JPH0396668A - Oil recovery device of oil cooling type compressor - Google Patents
Oil recovery device of oil cooling type compressorInfo
- Publication number
- JPH0396668A JPH0396668A JP23338689A JP23338689A JPH0396668A JP H0396668 A JPH0396668 A JP H0396668A JP 23338689 A JP23338689 A JP 23338689A JP 23338689 A JP23338689 A JP 23338689A JP H0396668 A JPH0396668 A JP H0396668A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- compressor
- orifice
- valve
- pressure difference
- 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
- 238000011084 recovery Methods 0.000 title claims abstract description 53
- 238000001816 cooling Methods 0.000 title 1
- 238000000926 separation method Methods 0.000 claims description 9
- 230000007423 decrease Effects 0.000 claims description 7
- 239000000314 lubricant Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 82
- 230000001105 regulatory effect Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000945 filler Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Landscapes
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は、油冷式圧縮機の油回収装置に関し、特に詳し
く言えば、圧縮機から吐出される気体中に含まれる油を
分離する油分離装置と、圧縮機の油戻し箇所との間に、
回収配管が設けられている油冷式圧縮機に関するもので
ある。Detailed Description of the Invention [Field of Industrial Application] The present invention relates to an oil recovery device for an oil-fed compressor, and more specifically, the present invention relates to an oil recovery device for an oil-fed compressor, and more particularly, to an oil recovery device for separating oil contained in gas discharged from a compressor. Between the separator and the oil return point of the compressor,
This invention relates to an oil-cooled compressor equipped with recovery piping.
［従来の技術］
従来の油冷式圧縮機は、例えば特開昭５８−１０６５８
８号公報，同５ｇ−９６０８７号公報、同５７−２５１
９３号公報に記載されているように、圧縮機から吐出さ
れた気体中に含まれている油は油分離装置で分離され、
そして分離された油の回収は、回収元である該油分離装
置と回収先である圧縮機の吸入側或は給油口との間の圧
力差により回収配管経由で行われている．このため，圧
縮機で圧縮され吐出された気体（以下代表的に例えば空
気とする）が必要以上に回収油分と共に圧縮機に戻るこ
とがないように、回収配管の途中にオリフィスを設けて
、油分のみを圧縮機へ回収するようにしている。そして
、このオリフィスの口径は，仕様圧力時すなわち定格圧
力時において最適性能を出すように固定的に決められて
おり，ｇ整機能がないものであった。[Prior Art] A conventional oil-cooled compressor is disclosed in, for example, Japanese Patent Application Laid-Open No. 58-10658.
Publication No. 8, Publication No. 5g-96087, Publication No. 57-251
As described in Publication No. 93, oil contained in the gas discharged from the compressor is separated by an oil separator,
The separated oil is recovered via recovery piping based on the pressure difference between the oil separation device, which is the source of the oil recovery, and the suction side or oil filler port of the compressor, which is the destination. Therefore, in order to prevent the gas compressed and discharged by the compressor (hereinafter typically referred to as air) from returning to the compressor together with the recovered oil more than necessary, an orifice is provided in the middle of the recovery piping to remove the oil. Only the waste is collected into the compressor. The diameter of this orifice is fixedly determined to provide optimum performance at the specified pressure, that is, at the rated pressure, and does not have a g adjustment function.
［発明が解決しようとする課題］
上記の従来技術においては、定格運転時には格別問題は
ないが、圧縮機の吐出圧力が仕様圧力より低い時、例え
ば起動時には、分離された油分の回収元である油分離装
置（この部分の圧力は圧縮機の吐出圧力と同等）と、回
収先である圧縮機の吸入側或は給油口附近との圧力差が
小さいため，オリフィスを通って回収される油量は減少
し，油分離装置から先へ吐出される圧縮空気中に一旦分
離された油が再び混入し，油の持去りという現象が生じ
る。この持去りは、使用空気量に応じて圧縮機をオン，
オフ制御する場合における再起動時（吐出圧力が仕様圧
力より低くなっている）に多く見られる現象である．
この対策として，オリフィス径を大きくして油の回収量
を増すことも考えられるが、オリフィス径を大きくする
と、仕様圧力（定格圧力）で運転している時には、回収
配管を通って圧縮機の吸入側へ戻される圧縮空気量が多
くなり、圧縮機の性能低下を生じる．
したがって、本発明は、圧縮機の吐出圧力が仕様圧力よ
り低いときにも油の回収が充分できると共に、圧縮空気
の一部が圧縮機の吸入側へ妄りに戻ることのない油冷式
圧縮機の油回収装置を提供することを目的としている。[Problems to be Solved by the Invention] In the above conventional technology, there is no particular problem during rated operation, but when the discharge pressure of the compressor is lower than the specified pressure, for example at startup, the separated oil is a source of recovery. Since the pressure difference between the oil separator (the pressure in this part is equivalent to the compressor discharge pressure) and the oil recovery site on the suction side of the compressor or near the oil filler port is small, the amount of oil recovered through the orifice is small. As a result, the oil that has been separated is re-mixed into the compressed air discharged from the oil separator, causing a phenomenon called oil removal. This removal is done by turning on the compressor depending on the amount of air used.
This phenomenon is often seen when restarting when using off control (discharge pressure is lower than the specified pressure). As a countermeasure to this problem, it is possible to increase the amount of oil recovered by increasing the orifice diameter, but if the orifice diameter is increased, when operating at the specified pressure (rated pressure), the oil will pass through the recovery pipe and enter the compressor. The amount of compressed air returned to the side increases, resulting in a decrease in compressor performance. Therefore, the present invention provides an oil-cooled compressor that can sufficiently recover oil even when the discharge pressure of the compressor is lower than the specified pressure, and that prevents a part of the compressed air from accidentally returning to the suction side of the compressor. The purpose is to provide oil recovery equipment.
［課題を解決するための手段］
本発明においては，上記目的を達威するために、油回収
元と油回収先との圧力差によってオリフィスロ径が変わ
り，仕様圧力時に最適オリフィスロ径となるオリフィス
を有した自動弁が回収配管に介装される．すなわち回収
配管には、油分離装置と圧縮機の油戻し箇所との圧力差
が小さいときには、通路面積が大きくなり、該圧力差が
大きいときは通路面積が小さくなる自動弁が介装される
。[Means for Solving the Problems] In the present invention, in order to achieve the above object, the orifice throat diameter changes depending on the pressure difference between the oil recovery source and the oil recovery destination, and the orifice throat diameter becomes optimal at the specified pressure. An automatic valve with an orifice is installed in the recovery pipe. That is, the recovery piping is provided with an automatic valve that increases the passage area when the pressure difference between the oil separation device and the oil return point of the compressor is small, and decreases the passage area when the pressure difference is large.
［作 用コ
本発明は、上記手段を有するので、圧縮機の吐出圧力が
低いとき、例えば起動時においては，油分離装置と圧縮
機の油戻し箇所との圧力差は小さいので、自動弁の通路
面積は大きくなる、すなわちオリフィスの口径は大きく
なる。したがって、油分離装置で分離された油は，使用
先に送られる圧縮空気に殆んど混入することなく圧縮機
の方への回収配管を通して回収される。[Function] Since the present invention has the above means, when the discharge pressure of the compressor is low, for example at startup, the pressure difference between the oil separator and the oil return point of the compressor is small, so the automatic valve is activated. The passage area becomes larger, ie the orifice diameter becomes larger. Therefore, the oil separated by the oil separator is recovered through the recovery pipe toward the compressor without being mixed with the compressed air sent to the user.
次に定格圧力運転時には上記圧力差は大きくなるので、
自動弁の通路面積は小さくなる。したがって、圧縮され
た空気の一部が回収配管を通って再び圧縮機に戻るよう
なことはない。すなわち圧縮機の性能が低下するような
ことはない。そして、このときには自動弁の通路面積は
定格運転時に対応する所定の面積を有するので油の回収
に支障はない。Next, during rated pressure operation, the above pressure difference increases, so
The passage area of automatic valves becomes smaller. Therefore, a portion of the compressed air does not return to the compressor through the recovery pipe. In other words, the performance of the compressor does not deteriorate. At this time, the passage area of the automatic valve has a predetermined area corresponding to the rated operation, so there is no problem in oil recovery.
［実 施 例］ 以下、本発明の１実施例を添付図面によって説明する。[Example] Hereinafter, one embodiment of the present invention will be described with reference to the accompanying drawings.
第１図は、油冷式圧縮機として，圧縮空気を作るための
油冷式スクリュー圧縮機を使用した実施例を示すシステ
ム図である。図示のシステム全体としては従来のものと
略同じである。すなわち本システムは，スクリュー圧縮
機２、油分離器３、アフタークーラー４、オイルクーラ
ー５、油分離装置であるフィルタ６，吐出調圧弁７，オ
イルフィルタ８，空気ｉｆ！Ｊ９、制御用圧力スイッチ
１０等から或る．
圧縮機２に吸入された空気は圧縮機２により圧縮され、
この圧縮途中に給油口２′から噴射された潤滑油ととも
に油分離器３へ吐出される。ここで一部の油分は油分離
器３の下部に溜り、残りの油分は油分離装置であるフィ
ルタ６で分離される。FIG. 1 is a system diagram showing an embodiment in which an oil-cooled screw compressor for producing compressed air is used as an oil-cooled compressor. The illustrated system as a whole is substantially the same as the conventional system. That is, this system includes a screw compressor 2, an oil separator 3, an aftercooler 4, an oil cooler 5, a filter 6 which is an oil separation device, a discharge pressure regulating valve 7, an oil filter 8, and an air if! J9, control pressure switch 10, etc. The air sucked into the compressor 2 is compressed by the compressor 2,
During this compression, the oil is discharged to the oil separator 3 together with the lubricating oil injected from the oil supply port 2'. Here, a part of the oil accumulates in the lower part of the oil separator 3, and the remaining oil is separated by a filter 6, which is an oil separator.
分離された油分は、回収配管工１に設けられた油回収装
置ｌを通って圧縮機へ回収される。油が分離された圧縮
空気は吐出調圧弁７を経て、アフタークーラー４にて冷
却された後，空気槽９へ送出される。一方、油分離器３
の下部に溜まった潤滑油は，オイルクーラー５にて冷却
され、オイルフィルタ８を経て再び圧縮機２へ供給され
る。The separated oil passes through an oil recovery device l provided in the recovery plumber 1 and is recovered to the compressor. The compressed air from which oil has been separated passes through a discharge pressure regulating valve 7, is cooled in an aftercooler 4, and then is sent to an air tank 9. On the other hand, oil separator 3
The lubricating oil collected at the bottom of the compressor is cooled by an oil cooler 5, and then supplied to the compressor 2 again through an oil filter 8.
油回収装置Ｉは，従来技術では前述した様な固定口径の
オリフィスであったが，本発明実施例では圧力差に依っ
て通路面積が変る自動弁である。In the prior art, the oil recovery device I was an orifice with a fixed diameter as described above, but in the embodiment of the present invention, it is an automatic valve whose passage area changes depending on the pressure difference.
自動弁としての油回収装置ｌのｌ実施例が第２図に示さ
れている。本装置は、弁＠２０と板バネ２１とから成っ
ている．弁箱２０は、回収配管１１に介装するために、
ネジ２２が形成されている大径腔部２３と、同様にネジ
２４が形成されている小径腔部２５とを有し．これらの
腔部を連通ずるようにして，比較的大径のオリフィス２
６が設けられている．
板バネ２ｌは、少なくともオリフィス２６の口径より広
い幅を有し，その端部は大径腔部の底壁２７に固定され
，フィルタ６と圧縮機２の油戻し箇所２′との間の圧力
差すなわち両腔部２３，２５間に作用する圧力差が小さ
いときは、図示されているように，底壁２７から，その
一方の端部が離間するように設けられている。また板バ
ネ２１には定格運転時に最適口径となる比較的小径のオ
リフィス２８が設けられている．そして、これらのオリ
フィス２６．２８は対向して設けられ、板バネ２１が弁
′ｌｌｉ２０の底壁２７に密着するときは，これらのオ
リフィス２６．２８は重なって連通ずるようになってい
る。An embodiment of an oil recovery device as an automatic valve is shown in FIG. This device consists of a valve @20 and a leaf spring 21. In order to insert the valve box 20 into the recovery pipe 11,
It has a large diameter cavity 23 in which a screw 22 is formed and a small diameter cavity 25 in which a screw 24 is similarly formed. A relatively large diameter orifice 2 is installed so that these cavities communicate with each other.
6 is provided. The leaf spring 2l has a width at least wider than the diameter of the orifice 26, and its end is fixed to the bottom wall 27 of the large diameter cavity, so that the pressure between the filter 6 and the oil return point 2' of the compressor 2 is reduced. When the difference, that is, the pressure difference acting between both cavities 23 and 25 is small, one end thereof is spaced apart from the bottom wall 27, as shown in the figure. The leaf spring 21 is also provided with a relatively small-diameter orifice 28 that has an optimum diameter during rated operation. These orifices 26, 28 are provided facing each other, and when the leaf spring 21 is in close contact with the bottom wall 27 of the valve 'lli20, these orifices 26, 28 overlap and communicate with each other.
次に具体的な数値を使用して、上記実施例の作用を説明
する，
圧縮機の仕様圧力を例えば８．５ｋｇｆ／ａ＃（ｇ）
（ ｇはゲージ圧力の意）、吐出調圧弁７の設定圧力を
５ｋｇｆ／ａｊ（ｇ）とすると、圧縮機２がＯＮ−ＯＦ
Ｆ制御方式の場合、空気槽９の圧力は５〜ｇ．ｓｋｇｆ
／ａ＃（ｇ）の間で使用される。圧縮機を運転すると、
空気槽９の圧力が吐出調圧弁７の設定圧力より低いとき
は、圧縮槽２の吐出圧力は吐出調圧弁７の設定圧力５ｋ
ｇｆ／ａＪ（ｇ）で運転される。Next, the operation of the above embodiment will be explained using specific numerical values.The specified pressure of the compressor is, for example, 8.5 kgf/a# (g).
(g means gauge pressure), if the set pressure of the discharge pressure regulating valve 7 is 5 kgf/aj (g), the compressor 2 is ON-OF.
In the case of the F control method, the pressure in the air tank 9 is 5 to g. skgf
/a#(g). When operating the compressor,
When the pressure in the air tank 9 is lower than the set pressure of the discharge pressure regulating valve 7, the discharge pressure of the compression tank 2 is equal to the set pressure of the discharge pressure regulating valve 7, 5k.
It is operated at gf/aJ (g).
この時の油回収装置１の前後の圧力差は０．８ｋｇｆ／
ａＪ（ｇ）程度であり、この時は油回収装置１の板バネ
２１は開いており、回収通路すなわちオリフィス２６の
面積はおよそ９．４ｍ” （板バネのリフト上閣、オリ
フィス２６の内径３ｍの場合）である。At this time, the pressure difference before and after the oil recovery device 1 is 0.8 kgf/
aJ (g), and at this time, the leaf spring 21 of the oil recovery device 1 is open, and the area of the recovery passage, that is, the orifice 26, is approximately 9.4 m'' (the inner diameter of the orifice 26 is 3 m). ).
圧縮機２の定格吐出圧力１１１，５ｋｇｆ／ａＪ（ｇ）
での最適オリフィスであるところのオリフィス２８の内
径は０．７ｍであり，これに比べ約２４倍の通路面積を
有している。従って圧力差が０．８ｋｇｆ／ａ！でも分
離された油分を充分回収することができる。Rated discharge pressure of compressor 2 111.5 kgf/aJ (g)
The inner diameter of the orifice 28, which is the optimum orifice, is 0.7 m, and has a passage area approximately 24 times larger than this. Therefore, the pressure difference is 0.8 kgf/a! However, the separated oil can be sufficiently recovered.
次に圧縮機の吐出圧力が上って来て空気槽９の圧力が上
昇するにつれて，油分離装置６と圧縮機の油戻し箇所２
′との間の圧力差すなわち油回収装置１の前後の圧力差
も上昇し、板バネ２１は徐々に閉じて，仕様吐出圧力８
．５ｋｇｆ／ａＪ（ｇ）では底壁２７に密着し，回収通
路は最適オリフィス２８だけとなって、分離された油分
を回収する。その後、使用空気量が増加し，吐出圧力が
下がってくると、前記の圧力差も減少し、板バネ２ｌは
圧力差に応じて徐々に開き、油回収量を増加させる働き
をする。Next, as the discharge pressure of the compressor rises and the pressure of the air tank 9 increases, the oil separation device 6 and the oil return point 2 of the compressor increase.
The pressure difference between
．． At 5 kgf/aJ (g), the oil comes into close contact with the bottom wall 27, and the only recovery passage is the optimum orifice 28 to recover the separated oil. Thereafter, when the amount of air used increases and the discharge pressure decreases, the pressure difference described above also decreases, and the leaf spring 2l gradually opens in accordance with the pressure difference, working to increase the amount of oil recovered.
また、使用空気量が減少し、吐出圧力が上昇してくると
． ８．５ｋｇｆ／ａＪ（ｇ）を越えたとき制御用圧力
スイッチ１０が動作して圧縮機を停止させる。Also, if the amount of air used decreases and the discharge pressure increases. When the pressure exceeds 8.5 kgf/aJ (g), the control pressure switch 10 operates to stop the compressor.
停止時は油分離器３内の圧縮空気を大気へ放出（図示せ
ず）するので、空気槽９側からの圧縮空気の逆流を防止
するため吐出調圧弁７内に設けられた逆止弁が動作する
。停止後、空気槽圧力が低下してくると、これを前述の
圧力スイッチ１０にて検知し、圧縮機は再起動される。When the oil separator 3 is stopped, the compressed air in the oil separator 3 is released to the atmosphere (not shown), so a check valve installed in the discharge pressure regulating valve 7 is installed to prevent the compressed air from flowing back from the air tank 9 side. Operate. After the compressor is stopped, when the air tank pressure decreases, this is detected by the pressure switch 10 described above, and the compressor is restarted.
この再起動は圧力スイッチ１０の設定圧力から始まり、
徐々に吐出圧力が上昇していき、前述の油回収作用をく
り返す。This restart starts from the set pressure of the pressure switch 10,
The discharge pressure gradually increases, and the oil recovery action described above is repeated.
油回収装霞１すなわち自動弁の他の異なる実施例が第３
図、第４図に夫々示されている。これらの図において、
第２図に示す各部分と同様な作用をする部分には同じ参
照符号を付して重複説明は省く。Another different embodiment of the oil recovery system 1, that is, the automatic valve is shown in the third example.
and FIG. 4, respectively. In these figures,
The same reference numerals are given to parts having the same functions as those shown in FIG. 2, and redundant explanation will be omitted.
第３図の実施例は、オリフィス２８を有するフロート４
０の重力と、油分離装置６と圧縮機の油戻し箇所２′と
の間の圧力差との兼ね合いにより、フロート４０が上下
してオリフィス２６を開き又は閉じることにより回収通
路面積が変わるものである。The embodiment of FIG. 3 has a float 4 having an orifice 28.
Due to the balance between the zero gravity and the pressure difference between the oil separator 6 and the oil return point 2' of the compressor, the recovery passage area changes by moving the float 40 up and down to open or close the orifice 26. be.
第４図に示す実施例においては、弁板４ｌはコイルスプ
リング４２．４２により弁座４３から離間する方向に付
勢されている。弁座４３は，その中心部に比較的大径の
オリフィス２６を形威しており，側部には小径のオリフ
ィス２８となる切欠を有する。油分離装置６と圧縮機の
油戻し箇所２１との間の圧力差が小さいときは、第４図
（ａ）に示すように，弁板４１が弁座４３からコイルス
プリング４２．４２の力によって離間し、オリフィス２
６は開き、通路面積は大きくなる．上記圧力差が大きく
なると、第４図（ｂ）に示すように弁板４１が弁座４３
に接触し、大径のオリフィス２６を閉鎖し、弁座４３の
側部に設けられている小さい切欠状のオリフィス２８の
みが開口し、圧縮空気の圧縮機２への妄りな戻りを防止
する。In the embodiment shown in FIG. 4, the valve plate 4l is biased away from the valve seat 43 by coil springs 42,42. The valve seat 43 has a relatively large-diameter orifice 26 in its center, and has a notch on the side that serves as a small-diameter orifice 28. When the pressure difference between the oil separator 6 and the oil return point 21 of the compressor is small, the valve plate 41 is moved away from the valve seat 43 by the force of the coil springs 42 and 42, as shown in FIG. 4(a). Separated, orifice 2
6 is open and the passage area becomes larger. When the above pressure difference becomes large, the valve plate 41 moves toward the valve seat 43 as shown in FIG. 4(b).
The large-diameter orifice 26 is closed, and only the small notch-shaped orifice 28 provided on the side of the valve seat 43 is opened, thereby preventing compressed air from accidentally returning to the compressor 2.
更に他の実施例を第５図に示す。この第５図に示す実施
例はシリンダ５０と、このシリンダ内に摺動自在に設け
られているピストン５ｌとを具えている．ネジを切った
接続口２２．２４には回収配管１１が接続される。ピス
トン５１は、比較的大径のオリフィス５２を軸内に有し
、ピストンの外周にはピストンリング５３，５４が設け
られている。シリンダ５０の内面には段部が複数個形成
され，ピストン５ｌと協働するようになっている。Still another embodiment is shown in FIG. The embodiment shown in FIG. 5 includes a cylinder 50 and a piston 5l slidably disposed within the cylinder. The recovery pipe 11 is connected to the threaded connection port 22,24. The piston 51 has a relatively large-diameter orifice 52 in its shaft, and piston rings 53 and 54 are provided around the outer periphery of the piston. A plurality of stepped portions are formed on the inner surface of the cylinder 50 and cooperate with the piston 5l.
シリンダ５０には，その底壁５５から離間する方向に所
定の間隔をおいて、比較的小径のオリフィス５６，５７
．５８・・・が複数個形成され、これらのオリフィスは
室５９に連通している。The cylinder 50 has relatively small diameter orifices 56, 57 spaced apart from the bottom wall 55 thereof at a predetermined distance.
．． A plurality of orifices 58 are formed, and these orifices communicate with the chamber 59.
今，油分離装置６と圧縮機の油戻し箇所２′との間の差
圧が小さいときは、第５図（ａ）に示すように、ピスト
ン５ｌはコイルスプリング６０により図において右方に
押され、小さなオリフィス５６．５７・・・が開口し，
通路面積は大きくなる。Now, when the differential pressure between the oil separator 6 and the oil return point 2' of the compressor is small, the piston 5l is pushed to the right in the figure by the coil spring 60, as shown in FIG. 5(a). The small orifices 56, 57... are opened,
The passage area becomes larger.
上記の圧力差が大きくなると，ピストン５１は差圧に応
じて左行し，これらオリフィス５６．５７．５８のうち
右方のオリフィスから順次閉鎖し，通路面積は小さくな
る。そして圧力差が最も大きくなると、第５図（ｂ）に
示すようにピストンは最も左方に移行し、１個のオリフ
ィス５６のみが開口し，通路面積は最小となり、圧縮空
気が圧縮機に戻るのが阻止される．
なお、先述の実施例において，圧力差が小さい時の回収
量の設定は、回収通路オリフィスの径，および弁のリフ
トを変えることにより変更でき、また、圧力差による弁
の開閉時期は、弁のバネ定数を変えることにより変更可
能であることは明らかである。When the above-mentioned pressure difference becomes large, the piston 51 moves to the left according to the pressure difference, and the orifices 56, 57, 58 are sequentially closed starting from the right one, and the passage area becomes smaller. When the pressure difference becomes the largest, the piston moves to the farthest left as shown in Figure 5(b), only one orifice 56 opens, the passage area becomes the minimum, and the compressed air returns to the compressor. is prevented. In addition, in the above embodiment, the setting of the recovery amount when the pressure difference is small can be changed by changing the diameter of the recovery passage orifice and the lift of the valve, and the opening/closing timing of the valve due to the pressure difference can be changed by changing the diameter of the recovery passage orifice and the lift of the valve. It is clear that this can be changed by changing the spring constant.
［発明の効果］
本発明によると、以上のように回収配管中に、通路面積
が自動的に変わる自動弁が介装されているので、吐出圧
力が変化しても、分離された油分の回収元と回収先の圧
力差に応じて自動的に油回収量の制御が行なえる．これ
により、再起動時、仕様運転時等，どの様な吐出圧力の
状態でも分離した油分の回収が適正にでき、圧縮空気中
への油分の混入を防止することができる．[Effects of the Invention] According to the present invention, as described above, an automatic valve that automatically changes the passage area is installed in the recovery piping, so even if the discharge pressure changes, the separated oil can be recovered. The amount of oil recovered can be automatically controlled according to the pressure difference between the source and destination. This allows the separated oil to be properly collected under any discharge pressure conditions, such as during restart or specified operation, and prevents oil from entering the compressed air.
図面は、本発明の実施例を示し，第１図はシステム全体
を示す概念図，第２図、第３図（ａ），（ｂ）、第４図
（ａ），（ｂ）、第５図（ａ） ， （ｂ）は自動弁の
それぞれ異なる実施例を示す断面図である．
１・・・自動弁（油回収装Ｗ）
２・・・圧縮機 ３・・・油分離器６・・・
油分離フィルタ（油分離装置）１ｌ・・・回収配管
２０・・・弁箱２工・・・板バネ ４０・
・・フロート４ｌ・・・弁板 ４３・・・弁
座５０・・・シリンダ ５１・・・ピストン２６
，２８，５２，５６，５７．５８・・・オリフィス（通
路）The drawings show an embodiment of the present invention, and FIG. 1 is a conceptual diagram showing the entire system, FIG. 2, FIG. 3 (a), (b), FIG. 4 (a), (b), and FIG. Figures (a) and (b) are cross-sectional views showing different embodiments of automatic valves. 1... Automatic valve (oil recovery equipment W) 2... Compressor 3... Oil separator 6...
Oil separation filter (oil separation device) 1l...Recovery piping
20... Valve box 2... Leaf spring 40.
...Float 4l...Valve plate 43...Valve seat 50...Cylinder 51...Piston 26
, 28, 52, 56, 57. 58... Orifice (passage)
Claims (1)
油分離装置と、圧縮機の油戻し箇所との間に回収配管が
設けられている油冷式圧縮機において、前記回収配管に
は、前記油分離装置と圧縮機の油戻し箇所との圧力差が
小さいときには通路面積が大きくなり、該圧力差が大き
いときには通路面積が小さくなる自動弁が介装されてい
ることを特徴とする油冷式圧縮機の油回収装置。 ２ 前記の自動弁が、比較的大径の第１のオリフィスを
有する弁箱と、該弁箱内に設けられた比較的小径の第２
のオリフィスを有する板バネとからなり、これらの両オ
リフィスは相対向するとともに、前記板バネは、油分離
装置と圧縮機の油戻し箇所との圧力差が小さいときには
前記弁箱の前記第１のオリフィスが穿たれている壁から
離間し、該圧力差が大きいときは該壁に密接するように
設けられている請求項１記載の油冷式圧縮機の油回収装
置。 ３ 前記の自動弁が、比較的大径の第１のオリフィスを
有する弁箱と、該弁箱内に配された比較的小径の第２の
オリフィスを有するフロートとからなり、前記弁箱内に
てこれらの両オリフィスが相対向するとともに、前記フ
ロートは、油分離装置と圧縮機の油戻し箇所との圧力差
が小さいときには前記弁箱の前記第１のオリフィスが穿
たれている壁から離間し、該圧力差が大きいときは該壁
に密接するように設けられている請求項１記載の油冷式
圧縮機の油回収装置。 ４ 前記の自動弁が、中心部に比較的大径のオリフィス
を有するとともに側部に比較的小径のオリフィスを有す
る弁座と、該弁座と協働する弁板とからなり、前記弁板
は、油分離装置と圧縮機の油戻し箇所との圧力差が小さ
いときには前記弁座から離間し、該圧力差が大きいとき
は前記弁座に密接するようにバネ付勢されている請求項
１記載の油冷式圧縮機の油回収装置。 ５ 前記の自動弁が、シリンダと該シリンダ内に設けら
れているバネ付勢されたピストンとからなり、前記ピス
トンは比較的大径のオリフィスを軸方向に有するととも
に、前記シリンダは比較的小径の複数個のオリフィスを
その軸方向に所定間隔をおいて有し、前記ピストンは、
油分離装置と圧縮機の油戻し箇所との圧力差が小さいと
きには前記ピストンのオリフィスと連通する前記シリン
ダのオリフィスの数を増し、該圧力差が大きいときは、
該数を減らすようにシリンダ内で軸方向に摺動自在であ
る請求項１記載の油冷式圧縮機の油回収装置。[Scope of Claims] 1. In an oil-fed compressor in which a recovery pipe is provided between an oil separation device that separates oil contained in gas discharged from the compressor and an oil return point of the compressor, The recovery piping is equipped with an automatic valve that increases the passage area when the pressure difference between the oil separation device and the oil return point of the compressor is small, and decreases the passage area when the pressure difference is large. An oil recovery device for an oil-cooled compressor featuring: 2. The automatic valve has a valve box having a first orifice with a relatively large diameter, and a second orifice with a relatively small diameter provided in the valve box.
a leaf spring having an orifice of 2. The oil recovery device for an oil-cooled compressor according to claim 1, wherein the orifice is spaced apart from the wall in which the orifice is bored and is provided in close contact with the wall when the pressure difference is large. 3. The automatic valve described above is comprised of a valve box having a first orifice with a relatively large diameter, and a float having a second orifice with a relatively small diameter disposed within the valve box, When the pressure difference between the oil separator and the oil return point of the compressor is small, the float is separated from the wall in which the first orifice of the valve body is bored. 2. The oil recovery device for an oil-cooled compressor according to claim 1, wherein the oil recovery device for an oil-cooled compressor is provided in close contact with the wall when the pressure difference is large. 4. The above-mentioned automatic valve comprises a valve seat having a relatively large diameter orifice in the center and a relatively small diameter orifice on the side, and a valve plate cooperating with the valve seat, and the valve plate is 2. The valve is spring-biased so as to move away from the valve seat when the pressure difference between the oil separator and the oil return point of the compressor is small, and to come into close contact with the valve seat when the pressure difference is large. Oil recovery equipment for oil-cooled compressors. 5. The automatic valve comprises a cylinder and a spring-biased piston provided in the cylinder, the piston having a relatively large diameter orifice in the axial direction, and the cylinder having a relatively small diameter orifice in the axial direction. The piston has a plurality of orifices at predetermined intervals in its axial direction,
When the pressure difference between the oil separation device and the oil return point of the compressor is small, the number of orifices in the cylinder communicating with the orifice of the piston is increased, and when the pressure difference is large,
The oil recovery device for an oil-cooled compressor according to claim 1, wherein the oil recovery device for an oil-cooled compressor is slidable in the axial direction within the cylinder so as to reduce the number.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1233386A JP2824289B2 (en) | 1989-09-08 | 1989-09-08 | Oil recovery unit for oil-cooled compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1233386A JP2824289B2 (en) | 1989-09-08 | 1989-09-08 | Oil recovery unit for oil-cooled compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0396668A true JPH0396668A (en) | 1991-04-22 |
| JP2824289B2 JP2824289B2 (en) | 1998-11-11 |
Family
ID=16954282
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1233386A Expired - Lifetime JP2824289B2 (en) | 1989-09-08 | 1989-09-08 | Oil recovery unit for oil-cooled compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2824289B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07217577A (en) * | 1994-02-01 | 1995-08-15 | Hitachi Ltd | Oil separation element for oil-cooled compressor |
| JP2008267347A (en) * | 2007-04-24 | 2008-11-06 | Denso Corp | Compressor |
| EP3155265A4 (en) * | 2014-06-13 | 2018-02-07 | Clark Equipment Company | Air compressor discharge system |
| CN108386357A (en) * | 2018-04-18 | 2018-08-10 | 北京燕都碧城科技有限公司 | A kind of single screw compressor anti-liquid impact device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60228796A (en) * | 1984-04-26 | 1985-11-14 | Hokuetsu Kogyo Co Ltd | Power reducing device of liquid-cooling type rotary compressor |
-
1989
- 1989-09-08 JP JP1233386A patent/JP2824289B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60228796A (en) * | 1984-04-26 | 1985-11-14 | Hokuetsu Kogyo Co Ltd | Power reducing device of liquid-cooling type rotary compressor |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07217577A (en) * | 1994-02-01 | 1995-08-15 | Hitachi Ltd | Oil separation element for oil-cooled compressor |
| JP2008267347A (en) * | 2007-04-24 | 2008-11-06 | Denso Corp | Compressor |
| EP3155265A4 (en) * | 2014-06-13 | 2018-02-07 | Clark Equipment Company | Air compressor discharge system |
| US10378536B2 (en) | 2014-06-13 | 2019-08-13 | Clark Equipment Company | Air compressor discharge system |
| CN108386357A (en) * | 2018-04-18 | 2018-08-10 | 北京燕都碧城科技有限公司 | A kind of single screw compressor anti-liquid impact device |
| CN108386357B (en) * | 2018-04-18 | 2024-05-28 | 北京燕都碧城科技有限公司 | Liquid impact preventing device of single screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2824289B2 (en) | 1998-11-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4362475A (en) | Compressor inlet valve | |
| US7086841B2 (en) | Air compressor with inlet control mechanism and automatic inlet control mechanism | |
| US5134856A (en) | Oil pressure maintenance for screw compressor | |
| US4270885A (en) | Unloading means for a gas compressor | |
| JP2009036182A (en) | Control valve for variable capacity compressor | |
| JPH0396668A (en) | Oil recovery device of oil cooling type compressor | |
| CN105612353A (en) | Oil supply type compressor | |
| EP1451469B1 (en) | Lubricant-cooled gas compressor | |
| CN218376877U (en) | Pump body subassembly, compressor unit spare and air conditioning system | |
| JPS61129494A (en) | Positive-displacement type air compressor | |
| JPH0116344B2 (en) | ||
| US2894677A (en) | Rotary compressor control | |
| CN115467829A (en) | Pump body subassembly, compressor unit spare and air conditioning system | |
| US3123093A (en) | Minimum pressure delivery valve assembly | |
| US2065199A (en) | Unloader governor device | |
| CN110925170A (en) | Novel double-speed exhaust valve and intake valve with unloading function | |
| JP2015124613A (en) | Quantity control device for compressor | |
| US6439261B1 (en) | Pressure responsive oil flow regulating supply valve | |
| JP2536176B2 (en) | Screw compressor | |
| EP0403829B1 (en) | Rotary compressor with oleopneumatic delivery control device | |
| US2170846A (en) | Automatic compressor unloader | |
| JPS6357634B2 (en) | ||
| KR101927128B1 (en) | Power source circuit for hydraulic device and providing method thereof | |
| JP2001090683A (en) | Intake control valve for oil-cooled compressor | |
| US2234462A (en) | Valve mechanism for unloading compressors |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080904 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080904 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090904 Year of fee payment: 11 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090904 Year of fee payment: 11 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100904 Year of fee payment: 12 |
|
| EXPY | Cancellation because of completion of term | ||
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100904 Year of fee payment: 12 |