2013-05-02 | Ihi Corp | Centrifugal compression facility and method for preventing surging therein |
| US10202980B2 (en) | 2011-10-03 | 2019-02-12 | Ihi Rotating Machinery Engineering Co., Ltd. | Centrifugal compressor apparatus and method for preventing surge therein |
| US10514029B2 (en) * | 2015-02-16 | 2019-12-24 | Tti (Macao Commercial Offshore) Limited | Air inlet control for air compressor |
| WO2023131186A1 (en) * | 2022-01-10 | 2023-07-13 | 重庆美的通用制冷设备有限公司 | Surge detection method and apparatus for compressor, and electronic device |
| CN114876846A (en) * | 2022-06-01 | 2022-08-09 | 西安陕鼓动力股份有限公司 | Full-automatic constant pressure control system and control method for centrifugal compressor unit |
| CN114876846B (en) * | 2022-06-01 | 2024-03-26 | 西安陕鼓动力股份有限公司 | Full-automatic constant-pressure control system and control method for centrifugal compressor unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4487339B2 (en) | 2010-06-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7922457B2 (en) | System and method for controlling a variable speed compressor during stopping | |
| KR100726203B1 (en) | Method for controlling a compressed air installation comprising several compressors, control box applied thereby and compressed air installation applying this method | |
| JP5465673B2 (en) | Control system | |
| EP0398436B1 (en) | Compressor control system to improve turndown and reduce incidents of surging | |
| JP3741014B2 (en) | Control method and compressor system for a plurality of compressors | |
| AU2007347705B2 (en) | Anti-bogdown control system for turbine/compressor systems | |
| JP4345672B2 (en) | Turbo compressor and operation method thereof | |
| EP2212631B1 (en) | Refrigerating system and method for controlling the same | |
| US6293766B1 (en) | Process for operating a compressor with a downstream user, and unit operating according to this process | |
| AU2011242422B2 (en) | Method for controlling a compressor | |
| JP2001082380A (en) | Method and device for controlling volume of gas force feeding device | |
| US4976588A (en) | Compressor control system to improve turndown and reduce incidents of surging | |
| JP3384894B2 (en) | Turbo compressor capacity control method | |
| JP2508695B2 (en) | Method and apparatus for operating a plurality of compressors in parallel | |
| JP6612412B1 (en) | Compressor | |
| JP2004316462A (en) | Method and device for controlling displacement of centrifugal compressor | |
| JPH11117894A (en) | Gas compression facility and its operating method | |
| JP2757426B2 (en) | Operation control method of centrifugal compressor | |
| JP3368480B2 (en) | Compressor control method and device | |
| JPH02123299A (en) | Controller for centrifugal compressor | |
| JP2655431B2 (en) | Constant flow control device for centrifugal compressor | |
| JP2774433B2 (en) | Centrifugal compressor capacity control device | |
| JPH04136498A (en) | Capacity control device of centrifugal compressor | |
| WO2017138481A1 (en) | Compressor surge generation prevention device and compressor system | |
| JPH0746797Y2 (en) | Compressed air manufacturing equipment |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20060824 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20090803 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20091208 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20100204 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20100309 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20100322 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130409 Year of fee payment: 3 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 4487339 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130409 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20140409 Year of fee payment: 4 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313111 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| LAPS | Cancellation because of no payment of annual fees |