JPH0227198Y2 - - Google Patents
Info
- Publication number
- JPH0227198Y2 JPH0227198Y2 JP10696586U JP10696586U JPH0227198Y2 JP H0227198 Y2 JPH0227198 Y2 JP H0227198Y2 JP 10696586 U JP10696586 U JP 10696586U JP 10696586 U JP10696586 U JP 10696586U JP H0227198 Y2 JPH0227198 Y2 JP H0227198Y2
- Authority
- JP
- Japan
- Prior art keywords
- liquid
- compressor
- discharge
- lubricating oil
- tank
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000007788 liquid Substances 0.000 claims description 67
- 239000010687 lubricating oil Substances 0.000 claims description 24
- 239000003921 oil Substances 0.000 claims description 21
- 238000011084 recovery Methods 0.000 claims description 21
- 230000000903 blocking effect Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000000605 extraction Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000000740 bleeding effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000007858 starting material Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案はスクリユ圧縮機の液体回収装置に関す
るものである。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a liquid recovery device for a screw compressor.
（従来の技術とその問題点）
スクリユ圧縮機は雌雄一対のらせん状ランドを
形成したロータが、ケーシング内において互に噛
み合い回転することによつて吸入気体の圧縮を行
なう。と同時に圧縮機内に対し、潤滑油を供給
し、圧縮作用空間内の潤滑、密封、冷却及び各軸
受、軸封等摺動部の潤滑を行なつている。(Prior art and its problems) A screw compressor compresses intake gas by having male and female rotors formed with a pair of helical lands meshing with each other and rotating in a casing. At the same time, lubricating oil is supplied into the compressor to lubricate, seal, and cool the compression space and lubricate sliding parts such as bearings and shaft seals.
この種のスクリユ圧縮機としては、本出願人の
提案による特公昭59−44514号公報のスクリユ圧
縮機が公知である。 As this type of screw compressor, the screw compressor proposed by the present applicant and disclosed in Japanese Patent Publication No. 44514/1983 is known.
この圧縮機は、第２図に示すようにケーシング
２に設けた吸入空気量制御用のアンローダ装置３
と、吐出室７の気体口９より逆止弁８Ａを介して
圧力気槽兼液体槽４に連通する吐出管４３と、前
記吐出室７の底壁に設けられた液体抜き口１０か
ら液体抜きポンプ１１を介して前記圧力気槽兼液
体槽４に設けた液体溜１２に連通する回収通路２
６を有している。 This compressor has an unloader device 3 for controlling the amount of intake air provided in a casing 2, as shown in
, a discharge pipe 43 that communicates with the pressure air tank/liquid tank 4 from the gas port 9 of the discharge chamber 7 via the check valve 8A, and a liquid drain port 10 provided on the bottom wall of the discharge chamber 7. A recovery passage 2 communicating with a liquid reservoir 12 provided in the pressure air tank/liquid tank 4 via a pump 11
6.
そして圧力気槽内の圧縮空気圧力により液体溜
１２から油量調整弁２４を介して圧縮機の吸入締
切り後の作用空間１３、吸入側軸受室１４及び吐
出側作用空間と吐出側軸受室２０間を僅かな空〓
を以て密封作用を行なつている吐出側軸封止機構
１５に対し、それぞれ並列に潤滑油を供給する潤
滑油供給回路と、圧縮機の起動時三方向電磁弁
SV1，SV2及びアンローダ装置３との共同動作に
よつて圧縮機の起動トルクを減少させる起動負荷
軽減装置とにより構成されている。 Then, the compressed air pressure in the pressure tank is used to transfer oil from the liquid reservoir 12 through the oil amount adjustment valve 24 between the working space 13 after the suction of the compressor is closed, the suction side bearing chamber 14, and the discharge side working space and the discharge side bearing chamber 20. A slight sky
A lubricating oil supply circuit that supplies lubricating oil in parallel to the discharge side shaft sealing mechanism 15 that performs a sealing action with a three-way solenoid valve when starting the compressor.
It is composed of SV 1 , SV 2 and a starting load reduction device that reduces the starting torque of the compressor by working together with the unloader device 3 .
そしてその動作は、まず図示していない駆動原
動機により圧縮機が起動し、圧力気槽兼液体槽４
内の圧力が一定圧力（１〜２Kg／cm2ゲージ圧力に
達すると、前記起動負荷軽減装置が作動し、圧縮
機内に流入する吸入空気をアンローダ装置３によ
り遮断し、吸気閉塞弁５を閉じ、同時に前述の油
量調整弁２４が動作し、圧縮機への潤滑油供給量
を絞り必要以上の供給を制限する。 In its operation, first the compressor is started by a driving motor (not shown), and the compressor is started in the pressure air tank/liquid tank 4.
When the internal pressure reaches a certain pressure (1 to 2 kg/cm 2 gauge pressure), the startup load reduction device is activated, the unloader device 3 blocks the intake air flowing into the compressor, and the intake blockage valve 5 is closed. At the same time, the aforementioned oil amount regulating valve 24 operates to throttle the amount of lubricating oil supplied to the compressor and limit the amount of lubricating oil supplied to the compressor.
さらに、圧縮機の吐出室７に於ては吸気閉塞弁
５の閉動作に伴い圧縮空気の流通が停止し、逆止
弁８Ａは閉じ圧縮機内に噴射された少量の潤滑油
だけが排出され、この排滑油は液体抜き口１０よ
り液体抜きポンプ１１によつて残留する圧縮気体
と共に回収通路２６を介して液体溜１２内に対し
て回収される。 Further, in the discharge chamber 7 of the compressor, the flow of compressed air is stopped due to the closing operation of the intake blocking valve 5, and the check valve 8A is closed, allowing only a small amount of lubricating oil injected into the compressor to be discharged. This drained lubricating oil is recovered into the liquid reservoir 12 through the liquid drain port 10 by the liquid drain pump 11 along with the remaining compressed gas through the recovery passage 26.
これにより吐出室７内の圧力が０Kg／cm2ゲージ
圧力若しくは負圧状態まで低下し、完全な無負荷
運転状態となり圧縮機の運転動力が減少する。 As a result, the pressure in the discharge chamber 7 decreases to 0 kg/cm 2 gauge pressure or a negative pressure state, resulting in a complete no-load operating state, and the operating power of the compressor decreases.
しかしながら以上の動作に於て、圧縮機の吸気
閉塞弁が閉じた以降、吐出室７内の圧力が液体抜
きポンプ１１の吸引作用によつて０Kg／cm2ゲージ
圧力若しくはそれ以下の負圧状態となる際に、一
時的に前記ポンプ内でキヤビテーシヨン現象が生
じ、これが原因となつて、その回収配管系統に大
きな振動を発することがあつた。 However, in the above operation, after the intake blockage valve of the compressor is closed, the pressure inside the discharge chamber 7 is reduced to a negative pressure state of 0 kg/cm 2 gauge pressure or lower due to the suction action of the liquid removal pump 11. When this occurs, a cavitation phenomenon temporarily occurs within the pump, which causes large vibrations in the recovery piping system.
特に前記液体抜きポンプから圧力気槽兼液体槽
４間の配管は比較的長く配管される為以下の問題
を有していた。 In particular, since the piping between the liquid removal pump and the pressure air tank/liquid tank 4 is relatively long, the following problems have occurred.
即ち、
(イ) 液体回収系統を形成する回収通路２６は、圧
縮機本体と別の振動系である圧力気槽兼液体槽
４に連通されている為、前記回収通路２６の配
管が長期間の使用時に於て振動疲労により破損
する虞れがあつた。その為、これを回避する為
に前記回収通路２６をフレキシビリテイを有す
る耐圧、高温用のゴムホース若しくはこれらに
代る可撓管にする等高価な配管材料を用いなけ
ればならなかつた。 (a) Since the recovery passage 26 forming the liquid recovery system is communicated with the compressor main body and the pressure air tank/liquid tank 4 which is a separate vibration system, the piping of the recovery passage 26 is not used for a long period of time. There was a risk of damage due to vibration fatigue during use. Therefore, in order to avoid this, it is necessary to use an expensive piping material for the recovery passageway 26, such as a pressure-resistant, high-temperature rubber hose with flexibility, or a flexible tube in place of these.
(ロ) 回収通路２６は吐出室７の液体抜き口１０と
液体溜１２とを直接連通するため配管の長さが
長くなる上に取付スペースが必要なこと及びそ
の固定が複雑となり小型化が妨げられていた。(b) Since the recovery passage 26 directly communicates the liquid outlet 10 of the discharge chamber 7 and the liquid reservoir 12, the length of the piping becomes long, and installation space is required, and its fixation becomes complicated, which impedes miniaturization. It was getting worse.
（考案の目的及び手段）
そこで本考案は、従来の圧縮機に於ける液体回
収系統上の問題点を解消し、液体回収系統を圧縮
機本体と同一の振動系に形成することによつて、
液体回収系統の信頼性を高めるとともに、圧縮機
の構造の簡素化、コストの引き下げを図ることを
目的とするもので、始動時に圧縮機の吸気閉塞弁
を閉塞する手段と連動し、無負荷運転時圧縮機へ
の潤滑油供給油量を全負荷運転時以下に制限する
油量調整弁と、前記圧縮機の吐出室には吐出弁体
を介して圧力空気槽兼液体槽に連通する気体口
と、該気体口より低水準位置に液体抜き口を設
け、運転中吐出口より吐出された圧縮空気と潤滑
油の混合流体中の圧縮気体を前記気体口から圧力
気槽兼液体槽へ、潤滑油は前記液体抜き口より液
体抜きポンプを介して液体溜にそれぞれ常時圧入
するように構成したスクリユ圧縮機に於て、前記
潤滑油を液体溜に回収するための回収通路を前記
液体抜き口より前記吐出弁体の那出側に連通し、
前記回収通路を圧縮機本体と同一振動系として配
設したことを特徴とする。(Purpose and Means of the Invention) Therefore, the present invention solves the problems with the liquid recovery system in conventional compressors, and by forming the liquid recovery system into the same vibration system as the compressor body,
The purpose is to improve the reliability of the liquid recovery system, simplify the structure of the compressor, and reduce costs.It works in conjunction with a means to close the compressor's intake block valve at startup, and prevents no-load operation. An oil volume adjustment valve that limits the amount of lubricating oil supplied to the compressor to below that during full load operation, and a gas port in the discharge chamber of the compressor that communicates with the compressed air tank and liquid tank via the discharge valve body. A liquid outlet is provided at a level lower than the gas port, and the compressed gas in the mixed fluid of compressed air and lubricating oil discharged from the discharge port during operation is transferred from the gas port to the pressure tank and liquid tank for lubrication. In a screw compressor configured such that oil is constantly pressurized into each liquid reservoir from the liquid extraction port via a liquid extraction pump, a recovery passage for recovering the lubricating oil into the liquid reservoir is provided from the liquid extraction port. communicates with the outlet side of the discharge valve body,
The present invention is characterized in that the recovery passage is arranged as the same vibration system as the compressor main body.
（作用）
本考案は以上の構成により成るので、全負荷運
転とアンロード運転の繰返し時において、万一液
体抜きポンプにキヤビテーシヨン現象が生じ、前
述回収通路である配管系統に振動が発生しても該
配管系統は液体抜きポンプと同一の振動系となつ
ている為その振動も小さく、よつて高価な配管材
料を用いる必要もなくなる。(Function) Since the present invention has the above-mentioned configuration, even if cavitation occurs in the liquid removal pump and vibration occurs in the piping system, which is the recovery passage, during repeated full-load operation and unload operation. Since the piping system has the same vibration system as the liquid removal pump, its vibration is small, and there is no need to use expensive piping materials.
（実施例）
第１図は本考案によるスクリユ圧縮機の一実施
例で、ケーシング２の上方にはアンローダ装置３
が配設され、圧力気槽兼液体槽４から供給される
消費側の圧縮空気の消費量に応じて、吸気閉塞弁
５を閉塞動作し、圧縮機１内への吸入空気量の制
御を行なつている。(Embodiment) Fig. 1 shows an embodiment of the screw compressor according to the present invention, in which an unloader device 3 is installed above the casing 2.
is provided, and according to the consumption amount of compressed air on the consumption side supplied from the pressure air tank/liquid tank 4, the intake blocking valve 5 is closed and the amount of intake air into the compressor 1 is controlled. It's summery.
それと共に、前記圧力気槽兼液体槽４内に連通
する電磁弁SV1及びSV2との組合わせ動作により
圧縮機の起動時前記吸気閉塞弁５を閉じ、圧縮機
の過大な起動トルクを減少させる起動負荷軽減装
置としての機能をも有している。 At the same time, by the combined operation of the solenoid valves SV 1 and SV 2 communicating with the pressure air tank/liquid tank 4, the intake blockage valve 5 is closed when the compressor is started, thereby reducing excessive starting torque of the compressor. It also functions as a startup load reduction device.
また、吐出口６には吐出室７を設け、該吐出室
７には吐出弁体８の逆止弁８Ａを介して圧力気槽
兼液体槽４内に連通する気体口９と、該気体口９
より低水準位置に開口する液体抜き口１０が設け
られており、後述する圧縮室内に噴射された圧縮
空気と潤滑油の混合流体はこの吐出室７内で比重
差により分離され、気体は気体口９より吐出管４
３を経て圧力気槽兼液体槽４に圧入される。 Further, the discharge port 6 is provided with a discharge chamber 7, and the discharge chamber 7 has a gas port 9 that communicates with the pressurized air tank/liquid tank 4 via the check valve 8A of the discharge valve body 8, and the gas port. 9
A liquid outlet 10 that opens at a lower level position is provided, and a mixed fluid of compressed air and lubricating oil injected into the compression chamber, which will be described later, is separated in this discharge chamber 7 due to a difference in specific gravity, and the gas is removed from the gas outlet. 9 to discharge pipe 4
3 and is press-fitted into a pressure air tank/liquid tank 4.
一方、吐出室７の底壁に流下した潤滑油は、液
体抜き口１０より液体抜きポンプ１１を介して全
負荷、無負荷運転時を問わず前記液体抜き口１０
と前記吐出弁体８の吐出側とを連通した回収通路
２６Ａ及び前記吐出管４３を経て常時圧力気槽兼
液体槽４の液体溜１２に回収される。 On the other hand, the lubricating oil that has flowed down to the bottom wall of the discharge chamber 7 is transferred from the liquid drain port 10 via the liquid drain pump 11 to the liquid drain port 10 regardless of whether the operation is under full load or during no-load operation.
The liquid is constantly collected into the liquid reservoir 12 of the pressurized gas tank/liquid tank 4 via the recovery passage 26A communicating the discharge side of the discharge valve body 8 and the discharge pipe 43.
液体溜１２内に貯留する潤滑油は、前記圧力気
槽内の圧縮空気圧力により押し出され、油通路２
１、油冷却器２２、油通路２３、油量調整弁２４
を経て油通路２５より作用空間１３内に噴射さ
れ、該圧縮室内の潤滑、密封、冷却作用を行なう
と共に、前記油通路２６より分岐して吸入側軸受
室１４及び吐出側の軸封機構１５に対して並列に
供給され、ロータ１６の吐出側端面１７とケーシ
ング１８の端壁との摺動部の潤滑及び軸受１９の
潤滑を行なう。 The lubricating oil stored in the liquid reservoir 12 is pushed out by the compressed air pressure in the pressure tank, and is pushed out through the oil passage 2.
1, oil cooler 22, oil passage 23, oil amount adjustment valve 24
The oil is injected from the oil passage 25 into the working space 13 to perform lubrication, sealing, and cooling effects in the compression chamber, and branched from the oil passage 26 to the suction side bearing chamber 14 and the discharge side shaft sealing mechanism 15. The lubricant is supplied in parallel to the rotor 16 and lubricates the sliding portion between the discharge side end surface 17 of the rotor 16 and the end wall of the casing 18 and the bearing 19.
吐出側軸封止機構１５は、ロータ１６軸に嵌着
し、その外周部とケーシング１８との間で僅かな
空〓を有して吐出側の作用空間（図示せず）と軸
受室２０とを封じている。 The discharge side shaft sealing mechanism 15 is fitted onto the shaft of the rotor 16, and has a slight air space between its outer circumference and the casing 18, so that the discharge side working space (not shown) and the bearing chamber 20 are connected to each other. is sealed.
油量調整弁２４は圧縮機の無負荷運転時潤滑油
の供給量を制限しているが、これは該圧縮機の無
負荷運転時は作用空間１３内での空気の圧縮作用
は行なわれない為、それに伴う発熱は生じないの
で潤滑と密封を目的とした極く少量の潤滑油が供
給されていれば足りる為であり、これにより潤滑
油の過剰な供給に伴う消費動力も減少する。 The oil amount regulating valve 24 limits the amount of lubricating oil supplied during no-load operation of the compressor, but this means that air compression within the working space 13 is not performed when the compressor is no-load operating. Therefore, no heat generation occurs, so it is sufficient to supply a very small amount of lubricating oil for the purpose of lubrication and sealing, and this also reduces power consumption due to excessive supply of lubricating oil.
次に、本実施例に基づく圧縮機の始動から平常
運転に至るまでの作用について説明する。 Next, the operation of the compressor according to this embodiment from starting to normal operation will be explained.
まず、図示していない始動器のスイツチを投入
すると、タイマーが働き三方電磁弁SV1は非通電
となり、圧力気槽兼液体溜４内に連通する回路３
１と回路３２は開、回路３２と回路３５は閉、同
時に三方電磁弁SV2は非通電状態で回路３１と減
圧弁３０を介して回路３３は閉、回路３３と回路
３４は開となつている。 First, when the switch of the starter (not shown) is turned on, a timer is activated and the three-way solenoid valve SV 1 is de-energized, and the circuit 3 that communicates with the pressure tank/liquid reservoir 4
1 and circuit 32 are open, circuit 32 and circuit 35 are closed, and at the same time, three-way solenoid valve SV 2 is de-energized, circuit 33 is closed via circuit 31 and pressure reducing valve 30, and circuit 33 and circuit 34 are open. There is.
この状態で、吸入空気はアンローダ装置３の吸
入口４１から吸入室４２に流入し、作用空間１３
で圧縮され吐出室７、吐出管４３を経て圧力気槽
兼液体槽４内に蓄積される。 In this state, suction air flows into the suction chamber 42 from the suction port 41 of the unloader device 3, and the working space 13
The liquid is compressed and stored in the pressure air tank/liquid tank 4 via the discharge chamber 7 and the discharge pipe 43.
そして、前記圧力気槽内の圧力が液体溜１２内
に貯留する潤滑油を圧送するにに充分な最低圧力
（１〜２Kg／cm2ゲージ圧力）に達すると、回路３
１からの圧縮空気圧力によりアンローダピストン
４４を図中左側に摺動移動させ、吸気閉塞弁５を
閉じ圧縮機１は無負荷状態となる。と同時に回路
３２，３６も連通状態にある為、油量調整弁２４
も油通路２３と２５を絞り、作用空間１３、吸入
側軸受室１４及び吐出側軸封機構１５に対する潤
滑油供給量を減少させる。 When the pressure in the pressure tank reaches the minimum pressure (1 to 2 kg/cm 2 gauge pressure) sufficient to pump the lubricating oil stored in the liquid reservoir 12, the circuit 3
The compressed air pressure from 1 causes the unloader piston 44 to slide to the left in the figure, and the intake blockage valve 5 is closed, leaving the compressor 1 in an unloaded state. At the same time, since the circuits 32 and 36 are also in communication, the oil amount adjustment valve 24
The oil passages 23 and 25 are also throttled to reduce the amount of lubricating oil supplied to the working space 13, the suction side bearing chamber 14, and the discharge side shaft sealing mechanism 15.
さらに、圧縮機１の吐出室７に於ては前述した
如く、吸気閉塞弁５の閉動作に伴い圧縮空気の流
通が停止し、逆止弁８Ａは閉じ圧縮機内に噴射さ
れた少量の潤滑油だけが排出されることになる
が、この潤滑油は液体抜き口１０より液体抜きポ
ンプ１１によつて残留する圧縮気体と共に、通路
２６Ａを介して吐出弁体８の吐出側に送られ、吐
出管４３を経て液体溜１２内に対して回収され
る。 Furthermore, as described above, the flow of compressed air in the discharge chamber 7 of the compressor 1 is stopped due to the closing operation of the intake blockage valve 5, and the check valve 8A is closed to prevent a small amount of lubricating oil from being injected into the compressor. However, this lubricating oil is sent from the liquid drain port 10 by the liquid drain pump 11 together with the remaining compressed gas through the passage 26A to the discharge side of the discharge valve body 8, and is then discharged from the discharge pipe. 43 and is collected into the liquid reservoir 12.
すると、前記吐出室７内の残留気体は拡散し、
圧力が０Kg／cm2圧力程度まで低下する。 Then, the residual gas in the discharge chamber 7 is diffused,
The pressure decreases to about 0 kg/cm 2 pressure.
これにより吐出口６に加わる背圧が除去される
から、圧縮機始動時の負荷が大幅に軽減された状
態で起動することになる。 This removes the back pressure applied to the discharge port 6, so that the compressor starts with a significantly reduced load upon starting.
以上の動作後、圧縮機は平常運転に移行する。
その後タイマー（図示せず）の動作により三方電
磁弁SV1及びSV2各々に通電され、回路３１と３
２は閉、代つて回路３６と３２は回路３５と３４
を介して吸入室４２に連通、回路３１と３３は連
通、代つて回路３３と３４は閉となりよつてアン
ローダピストン４４は図中右方向に移動し、吸気
閉塞弁５が開き圧縮機は全負荷運転に移行する。 After the above operations, the compressor shifts to normal operation.
Thereafter, the three-way solenoid valves SV 1 and SV 2 are energized by the operation of a timer (not shown), and the circuits 31 and 3 are energized.
2 is closed, circuits 36 and 32 are replaced by circuits 35 and 34
The circuits 31 and 33 are in communication with each other, and the circuits 33 and 34 are closed.The unloader piston 44 moves to the right in the figure, and the intake block valve 5 opens and the compressor is under full load. Shift to driving.
さらに圧力気槽兼液体槽４内の圧力が規定圧力
に達すると圧力スイツチPS1が動作し、平常運転
下に於ける無負荷運転状態に移行し、以降はその
繰返し動作を行なうことになるが、前記起動時の
負荷軽減状態は、当該無負荷状態に於いても同様
の作用で行なわれる。 Furthermore, when the pressure inside the pressure gas tank/liquid tank 4 reaches the specified pressure, the pressure switch PS 1 is activated, and the system shifts to a no-load operation state under normal operation, and this operation will be repeated thereafter. The load reduction state at the time of start-up is performed in the same manner even in the no-load state.
以上の動作に於て、吸気閉塞弁５が閉じ油量調
整弁２４が油量を絞つた所謂無負荷運転状態に於
て、前記吸気閉塞弁と油量調整弁との動作タイミ
ングによつては前記吐出室７内の圧力が−0.1
Kg／cm2ゲージ圧力程度まで低下することがあり、
これにより、一時的に液体抜きポンプ１１内にキ
ヤビテーシヨン現象が生じこれが振動源となつて
油通路２６の配管系統を振動させることがある
が、該配管系統は前記振動源と同一の振動系とし
て一体的に構成されている為これにより生ずる振
動は極めて小さいものである。 In the above operation, in the so-called no-load operating state in which the intake blockage valve 5 is closed and the oil amount adjustment valve 24 is restricting the oil amount, depending on the operation timing of the intake obstruction valve and the oil amount adjustment valve, The pressure inside the discharge chamber 7 is -0.1
The pressure may drop to about Kg/cm 2 gauge pressure.
As a result, a cavitation phenomenon temporarily occurs in the liquid drain pump 11, which becomes a vibration source and vibrates the piping system of the oil passage 26, but the piping system is integrated as the same vibration system as the vibration source. The vibrations caused by this are extremely small.
（考案の効果）
以上詳述したように本考案によれば回収通路２
６Ａを吐出室７の液体抜き口１０と吐出弁体８の
吐出側とに連通して圧縮機本体と同一の振動系と
して液体回収系統を構成しているので全負荷運転
とアンロード運転の繰返し時に於ても回収通路２
６Ａを形成する配管に生ずる振動も極めて小さく
できるから、従来のように高価な耐圧、高温用の
ゴムホースやこれに相当する高価な可撓管を用い
る必要もなくなり、安価な鋼管又は銅管を使用で
きるため、コストが引き下げられる。また、互い
に近傍箇所に位置する液体抜き口１０と吐出弁帯
８の吐出側とを接続するので、配管の長さが短く
くなり、取付スペースも小さいため配管作業が簡
単でかつコンパクトになる。(Effect of the invention) As detailed above, according to the invention, the collection passage 2
6A is connected to the liquid outlet 10 of the discharge chamber 7 and the discharge side of the discharge valve body 8, and the liquid recovery system is constructed as the same vibration system as the compressor main body, so full load operation and unload operation are repeated. Collection path 2 even at times
Since the vibration generated in the piping that forms the 6A can be extremely small, there is no need to use expensive pressure-resistant, high-temperature rubber hoses or equivalent expensive flexible tubes as in the past, and instead use inexpensive steel or copper tubes. This reduces costs. Furthermore, since the liquid outlet 10 and the discharge side of the discharge valve band 8 which are located close to each other are connected, the length of the piping is shortened and the installation space is also small, making the piping work simple and compact.
第１図は本考案による圧縮機の全体図、第２図
は従来の圧縮機の全体図を示す。
１……圧縮機、３……アンローダ装置、４……
圧力気槽兼液体槽、５……吸気閉塞弁、６……吐
出口、７……吐出室、８……吐出弁体、９……気
体口、１０……液体抜き口、１１……液体抜きポ
ンプ、１２……液体溜、１３……作用空間、２５
……油量調整弁、２６Ａ……回収通路。
FIG. 1 shows an overall view of a compressor according to the present invention, and FIG. 2 shows an overall view of a conventional compressor. 1... Compressor, 3... Unloader device, 4...
Pressure gas tank/liquid tank, 5...Intake blockage valve, 6...Discharge port, 7...Discharge chamber, 8...Discharge valve body, 9...Gas port, 10...Liquid outlet, 11...Liquid Bleeding pump, 12...Liquid reservoir, 13...Working space, 25
...Oil amount adjustment valve, 26A...Recovery passage.
Claims (1)
連動し、無負荷運転時圧縮機への潤滑油供給油量
を全負荷運転時以下に制限する油量調整弁と、前
記圧縮機の吐出室には吐出弁体を介して圧力空気
槽兼液体槽に連通する気体口と、該気体口より低
水準位置に液体抜き口を設け、運転中吐出口より
吐出された圧縮空気と潤滑油の混合流体中の圧縮
気体を前記気体口から圧力気槽兼液体槽へ、潤滑
油は前記液体抜き口より液体抜きポンプを介して
液体溜にそれぞれ常時圧入するように構成したス
クリユ圧縮機に於て、前記潤滑油を液体溜に回収
するための回収通路を前記液体抜き口より前記吐
出弁体の吐出側に連通し、前記回収通路を圧縮機
本体と同一振動系として配設したことを特徴とす
るスクリユ圧縮機の液体回収装置。 an oil amount adjustment valve that works in conjunction with a means for closing an intake blocking valve of the compressor at startup to limit the amount of lubricating oil supplied to the compressor during no-load operation to less than that during full-load operation; and a discharge chamber of the compressor. is equipped with a gas port that communicates with the compressed air tank and liquid tank via a discharge valve body, and a liquid drain port located at a lower level than the gas port, so that the compressed air and lubricating oil discharged from the discharge port are mixed during operation. In a screw compressor configured such that compressed gas in the fluid is constantly pressurized from the gas port to the pressure gas tank/liquid tank, and lubricating oil is constantly pressurized from the liquid drain port to the liquid reservoir via the liquid drain pump, A recovery passage for recovering the lubricating oil into a liquid reservoir is communicated from the liquid outlet to the discharge side of the discharge valve body, and the recovery passage is arranged as the same vibration system as the compressor main body. Liquid recovery device for screw compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10696586U JPH0227198Y2 (en) | 1986-07-11 | 1986-07-11 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10696586U JPH0227198Y2 (en) | 1986-07-11 | 1986-07-11 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6314887U JPS6314887U (en) | 1988-01-30 |
| JPH0227198Y2 true JPH0227198Y2 (en) | 1990-07-23 |
Family
ID=30982810
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10696586U Expired JPH0227198Y2 (en) | 1986-07-11 | 1986-07-11 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0227198Y2 (en) |
-
1986
- 1986-07-11 JP JP10696586U patent/JPH0227198Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6314887U (en) | 1988-01-30 |
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