JP2000314385A - Lubricating screw compressor - Google Patents
Lubricating screw compressorInfo
- Publication number
- JP2000314385A JP2000314385A JP11125567A JP12556799A JP2000314385A JP 2000314385 A JP2000314385 A JP 2000314385A JP 11125567 A JP11125567 A JP 11125567A JP 12556799 A JP12556799 A JP 12556799A JP 2000314385 A JP2000314385 A JP 2000314385A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- bearing
- suction
- side bearing
- temperature
- 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
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明はロータ室内に油を噴
射する給油式スクリュー圧縮機に関する。The present invention relates to an oil supply type screw compressor for injecting oil into a rotor chamber.
【0002】[0002]
【従来の技術】従来の給油式スクリュー圧縮機は実開昭
60−118390号記載のように、ケーシング内に雌雄一対の
スクリューロータを収め、オイルクーラで冷却した油を
ロータ室及び軸受に供給する。2. Description of the Related Art A conventional oil-filled screw compressor is actually open.
As described in JP-A-60-118390, a pair of male and female screw rotors are housed in a casing, and oil cooled by an oil cooler is supplied to a rotor chamber and a bearing.
【0003】ロータ室への給油は圧縮中のガスの冷却,
ロータ周りのすきまシール,ロータ接触回転の潤滑のた
めのもので、圧縮機から吐出した油と高圧ガスはオイル
セパレータで分離し、分離油は圧縮機本体側へと再循環
する。分離油の循環は油溜めを有するレシーバタンクと
ロータ室及び軸受位置での圧力差で行い、軸受からの排
油は吸込側及び吐出側共に吸い込み完了位置近傍のロー
タ室へ回収する。[0003] Oil supply to the rotor chamber cools the gas during compression,
The oil is separated from the compressor and the high-pressure gas by an oil separator, and the separated oil is recirculated to the compressor body. The separation oil is circulated by the pressure difference between the receiver tank having the oil reservoir, the rotor chamber and the bearing position, and the oil discharged from the bearing is recovered to the rotor chamber near the suction completion position on both the suction side and the discharge side.
【0004】給油式圧縮機でのロータ室及び軸受への油
はオイルクーラ出口で分岐するため、一定温度で給油す
る。また、圧縮機の性能を維持するため、給油温度は6
0℃程度である。[0004] The oil to the rotor chamber and the bearings in the oil supply type compressor is branched at the oil cooler outlet, and is supplied at a constant temperature. In order to maintain the performance of the compressor, the refueling temperature should be 6
It is about 0 ° C.
【0005】[0005]
【発明が解決しようとする課題】圧力比=8の空気圧縮
機においては、圧縮本体への給油温度は約60℃、油と
空気量の単位時間当たりの重量比は10:1程度で、吐
出温度は約75℃となる。このとき軸受温度は吐出側で
約70℃,吸込側で約60℃で、軸受温度は熱容量の大
きなロータに影響される。運転時の吸込側ロータ温度は
吸込温度である大気温度程度(≒20℃),吐出側ロー
タ温度は吐出温度程度(≒75℃)で、このロータ温度
が軸受温度に影響される。通常、軸受の信頼性の目安と
して軸受温度の上限を抑えており、吸込側軸受温度は余
裕がある。In an air compressor having a pressure ratio of 8, the oil supply temperature to the compression body is about 60 ° C., the weight ratio of oil to air per unit time is about 10: 1, and the discharge is The temperature will be about 75 ° C. At this time, the bearing temperature is about 70 ° C. on the discharge side and about 60 ° C. on the suction side, and the bearing temperature is affected by the rotor having a large heat capacity. During operation, the suction-side rotor temperature is about the atmospheric temperature (≒ 20 ° C.), which is the suction temperature, and the discharge-side rotor temperature is about the discharge temperature (≒ 75 ° C.). This rotor temperature is affected by the bearing temperature. Usually, the upper limit of the bearing temperature is suppressed as a measure of the reliability of the bearing, and there is room for the suction-side bearing temperature.
【0006】圧縮機の効率向上を図るには機械損失を低
減することが必要で、そのためには軸受の摩擦損失動力
を低減することである。軸受の摩擦損失動力は軸受での
油粘度に影響し、粘度が小さいほど軸受の摩擦損失動力
が小さくなる。しかしながら、従来の技術では吐出側及
び吸込側軸受とも一定温度で給油しているため、吸込側
軸受温度は吐出側軸受に比べ低く、吸込側軸受の摩擦損
失動力が高めであった。[0006] In order to improve the efficiency of the compressor, it is necessary to reduce the mechanical loss. For that purpose, it is necessary to reduce the friction loss power of the bearing. The friction loss power of the bearing affects the oil viscosity in the bearing, and the lower the viscosity, the smaller the friction loss power of the bearing. However, in the prior art, since the oil is supplied at a constant temperature to both the discharge side and the suction side bearing, the temperature of the suction side bearing is lower than that of the discharge side bearing, and the friction loss power of the suction side bearing is high.
【0007】本発明は前記した従来技術の問題点を解決
することにある。An object of the present invention is to solve the above-mentioned problems of the prior art.
【0008】[0008]
【課題を解決するための手段】本発明では、吸込側軸受
と吐出側軸受の温度をほぼ同じくするため、吐出側軸受
室と吸込側軸受給油孔を配管などで連結し、吐出側軸受
から高温となった排油を吸込側軸受へ供給する。According to the present invention, in order to make the temperature of the suction side bearing and the temperature of the discharge side bearing substantially the same, the discharge side bearing chamber and the suction side bearing lubrication hole are connected by piping or the like, and the temperature of the discharge side bearing is increased. Is supplied to the suction-side bearing.
【0009】[0009]
【発明の実施の形態】以下、本発明の実施の形態を図
1,図2を参照して説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.
【0010】図1に本発明の給油式スクリュー圧縮機の
全体構成を示す。圧縮機本体1の吐出側は配管2によっ
てレシーバタンク3と連結され、さらにレシーバタンク
3の上部からはオイルセパレータ4,アフタークーラ5
の順に配管6,7によってそれぞれ連結されている。レ
シーバタンク3の下部は油溜めになっており、オイルク
ーラ8を介し、圧縮機本体1と連結されている。連結は
配管9,10による。圧縮機本体1のケーシングはMケ
ーシング11とDケーシング12とからなり、Mケーシ
ング11には雄ロータ13と雌ロータ14が噛み合って
収まっている。雄,雌ロータ13,14の両端は吸込側
ラジアル軸受15a,15b及び吐出側ラジアル軸受1
6a,16bで支持され、吐出側にはスラスト荷重を受
けるスラスト軸受17a,17bを設けている。吐出側
軸受16a,16b,17a,17bはDカバー18,
吸込側軸受15a,15bはSカバー19で被われ、吸
込側雄ロータ13軸には外部と遮断するメカニカルシー
ル20が設けてある。FIG. 1 shows the overall structure of a refueling screw compressor according to the present invention. The discharge side of the compressor body 1 is connected to a receiver tank 3 by a pipe 2, and an oil separator 4, an aftercooler 5
In this order by pipes 6 and 7. The lower part of the receiver tank 3 is an oil reservoir, and is connected to the compressor body 1 via an oil cooler 8. The connection is through pipes 9 and 10. The casing of the compressor body 1 is composed of an M casing 11 and a D casing 12, and a male rotor 13 and a female rotor 14 are fitted in the M casing 11 and fitted therein. Both ends of the male and female rotors 13 and 14 have suction side radial bearings 15a and 15b and discharge side radial bearings 1 respectively.
Thrust bearings 17a and 17b supported by 6a and 16b and receiving a thrust load are provided on the discharge side. The discharge side bearings 16a, 16b, 17a, and 17b are D covers 18,
The suction-side bearings 15a and 15b are covered with an S cover 19, and a mechanical seal 20 is provided on the shaft of the suction-side male rotor 13 to shut off the outside.
【0011】Mケーシング11にはロータ給油孔21,
吸込側軸受給油孔22,排油孔23、及び吸込口24,
Dケーシング12には吐出側軸受給油孔25a,25
b,吐出口26が形成され、Sカバー19にはメカニカ
ルシール給油孔27,Dカバー18には排油孔28が形
成されている。The M casing 11 has a rotor oil supply hole 21,
The suction-side bearing oil supply hole 22, the oil drain hole 23, and the suction port 24,
In the D casing 12, the discharge side bearing oil supply holes 25a, 25
b, a discharge port 26 is formed, a mechanical seal oil supply hole 27 is formed in the S cover 19, and an oil discharge hole 28 is formed in the D cover 18.
【0012】次に、このように構成された給油式スクリ
ュー圧縮機の動作について説明する。雄ロータ13がモ
ータなどによって駆動されると、雄ロータ13と噛み合
う雌ロータ14も回転する。Next, the operation of the oil-filled screw compressor having the above-described structure will be described. When the male rotor 13 is driven by a motor or the like, the female rotor 14 meshing with the male rotor 13 also rotates.
【0013】これにより吸込口24から空気は吸い込
み、さらに圧縮を行う。圧縮中は給油孔21から油を噴
射し、圧縮過程を等温圧縮に近づける。圧縮機1から吐
出した空気には多量の油が含まれており、レシーバタン
ク3で空気と油の一次分離を行う。さらにオイルセパレ
ータ4で空気と油の二次分離を行い、アフタークーラ5
で高圧空気を冷却し、油のないクリーンな高圧空気とし
て使用される。As a result, air is sucked in from the suction port 24 and further compressed. During compression, oil is injected from the oil supply hole 21 to bring the compression process closer to isothermal compression. The air discharged from the compressor 1 contains a large amount of oil, and the receiver tank 3 performs primary separation of the air and the oil. Further, the oil separator 4 performs a secondary separation of air and oil, and the aftercooler 5
It cools high-pressure air and is used as clean high-pressure air without oil.
【0014】レシーバタンク3での空気と油の一次分離
によって分離された油は重力で落下する。レシーバタン
ク3の下部は油溜めとなっており、レシーバタンク圧と
圧縮機本体給油位置との圧力差で圧縮機本体1へ給油さ
れる。圧力比=8の空気圧縮機においては、給油温度約
60℃、油と空気量の単位時間当たりの重量比を10:
1程度で、吐出温度は75℃程度となる。レシーバタン
ク3での油溜めの油温は吐出温度の約75℃で、オイル
クーラ8通過後の油温度は約60℃となる。The oil separated by primary separation of air and oil in the receiver tank 3 falls by gravity. The lower part of the receiver tank 3 is an oil reservoir, and is supplied to the compressor body 1 by a pressure difference between the receiver tank pressure and the compressor body refueling position. In an air compressor with a pressure ratio = 8, the oil supply temperature is about 60 ° C., and the weight ratio of oil and air per unit time is 10:
At about 1, the discharge temperature is about 75 ° C. The oil temperature of the oil reservoir in the receiver tank 3 is about 75 ° C. of the discharge temperature, and the oil temperature after passing through the oil cooler 8 is about 60 ° C.
【0015】圧縮本体1への給油は配管10aからロー
タ給油孔21を介してのロータ室29への給油と、配管
10bから軸受給油孔25を介しての吐出側軸受16,
17への給油,配管10cから給油孔27を介してのメ
カニカルシール20への給油とがある。吐出側軸受1
6,17への給油は吐出側での軸封30a,30bも兼
ねており、軸受16,17を通過後、Dカバー18内に
排出される。この油は戻り管31を通って吸込側軸受給
油孔22に導き、吸込側軸受15通過後、吸込み行程の
ロータ室29へ回収される。Oil is supplied to the compression main body 1 from the pipe 10a to the rotor chamber 29 via the rotor oil hole 21 and from the pipe 10b to the discharge-side bearings 16, via the bearing oil hole 25.
17 and oil supply from the pipe 10 c to the mechanical seal 20 via the oil supply hole 27. Discharge side bearing 1
The oil supply to the cylinders 6 and 17 also serves as the shaft seals 30a and 30b on the discharge side, and is discharged into the D cover 18 after passing through the bearings 16 and 17. This oil is guided to the suction-side bearing oil supply hole 22 through the return pipe 31, and is recovered to the rotor chamber 29 in the suction stroke after passing through the suction-side bearing 15.
【0016】このように吸込側軸受15への給油温度は
吐出側軸受16,17への給油温度に比べ高いが、ロー
タ温度の影響(吐出側で高く,吸込側で低い)を及ぼ
し、吐出側軸受16,17及び吸込側軸受15の温度は
同程度となる。したがって、従来の給油系に比べ、吸込
側軸受15での油粘度を高めることができ、吸込側軸受
15の摩擦損失動力を低減することができる。As described above, the oil supply temperature to the suction-side bearing 15 is higher than the oil supply temperature to the discharge-side bearings 16 and 17, but is affected by the rotor temperature (high on the discharge side and low on the suction side). The temperatures of the bearings 16 and 17 and the suction-side bearing 15 are substantially the same. Therefore, the oil viscosity in the suction side bearing 15 can be increased as compared with the conventional oil supply system, and the friction loss power of the suction side bearing 15 can be reduced.
【0017】[0017]
【発明の効果】本発明によれば吐出側軸受の排油を十分
に回収することができ、軸受の信頼性を損なうことな
く、吸込側軸受での油粘度を高め、吸込側軸受の摩擦損
失動力を低減させ、さらには圧縮機効率を高めることが
できる。According to the present invention, it is possible to sufficiently recover the drain oil of the discharge side bearing, to increase the oil viscosity in the suction side bearing without deteriorating the reliability of the bearing, and to reduce the friction loss of the suction side bearing. Power can be reduced, and compressor efficiency can be increased.
【図1】本発明の給油式スクリュー圧縮機の縦断面図と
全体構成を示す図。FIG. 1 shows a longitudinal sectional view and an overall configuration of a refueling screw compressor according to the present invention.
【図2】本発明の給油式スクリュー圧縮機の横断面図。FIG. 2 is a cross-sectional view of the oil supply type screw compressor of the present invention.
15…吸込側ラジアル軸受、16…吐出側ラジアル軸
受、17…吐出側スラスト軸受、21…ロータ給油孔、
22…吸込側軸受給油孔、23,28…排油孔、25…
吐出側軸受給油孔、31…戻り管。15: suction side radial bearing, 16: discharge side radial bearing, 17: discharge side thrust bearing, 21: rotor oil supply hole,
22 ... suction side bearing oil supply holes, 23, 28 ... oil drain holes, 25 ...
Discharge side bearing lubrication hole, 31 ... return pipe.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 青木 優和 静岡県清水市村松390番地 株式会社日立 製作所産業機器グループ内 Fターム(参考) 3H029 AA03 AA15 AA21 AB02 BB12 BB35 BB42 CC17 CC22 CC33 CC44 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Yuka Aoki 390 Muramatsu, Shimizu-shi, Shizuoka F-term in the Industrial Equipment Group, Hitachi, Ltd. 3H029 AA03 AA15 AA21 AB02 BB12 BB35 BB42 CC17 CC22 CC33 CC44
Claims (1)
タを収め、ケーシングの一方に吸込口,他方に吐出口を
形成し、スクリューロータの両端を軸受で支持した給油
式スクリュー圧縮機において、吐出側軸受室と吸込側軸
受給油孔を通路で連結したことを特徴とした給油式スク
リュー圧縮機。An oil-filled screw compressor in which a pair of male and female screw rotors are housed in a casing, an inlet is formed in one of the casings, and a discharge port is formed in the other, and both ends of the screw rotor are supported by bearings. A refueling screw compressor characterized in that a chamber and a suction-side bearing lubrication hole are connected by a passage.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11125567A JP2000314385A (en) | 1999-05-06 | 1999-05-06 | Lubricating screw compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11125567A JP2000314385A (en) | 1999-05-06 | 1999-05-06 | Lubricating screw compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2000314385A true JP2000314385A (en) | 2000-11-14 |
Family
ID=14913399
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP11125567A Pending JP2000314385A (en) | 1999-05-06 | 1999-05-06 | Lubricating screw compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2000314385A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE1014642A3 (en) * | 2002-02-14 | 2004-02-03 | Atlas Copco Airpower Nv | Oil injected screw compressor component, has second groove provided in rotor shaft to improve rotor shaft bearing lubrication |
JP2005308330A (en) * | 2004-04-22 | 2005-11-04 | Kobe Steel Ltd | Screw refrigeration unit |
JP2009293593A (en) * | 2008-06-09 | 2009-12-17 | Mitsubishi Electric Corp | Screw compressor and its maintenance method |
CN114412785A (en) * | 2022-03-28 | 2022-04-29 | 天津捷盛东辉保鲜科技有限公司 | Wide-temperature-range constant-temperature rotor type double-screw refrigeration compressor |
-
1999
- 1999-05-06 JP JP11125567A patent/JP2000314385A/en active Pending
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE1014642A3 (en) * | 2002-02-14 | 2004-02-03 | Atlas Copco Airpower Nv | Oil injected screw compressor component, has second groove provided in rotor shaft to improve rotor shaft bearing lubrication |
JP2005308330A (en) * | 2004-04-22 | 2005-11-04 | Kobe Steel Ltd | Screw refrigeration unit |
JP4546136B2 (en) * | 2004-04-22 | 2010-09-15 | 株式会社神戸製鋼所 | Screw refrigeration equipment |
JP2009293593A (en) * | 2008-06-09 | 2009-12-17 | Mitsubishi Electric Corp | Screw compressor and its maintenance method |
CN114412785A (en) * | 2022-03-28 | 2022-04-29 | 天津捷盛东辉保鲜科技有限公司 | Wide-temperature-range constant-temperature rotor type double-screw refrigeration compressor |
CN114412785B (en) * | 2022-03-28 | 2022-07-15 | 天津捷盛东辉保鲜科技有限公司 | Wide-temperature-range constant-temperature rotor type double-screw refrigeration compressor |
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