JPS6053686A - Method of high efficiently controlling compressor - Google Patents
Method of high efficiently controlling compressorInfo
- Publication number
- JPS6053686A JPS6053686A JP16046383A JP16046383A JPS6053686A JP S6053686 A JPS6053686 A JP S6053686A JP 16046383 A JP16046383 A JP 16046383A JP 16046383 A JP16046383 A JP 16046383A JP S6053686 A JPS6053686 A JP S6053686A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- terminal
- signal
- discharge pressure
- discharge
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、工場の動力源として、数多く使用されている
、圧縮機群の省エネルギ運転方法の一つとし、負荷流量
の使用量に応じて、圧縮機の吐出圧力ｋ １ｌｉｌｌ
ｆａｌｌする方法に関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention is one of the energy-saving operation methods for a group of compressors, which are widely used as a power source in factories, and which , compressor discharge pressure k 1lill
Concerning how to fall.
圧縮機の負荷風昂：Ｃ対する吐出ＬＥ力お・よび軸動力
将性は、第１図に示すように、吐出圧力Ｐに１、負荷風
相の上昇とともに減少し、一方、４ｑ１１動力りは９荷
風量の上昇とともに上昇する。従つ−Ｃ１吐出圧力Ｐを
低く押える事ができると、負荷風量を多くとれ、軸動力
りを低く押える事が出来る。As shown in Fig. 1, the compressor's discharge LE force and shaft power characteristics with respect to the load wind phase C decrease by 1 as the discharge pressure P increases, and as the load wind phase increases, while the 4q11 power decreases as the load wind phase increases. 9 It increases with the increase in air flow rate. Therefore, if the -C1 discharge pressure P can be kept low, the load air volume can be increased and the shaft power can be kept low.
従って、圧縮機を高効率運転させるには、いかに、吐出
圧力を低く押える手ができるかにあると言える。Therefore, it can be said that in order to operate the compressor with high efficiency, it is possible to keep the discharge pressure low.
従来の圧縮機の制御方法を第３図に示す。工場の動力源
である圧縮戦群は、空力機器が多岐にわたっているため
、空力機器等の末端圧力を低側１するには、圧力検出器
が多量に必要で、寵１ｊ朗］が後難になる等の不具会が
あるため、吐出圧力ー矩１ｉｉｌ ［＋が一般的である
。吐出圧力一定？ｔｉｌｉ 釣力式は、第２図に示すよ
’＞Ｋ、末端負荷である空力機器りの最低保証圧力ＰＬ
と、最大使用風隼Ｑ５Ｔ時の配管損失Ｐ）！全加算した
圧力 Ｐ Ｔ ＝ Ｐ ｒ、 十Ｐ Ｈで吐出圧力を一
定と成るＪ：うに制御する墨により、末端負荷の圧力を
、最低保証圧力以上となるように制御する。第３図の一
般的な圧縮機群における吐出ＬＥ力と、末端圧力の等価
モデルにおける圧力と負荷ｊ載量の特性は、第４図中、
Ｐｏ１とＩ’ＬＩに示すように成る。すなわち、吐出圧
力Ｐｏｌを一定に開側ｊすると、負荷風ｍｌ゛の上昇と
ともに配管損失が大きくなり末端圧力ＰＬＩは低下する
。A conventional compressor control method is shown in FIG. The compression battle group, which is the power source of the factory, has a wide variety of aerodynamic equipment, so in order to lower the end pressure of the aerodynamic equipment, etc., a large number of pressure detectors are required, and this is a problem. Since there are some problems such as, discharge pressure - 1iil [+] is generally used. Is the discharge pressure constant? tili The fishing force formula is shown in Figure 2, where K is the minimum guaranteed pressure PL of the aerodynamic equipment that is the terminal load.
And piping loss P at the maximum operating wind Hayabusa Q5T)! The total added pressure P T = P r, and the discharge pressure becomes constant at 10 P H. By controlling the discharge pressure as described above, the pressure of the terminal load is controlled to be equal to or higher than the minimum guaranteed pressure. The characteristics of pressure and load j in the equivalent model of discharge LE force and terminal pressure in a general compressor group shown in Fig. 3 are shown in Fig. 4.
The results are as shown in Po1 and I'LI. That is, when the discharge pressure Pol is kept constant on the open side, as the load wind ml' increases, the piping loss increases and the terminal pressure PLI decreases.
１〕Ｌ：末端圧力
Ｐｏ：吐出圧力
Ｒ＝配管損失
Ｑ 、負荷風量
とすると、
ＰＬ二Ｐ ｏ −１（、・Ｑ、２−（１１にて示さ消５
、負荷風量により末端Ｕ〔力ＰＬが変化することがわか
る。1] L: Terminal pressure Po: Discharge pressure R = piping loss Q, load air volume, then PL2P o -1(, ・Q, 2-(not shown in 11)
, it can be seen that the terminal U [force PL] changes depending on the load air volume.
第４図により明らかなように、吐出圧力ー軍制菌によれ
ば末端圧力は、負荷風景により変化し２同図中斜線のよ
う々無駄な高い圧力を送っていることになる。すなわち
、商い圧力で送ることにより、無駄な動力及びエイ・ル
キーを消費しているう〔発明の目的〕
本発明は、末端に検出器を設置することなく良好な省エ
イ・ルキ運転を笑現できるｉ！ＩＩ釧方法全方法するＫ
ある。As is clear from FIG. 4, according to the discharge pressure-force control method, the terminal pressure changes depending on the load situation, resulting in unnecessary high pressure being sent as shown by the diagonal lines in the figure. In other words, by sending at commercial pressure, unnecessary power and energy consumption are consumed. [Object of the Invention] The present invention realizes good energy saving and energy saving operation without installing a detector at the end. I can do it! II All methods K
be.
本発明の概要を、第５図の流量を検出して吐出圧力の設
定値を変化させる場合と、第６図の圧縮機の運転台数を
カウントして吐出ＥＥ力の設定１゛「１を変化させる場
合とについて説明する。The outline of the present invention is shown in Fig. 5, in which the flow rate is detected and the setting value of the discharge pressure is changed, and in Fig. 6, the discharge EE force is changed by counting the number of operating compressors. This section explains how to do this.
第５図の流量゛を検出しで、吐出圧力の割面設定１ｌＰ
Ｊを変える方式は、ｌｌ−ｒｊｌ凶中圧力イ莢出器１よ
ジ吐出圧力の信号と、流′に４計２より流かの信号を受
け、第６図に示すフロック図からなる制伊ＩＪ都３を廟
する。末端圧力設定器３３で末端圧力最低保Ｊ１１：圧
力全設定し、流量信号を自乗器３１により自乗し、比例
器３２により配管損失の係数全設定する事により、Ａ点
の信号は等測的な配賞ロスに相当する圧力設定と成る。Detect the flow rate in Figure 5 and set the discharge pressure to 1lP.
The method for changing J is to receive a signal of the discharge pressure from the sheller 1 and a signal of the discharge pressure from the sheller 1 to the flow ', and to create a control system consisting of the block diagram shown in Figure 6. Mausoleum of IJ Miyako 3. By setting the minimum terminal pressure J11: full pressure with the terminal pressure setting device 33, squaring the flow rate signal with the squarer 31, and setting the entire piping loss coefficient with the proportional device 32, the signal at point A can be made isometric. This is a pressure setting that corresponds to a loss in prize distribution.
加算器３４Ｖ（より末端圧力６ψＷ命：３３で設定され
た末端圧力の設定値とＡ点の配管ロスに相当する信号金
加’Ｉ？すると、Ｃ点の１８号は、末端圧力で最低仙踵
＋ＥＦｆ力をキープするに２襞な、らる流量時の配官ロ
ス分ケ考慮した吐出圧力の制釧設定値となる。従って、
Ｃ点の信号と第５図の検出器１の吐出圧力の信号りとに
より、圧力ー軍制ｆ卸回路３５により、下記のように圧
縮機群の発停制釧を行なう。Adder 34V (terminal pressure 6ψW): Add signal corresponding to the terminal pressure setting value set in 33 and the piping loss at point A. To maintain the +EFf force, the discharge pressure control setting value takes into account the distribution loss at the time of the flow rate.Therefore,
Based on the signal at point C and the discharge pressure signal from the detector 1 shown in FIG. 5, the pressure control circuit 35 controls the start and stop of the compressor group as described below.
Ｃく］−）；圧縮機群の１台を停止
Ｃ二り：現状維持
Ｃ＞Ｄ：圧ｍ機群の一台を始動
上記の条件は、あく寸で圧力信号のみの条件であり、そ
の他、圧縮機の故障状態及び比較判定の不感帯、効果特
等のタイマー等は圧力ー軍制師−ｊ路の中に含まれる。C]-); Stop one unit of the compressor group C2: Maintain the status quo C>D: Start one unit of the compressor group , compressor failure status, dead zone for comparative judgment, timer for special effects, etc. are included in the pressure-system-j path.
このようなロジックにより、末端圧力全考慮した吐出圧
力側斜全行なうと、吐出圧力の設定値及び末端圧力の領
は第４図中、吐出圧力の設定値Ｐ ｏ ｓのように、負
荷風量の増加とともに上昇するが末端の圧力は、ＰＬＮ
のように常Ｖこ一定と成る。According to this logic, if the discharge pressure side is completely adjusted in consideration of the terminal pressure, the set value of the discharge pressure and the area of the terminal pressure will be the same as the set value of the discharge pressure P o s in Fig. 4, and the load air volume. The pressure at the end increases as the PLN
As shown, V is always constant.
従って、従来技術の吐出圧力ー軍制仰の負荷風景の変動
特性（第４図中ＰＯＩ、ＰＬＩ）にｌ：ｌＺ較し、斜線
に相当する末端圧力の低減が得られ、大巾な省工坏ルキ
効果が得られる。Therefore, compared to the variation characteristics of the discharge pressure-military control load landscape (l:lZ) of the conventional technology (POI, PLI in Fig. 4), a reduction in the terminal pressure corresponding to the diagonal line can be obtained, and a large amount of labor can be saved. You can get the Luki effect.
上記と同様に、運転台数に応じて吐出制ｆｉＩＩＩ８：
力を補正する制菌方式を第７図に、ｎｉ：ｌ側１ブロッ
ク図を第８図にそれぞれ示す。同図中、運転台数による
流量換算回路６１により、圧縮機が運転中にＯＮ −Ｊ
、ＯＡＤ中の台数を検出し、等測的な床間全算出し、前
述茄、搦′計の場合と同様に、自乗器５１にて自乗し、
比例器５２で配管ロスに相当する圧力信号）゛を出力す
る。力１１算器５４により、設定器５３で設定をれた末
端圧力の設定値と、Ｆ点の配管ロスに相当する信号を加
算すると、Ｈ点の信号は、末端圧力で最低保証圧力をキ
ープするに必襞な、ある流量時の配管ロス分を考慮、し
た吐出圧力の割面設定値となる。圧力ー軍制阻回路５５
により、流量計設筐と同様の圧縮機群の発停制＠Ｉを行
なうと、吐出圧力の設定値及び末端圧力の仙は第４図中
、吐出圧力の設定値はＰａｙのように、運転台数の増加
とともに段階的に上昇するが、末端の圧力はＰ＋、Ｍの
ように、末端の最低保証圧力全キープするべく、ノコキ
リ波状に変化する。Similarly to the above, discharge control fiIII8:
The antibacterial system for correcting the force is shown in FIG. 7, and the block diagram of the ni:l side is shown in FIG. 8, respectively. In the same figure, a flow rate conversion circuit 61 based on the number of operating units turns ON-J while the compressor is in operation.
, detect the number of units in OAD, calculate the total isometric floor space, and square it with the squarer 51 as in the case of the above-mentioned 茄 and 搦' meter.
The proportional device 52 outputs a pressure signal corresponding to piping loss). When the force 11 calculator 54 adds the terminal pressure set value set by the setting device 53 and the signal corresponding to the piping loss at point F, the signal at point H maintains the minimum guaranteed pressure at the terminal pressure. This is the discharge pressure ratio set value that takes into account the piping loss at a certain flow rate, which is necessary for this purpose. Pressure-Military Interdiction Circuit 55
Therefore, when the compressor group start/stop control @I is performed in the same way as the flowmeter design case, the set value of discharge pressure and the value of terminal pressure are as shown in Fig. 4, and the set value of discharge pressure is as shown in Pay. As the number of units increases, the pressure increases step by step, but the pressure at the end changes in a sawtooth waveform, such as P+ and M, in order to maintain the minimum guaranteed pressure at the end.
流邦計投前時と同様、本方式でも、第４図のが［線の様
な末端圧力の低減が得られる。As with the case before the Ryuho Project, this method also achieves a reduction in terminal pressure as shown by the line in Figure 4.
本発明によれば （］）等価的に末端圧力の一軍制朝ｊが出来る。 According to the invention (]) Equivalently, a one-army system with terminal pressure can be created.
（２）吐出圧力ー軍制側ｊに比べて、吐出力の設定１１
なを低くできる。(2) Discharge pressure - Compared to military system j, discharge force setting 11
can be lowered.
（３）大巾な省エイ・ルキ効果が得られる。(3) Significant stingray-saving effect can be obtained.
第１図は圧縮機の負荷風量”と吐出圧力及び１１１Ｉ動
力科性図、第２図は配管系統の負荷風量と吐出圧力及び
配管ロスの特性図、第３図は従来の吐出圧−５り開明１
のブロック図、第４図は従来の吐１ｊ肩ｊ−−−軍制両
時と本発明の吐出制菌圧袖屯時の負荷ｊ虱邦と吐出圧力
及び末端圧力の慣性図、′Ｆ；５図はオ・′発明の流煽
゛検出器設置時の一実施例のフロック図、第６図は第５
・図の詳細ブロック図、第７図はオー発明の圧縮機台数
全カウント時の一実施例のブ【１ツク図、第８図は第７
図の詳細ブロック図である。
Ｃ及びＣ１−Ｃ５・・・圧縮機ケ示す。Ｌ及びＬ１〜１
．５・・・負荷及び空圧機器？示す。
１・・・圧力検出器、２・・吐出圧−軍制側ｊ装置、３
・・・流肯袖正付吐出圧一定制御装置、４・・流量検出
器、３１・・自乗器、３２・・・比例器、３３・・・末
端圧力設定器、３４・・・〃ｒＪ算器、３５・・・圧力
一定ｆｌｊＩｌ直回路、５・・・運転台数補正付吐出圧
力一定ｆｌｉｌｌ ｆｆｔｌ ｇ置、６・・・運転台数
流量換算器、６１・・・運転台数流山１換Ｎ器、５１・
・・自乗器、５２・・・比例器、５３・・末端圧力設１
５ う 図
イ、４０
′ｔ７乙囚Figure 1 is a characteristic diagram of compressor load air volume, discharge pressure, and 111I power dynamics, Figure 2 is a characteristic diagram of load air volume, discharge pressure, and piping loss of the piping system, and Figure 3 is a characteristic diagram of conventional discharge pressure -5. Kaimei 1
Fig. 4 is an inertia diagram of the load, discharge pressure, and end pressure during the conventional discharge 1j shoulder --- military system and the discharge sterilization sleeve pressure of the present invention, 'F; The figure is a block diagram of one embodiment of the installation of the flow agitation detector of the O' invention, and Figure 6 is the flow diagram of the fifth embodiment.
・Detailed block diagram of the figure, Figure 7 is a block diagram of one embodiment of O invention when counting the total number of compressors, Figure 8 is a block diagram of the embodiment
FIG. 2 is a detailed block diagram of the figure. C and C1-C5... Indicates a compressor. L and L1~1
．． 5...Load and pneumatic equipment? show. 1...Pressure detector, 2...Discharge pressure-military side j device, 3
...Discharge pressure constant control device with flow sensor, 4..Flow rate detector, 31..Squarer, 32..Proportional device, 33.. Terminal pressure setting device, 34..〃rJ calculation 35... Constant pressure fljIl direct circuit, 5... Constant discharge pressure flill fftl g position with correction for number of operating units, 6... Number of operating units flow rate converter, 61... Number of operating units flow rate 1 conversion N unit, 51・
...Squarer, 52...Proportional device, 53...Terminal pressure setting 1
5 U Figure I, 40't7 Otsu prisoner
Claims (1)
応じて吐出圧力の設定値を制御することを特徴とする圧
縮機の高効率側斜方法、。(2) A high-efficiency side diagonal method for a compressor, which is characterized by controlling the set value of discharge pressure according to the usage of load flow rate or the number of operating compressors in a group.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16046383A JPS6053686A (en) | 1983-09-02 | 1983-09-02 | Method of high efficiently controlling compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16046383A JPS6053686A (en) | 1983-09-02 | 1983-09-02 | Method of high efficiently controlling compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6053686A true JPS6053686A (en) | 1985-03-27 |
Family
ID=15715484
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16046383A Pending JPS6053686A (en) | 1983-09-02 | 1983-09-02 | Method of high efficiently controlling compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6053686A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS647508U (en) * | 1987-07-04 | 1989-01-17 | ||
| JP2002098084A (en) * | 2000-09-20 | 2002-04-05 | Hitachi Ltd | Screw compression equipment and its operating method |
-
1983
- 1983-09-02 JP JP16046383A patent/JPS6053686A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS647508U (en) * | 1987-07-04 | 1989-01-17 | ||
| JPH058092Y2 (en) * | 1987-07-04 | 1993-03-01 | ||
| JP2002098084A (en) * | 2000-09-20 | 2002-04-05 | Hitachi Ltd | Screw compression equipment and its operating method |
| JP4520608B2 (en) * | 2000-09-20 | 2010-08-11 | 株式会社日立プラントテクノロジー | Screw compressor |
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