JP2000110760A - Oil cooled screw compressor - Google Patents
Oil cooled screw compressorInfo
- Publication number
- JP2000110760A JP2000110760A JP10280674A JP28067498A JP2000110760A JP 2000110760 A JP2000110760 A JP 2000110760A JP 10280674 A JP10280674 A JP 10280674A JP 28067498 A JP28067498 A JP 28067498A JP 2000110760 A JP2000110760 A JP 2000110760A
- Authority
- JP
- Japan
- Prior art keywords
- pressure stage
- low
- casing
- rotor
- stage
- 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
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は雄ロータ及び雌ロー
タ対を２組有する油冷式の圧縮機に係り、特に２組のロ
ータ対を同一ケーシングに収納する油冷式スクリュー圧
縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil-cooled compressor having two pairs of male and female rotors, and more particularly to an oil-cooled screw compressor in which two pairs of rotors are housed in the same casing.
【０００２】[0002]
【従来の技術】従来の油冷式２段スクリュー圧縮機で
は、特開平8-109887号公報に記載のように低圧段と高圧
段のロータおよびケーシングをタンデムに配列してい
た。また、特開昭48-21806号公報に記載のように、１つ
のケーシング内に高圧段及び低圧段のロータを収納して
いた。2. Description of the Related Art In a conventional oil-cooled two-stage screw compressor, rotors and casings of a low-pressure stage and a high-pressure stage are arranged in tandem as described in Japanese Patent Application Laid-Open No. 8-109887. Further, as described in JP-A-48-21806, the rotors of the high pressure stage and the low pressure stage are housed in one casing.
【０００３】[0003]
【発明が解決しようとする課題】２段に構成された油冷
式のスクリュー圧縮機では、特開平8-109887号公報に記
載のように低圧段と高圧段のロータおよびケーシングを
タンデムに配列すると、ロータ軸方向の寸法が長くなり
機器の小型化の面で不十分であった。また、この公報に
記載のものは、ロータ軸がモータに直結されているので
ロータの設定回転数を変更することが困難であり、圧縮
機の仕様毎に異なった諸元のロータを製作する必要があ
った。In an oil-cooled screw compressor having two stages, a rotor and a casing of a low-pressure stage and a high-pressure stage are arranged in tandem as described in JP-A-8-109887. However, the size in the axial direction of the rotor becomes longer, which is insufficient in terms of miniaturization of equipment. Further, since the rotor described in this publication has a rotor shaft directly connected to the motor, it is difficult to change the set number of rotations of the rotor, and it is necessary to manufacture a rotor having different specifications for each compressor specification. was there.
【０００４】特開昭48-21806号公報に記載のものは、ロ
ータ軸方向の寸法は比較的短く抑えられているが、高圧
段と低圧段の吐出方向が逆向きであり、組立て時に反転
を繰り返しながら、スラスト荷重を負荷するアンギュラ
玉軸受を取付ける必要があった。また、圧縮機のメンテ
ナンス時にロータをケーシングから抜き取る際に、高圧
段と低圧段いずれかを駆動軸方向に引き抜く必要があ
り、原動機をあらかじめ移動しておく等の余分な作業が
必要であった。特に、2段圧縮機は１５０ｋＷ以上の大
型機が一般的であり、これらの作業性の悪さはメンテナ
ンスコストの大幅な上昇につながる。Japanese Patent Application Laid-Open No. 48-21806 discloses that the dimension in the rotor axis direction is relatively short, but the discharge directions of the high-pressure stage and the low-pressure stage are opposite, and the assembly is reversed during assembly. Repeatedly, it was necessary to install an angular contact ball bearing for applying a thrust load. In addition, when removing the rotor from the casing during maintenance of the compressor, it is necessary to pull out either the high-pressure stage or the low-pressure stage in the direction of the drive shaft, which requires extra work such as moving the prime mover in advance. In particular, large compressors of 150 kW or more are generally used as the two-stage compressor, and such poor workability leads to a large increase in maintenance cost.
【０００５】２段圧縮機では、低圧段のロータを１サイ
ズまたは２サイズ大型の機種の高圧段のロータに使用し
て部品の共通化を図っている。低圧段と高圧段の各軸端
にピニオンギヤを設け、それぞれを共通のブルギヤで駆
動する場合には、高圧段と低圧段の捩れ方向を逆に加工
する必要がある。そのため、ロータのシリーズ設計を行
う上で共通化が困難である。In a two-stage compressor, a low-pressure stage rotor is used for a high-pressure stage rotor of one or two size large-sized models to achieve commonality of parts. When a pinion gear is provided at each shaft end of the low-pressure stage and the high-pressure stage, and each is driven by a common bull gear, it is necessary to machine the torsional directions of the high-pressure stage and the low-pressure stage in reverse. Therefore, it is difficult to standardize the rotors when designing the series.
【０００６】本発明上記従来技術の不具合に鑑みなされ
たものであり、その目的は、小型コンパクトな２段の油
冷式スクリュー圧縮機を提供することにある。本発明の
他の目的は、ロータのシリーズ設計や部品の共通化が容
易な２段の油冷式スクリュー圧縮機を提供することにあ
る。本発明のさらに他の目的は、メンテナンスの容易な
２段の油冷式スクリュー圧縮機を提供することにある。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned disadvantages of the related art, and has as its object to provide a small and compact two-stage oil-cooled screw compressor. Another object of the present invention is to provide a two-stage oil-cooled screw compressor in which the series design of rotors and the common use of parts are easy. Still another object of the present invention is to provide a two-stage oil-cooled screw compressor that is easy to maintain.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するため
の本発明の第１の特徴は、同一のケーシング内に雄ロー
タと雌ロータの対を2組回転自在に収納し、一方のロー
タ対が低圧段、他方のロータ対が高圧段を形成する油冷
式スクリュー圧縮機において、低圧段は作動ガスの吸込
み方向がラジアル方向であり、高圧段は作動ガスの吸込
み方向がアキシャル方向となるようにしたものである。
そして好ましくは、高圧段と低圧段は、ともに吐出方向
が軸方向であるものである。A first feature of the present invention to achieve the above object is that two pairs of a male rotor and a female rotor are rotatably housed in the same casing, and one of the rotor pairs is accommodated. In the oil-cooled screw compressor in which the low pressure stage and the other rotor pair form a high pressure stage, the suction direction of the working gas in the low pressure stage is the radial direction, and the suction direction of the working gas in the high pressure stage is the axial direction. It was made.
Preferably, the high-pressure stage and the low-pressure stage both have an axial discharge direction.
【０００８】また好ましくは、ケーシングの上部に低圧
段をなす雄ロータと雌ロータ対を水平に配列し、低圧段
から吐出される吐出ガスを高圧段に導く通路を前記ロー
タ対の下部に配置し、さらにその下部に高圧段の雄ロー
タと雌ロータ対を水平に配列したものである。より好ま
しくは、ケーシングの吐出側に、高圧段のロータ対を支
持する軸受を保持する高圧段Ｄケーシングと、低圧段の
ロータ対を支持する軸受を保持する低圧段Ｄケーシング
とを設け、この低圧段Ｄケーシングに、低圧段から吐出
される吐出ガスをケーシングの中段に形成された通路に
導く空間形成し、高圧段Ｄケーシングには吐出口を形成
したものである。Preferably, a male rotor and a female rotor pair forming a low pressure stage are horizontally arranged at an upper portion of a casing, and a passage for guiding discharge gas discharged from the low pressure stage to a high pressure stage is arranged at a lower portion of the rotor pair. Further, a male rotor and a female rotor pair of a high-pressure stage are horizontally arranged at a lower portion thereof. More preferably, on the discharge side of the casing, a high-pressure stage D casing that holds a bearing that supports the high-pressure stage rotor pair and a low-pressure stage D casing that holds a bearing that supports the low-pressure stage rotor pair are provided. A space is formed in the stage D casing to guide the discharge gas discharged from the low pressure stage to a passage formed in the middle stage of the casing, and a discharge port is formed in the high pressure stage D casing.
【０００９】このように構成することで、圧縮機本体の
ロータ軸方向寸法を従来のタンデム配置の圧縮機より大
幅に短くした。また、一般的に高圧段ロータは低圧段ロ
ータよりも短いから、高圧段と低圧段のロータ長さの差
を利用して各段の吸込ポートを設けて、軸方向の長さを
極力低減した。さらに、吐出側のスラスト軸受を収納す
るＤケーシングを高圧段と低圧段とで別個に設けた。With this configuration, the size of the compressor body in the rotor axial direction is significantly shorter than that of a conventional tandem compressor. In addition, since the high-pressure stage rotor is generally shorter than the low-pressure stage rotor, the suction port of each stage is provided by utilizing the difference in rotor length between the high-pressure stage and the low-pressure stage, and the axial length has been reduced as much as possible. . Further, a D casing for accommodating the thrust bearing on the discharge side is separately provided for the high pressure stage and the low pressure stage.
【００１０】[0010]
【発明の実施の形態】以下、本発明の一実施例を図面を
用いて説明する。図１は、本発明に係る油冷式２段スク
リュー圧縮機の縦断面図であり、図２は、図１のＡ−Ａ
断面図である。油冷式スクリュー圧縮機は、低圧段部分
と高圧段部分がケーシングを共有している。低圧段部分
はケーシング１の上部に配置されており、低圧段雄ロー
タ２と低圧段雌ロータ３は、円筒ころ軸受７により吸込
側の軸部を回転自在に支承されている。また、アンギュ
ラ玉軸受１３により吐出側の軸部を回転自在に支承され
ている。そしてこれらの軸受７、１３は、ケーシング１
に保持されている。低圧段に吸込まれる作動ガスは、低
圧段のロータ２、３のラジアル方向から吸込まれる。す
なわち、吸込ガスは、ケーシング１の上部に設けられた
吸込口６から、回転する低圧段ロータ２、３の歯溝にラ
ジアル方向から流入する。本実施例においては、低圧段
ロータ２、３の吸込側の軸部に対応するケーシング部分
の軸方向長さは、円筒ころ軸受７を取付ける長さだけあ
ればよい。DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view of an oil-cooled two-stage screw compressor according to the present invention, and FIG.
It is sectional drawing. In the oil-cooled screw compressor, the low-pressure stage and the high-pressure stage share a casing. The low-pressure step portion is arranged on the upper part of the casing 1, and the low-pressure step male rotor 2 and the low-pressure step female rotor 3 are rotatably supported by a cylindrical roller bearing 7 on a suction-side shaft. Further, a shaft on the discharge side is rotatably supported by an angular ball bearing 13. These bearings 7 and 13 are
Is held in. The working gas sucked into the low pressure stage is sucked from the low pressure stage rotors 2 and 3 in the radial direction. That is, the suction gas flows from the suction port 6 provided in the upper part of the casing 1 into the tooth spaces of the rotating low-pressure stage rotors 2 and 3 in the radial direction. In the present embodiment, the axial length of the casing portion corresponding to the suction-side shaft portions of the low-pressure stage rotors 2 and 3 only needs to be the length in which the cylindrical roller bearing 7 is mounted.
【００１１】スクリュー圧縮機において、ラジアル方向
からガスを吸い込むものでは、高温の吐出側のガスと潤
滑油がロータ間の噛み合い隙間からラジアル方向の吸込
ポートへ漏れると、吸込ガスの温度を上昇させて体積効
率を低下させる場合がある。本実施例においては、２段
圧縮機として各段の圧縮比を小さくしているので、この
影響をほとんど無視できる。しかも、大型の圧縮機に適
用されることが多い２段圧縮機では、大量の吸込ガスを
扱うので、吸込ガスの流れ方向を１８０度転換する必要
のあるアキシャル吸込構造よりもラジアル吸込の方が吸
込み抵抗が小さい。その結果、限られたスペースで高い
吸込効率を達成することができる。In a screw compressor in which gas is sucked from the radial direction, when the high-temperature discharge-side gas and lubricating oil leak from the meshing gap between the rotors to the radial suction port, the temperature of the suction gas is increased. Volumetric efficiency may be reduced. In this embodiment, since the compression ratio of each stage is reduced as a two-stage compressor, this effect can be almost ignored. Moreover, in a two-stage compressor which is often applied to a large compressor, a large amount of suction gas is handled, so that the radial suction is more effective than the axial suction structure which needs to change the flow direction of the suction gas by 180 degrees. Low suction resistance. As a result, high suction efficiency can be achieved in a limited space.
【００１２】圧縮機内に吸込まれた作動ガスは、低圧段
における圧縮過程で潤滑油が注入される。低圧段の雄ロ
ータ２と雌ロータ３により形成される圧縮室内で圧縮さ
れた作動ガスは、ケーシングの低圧段側のロータ挿入部
の壁面に形成された低圧段ラジアル方向吐出ポート８と
低圧段Ｄケーシング１７のロータ吐出側端面に形成され
た低圧段アキシャル方向吐出ポート９を出て、ケーシン
グの低圧段と高圧段に挟まれた空間である中間段通路１
０へ流入する。The working gas sucked into the compressor is injected with lubricating oil during the compression process in the low pressure stage. The working gas compressed in the compression chamber formed by the male rotor 2 and the female rotor 3 of the low-pressure stage is supplied to a low-pressure stage radial discharge port 8 formed on the wall of the rotor insertion portion on the low-pressure stage side of the casing. The intermediate stage passage 1 exits from the low-pressure stage axial direction discharge port 9 formed on the rotor discharge-side end face of the casing 17 and is a space between the low-pressure stage and the high-pressure stage of the casing.
Flow into zero.
【００１３】中間段通路１０へも潤滑油が噴射され、圧
縮ガスを冷却する。中間段通路１０は高圧段のロータ
４、５の長さに相当するだけ形成する。中間段を流れる
間に十分にガスと噴射される油が熱交換され、中間冷却
の効果が上げられ、圧縮機が高い効率を達成できる。中
間段で冷却されたガスは、高圧段の吸込ポート１１で流
れの向きを変えられ、高圧段ロータのアキシャル方向か
ら高圧段雄ロータ４と高圧段雌ロータ５が形成する空間
に吸込まれる。Lubricating oil is also injected into the intermediate stage passage 10 to cool the compressed gas. The intermediate stage passage 10 is formed to correspond to the length of the high-pressure stage rotors 4 and 5. During the flow through the intermediate stage, the gas and the injected oil are sufficiently heat-exchanged, the effect of the intermediate cooling is increased, and the compressor can achieve high efficiency. The flow of the gas cooled in the intermediate stage is changed by the suction port 11 of the high-pressure stage, and is sucked into the space formed by the high-pressure stage male rotor 4 and the high-pressure stage female rotor 5 from the axial direction of the high-pressure stage rotor.
【００１４】高圧段部分はケーシング１の下部に配置さ
れており、高圧段雄ロータ４と雌ロータ５は円筒ころ軸
受１２により吸込側の軸部を回転自在に支承され、アン
ギュラ玉軸受１４により吐出側の軸ぶを回転自在に支承
されている。低圧段と同様に、軸受１２、１４は、ケー
シング１内に保持されている。中間段から高圧段の吸込
部にいたる通路には、すでに低圧段で昇圧されたガスが
流入する。したがって、流速は低圧段吸込状態の１／３
程度かあるいはそれ以下まで低下しており、アキシャル
吸込の場合に生じる通路の曲がり等に起因する圧力損失
を無視できる。The high-pressure step portion is disposed at the lower portion of the casing 1. The high-pressure step male rotor 4 and the female rotor 5 are rotatably supported on a suction-side shaft by a cylindrical roller bearing 12, and are discharged by an angular ball bearing 14. The side shaft is rotatably supported. As in the low pressure stage, the bearings 12, 14 are held in the casing 1. The gas already pressurized at the low pressure stage flows into the passage from the intermediate stage to the suction section of the high pressure stage. Therefore, the flow velocity is 1/3 of the low pressure stage suction state.
The pressure loss is reduced to about or below, and the pressure loss due to the bending of the passage and the like generated in the case of the axial suction can be ignored.
【００１５】中間段通路を通過したガスを１８０度方向
転換するために、高圧段の吸込側に方向転換部を設け
る。これは、高圧段のロータが低圧段のロータより短い
から、この差を利用するものである。そして、この場所
に方向転換部を設けると、高圧段と低圧段の吐出側の端
面をほぼ同一面に揃えることも可能になる。この結果、
ケーシングの小型化および加工の容易化が図れる。In order to change the direction of the gas passing through the intermediate stage passage by 180 degrees, a direction changing portion is provided on the suction side of the high pressure stage. This utilizes this difference because the rotor at the high pressure stage is shorter than the rotor at the low pressure stage. When the direction change portion is provided at this location, the end faces on the discharge side of the high-pressure stage and the low-pressure stage can be made substantially flush with each other. As a result,
The casing can be reduced in size and processing can be facilitated.
【００１６】高圧段の雄ロータ４と雌ロータ５間に形成
される圧縮室でさらに所定の圧力まで昇圧された作動ガ
スは、ケーシング１の高圧段側のロータ挿入部の壁面に
形成された高圧段ラジアル方向吐出ポート１５と高圧段
Ｄケーシングのロータ吐出側端面に形成された高圧段ア
キシャル方向吐出ポート１６から流出し、高圧段Ｄケー
シング１８に形成した吐出口から吐出される。The working gas, which has been further pressurized to a predetermined pressure in the compression chamber formed between the male rotor 4 and the female rotor 5 in the high pressure stage, is supplied to the high pressure stage formed on the wall of the rotor insertion portion of the casing 1 on the high pressure stage side. It flows out from the step radial direction discharge port 15 and the high pressure step axial direction discharge port 16 formed on the rotor discharge side end face of the high pressure step D casing, and is discharged from a discharge port formed in the high pressure step D casing 18.
【００１７】なお、本実施例においては、各段のロータ
の吸込方向と吐出方向を同一にしているので、ロータに
作用するスラスト荷重を負担するアンギュラ玉軸受１
３、１４をＤケーシングに収容している。このＤケーシ
ングはロータを収容するケーシングとは別個に設けられ
ている。そして、低圧段のＤケーシング１７と高圧段の
Ｄケーシング１８とは別体にしている。In this embodiment, since the suction direction and the discharge direction of the rotor in each stage are the same, the angular contact ball bearing 1 which bears the thrust load acting on the rotor.
3 and 14 are housed in a D casing. This D casing is provided separately from the casing that houses the rotor. The low-pressure stage D casing 17 and the high-pressure stage D casing 18 are separately provided.
【００１８】低圧段のＤケーシング１７には低圧段アキ
シャル方向吐出ポート９が形成されており、この吐出ポ
ート９はケーシング１の中間段通路１０へ連通する働き
もする。A low-pressure stage axial casing discharge port 9 is formed in the low-pressure stage D casing 17, and the discharge port 9 also serves to communicate with the intermediate stage passage 10 of the casing 1.
【００１９】本実施例によれば、高圧段ロータ４，５の
み、または低圧段ロータ２，３のみを分解することが可
能である。さらに、ロータを分解するためには駆動軸と
反対の１方向だけ分解すればよく、ロータを抜出す作業
が容易になる。もちろん、組立て時にも同様に高圧段と
低圧段を同じ方向から組み立てればよく、メンテナンス
性能を向上するのみならず製造時のコストをも低減でき
る。According to this embodiment, it is possible to disassemble only the high-pressure stage rotors 4 and 5 or only the low-pressure stage rotors 2 and 3. Further, in order to disassemble the rotor, it is sufficient to disassemble only in one direction opposite to the drive shaft, and the work of extracting the rotor becomes easy. Of course, at the time of assembly, the high-pressure stage and the low-pressure stage may be similarly assembled from the same direction, so that not only the maintenance performance is improved but also the manufacturing cost can be reduced.
【００２０】高圧段と低圧段のロータをロータの捩れ方
向が同一の相似形状とすることができるので、ロータの
共用化設計が容易である。また、図示しない原動機の回
転数を高圧段及び低圧段のロータの回転数に設定するた
めに、歯車変速手段を用いている。この歯車変速手段
は、駆動軸２３に取付けられたまたは形成されたブルギ
ヤ１９と、このブルギヤに噛み合い所望の増速比が得ら
れるピニオンギヤ２０、２１とからなり、これらギヤ１
９、２０、２１は、ケーシング１に隣接して設けたギヤ
ーケーシング２２で覆われている。なお、ピニオンギヤ
２０、２１は、低圧段及び高圧段の雄ロータ軸端に取付
ける。ギヤ１９、２０、２１の歯数を適宜組合わせるこ
とにより、原動機の回転数を所望の設計回転数に容易に
設定できる。Since the rotors of the high-pressure stage and the low-pressure stage can have similar shapes in which the torsional directions of the rotor are the same, it is easy to design the rotor in common. In order to set the rotation speed of the prime mover (not shown) to the rotation speeds of the rotors of the high-pressure stage and the low-pressure stage, a gear transmission is used. The gear shifting means comprises a bull gear 19 attached to or formed on a drive shaft 23, and pinion gears 20, 21 which mesh with the bull gear to obtain a desired speed increase ratio.
9, 20 and 21 are covered with a gear casing 22 provided adjacent to the casing 1. The pinion gears 20 and 21 are attached to the male rotor shaft ends of the low pressure stage and the high pressure stage. By appropriately combining the number of teeth of the gears 19, 20, and 21, the rotation speed of the prime mover can be easily set to a desired design rotation speed.
【００２１】[0021]
【発明の効果】本発明によれば、油冷式スクリュー圧縮
機において、低圧段ではラジアル方向から作動ガスを吸
い込み、高圧段ではアキシャル方向からガスを吸い込ん
でいるので、高効率でかつ軸方向にコンパクトな油冷式
スクリュー圧縮機が得られる。また、本発明によれば、
メンテナンスが容易な油冷式スクリュー圧縮機を得るこ
とができる。さらに、本発明によれば、ロータのシリー
ズ化設計が容易であり、部品の共通化による製造コスト
の低減も可能である。According to the present invention, in the oil-cooled screw compressor, the working gas is sucked from the radial direction at the low pressure stage, and the gas is sucked from the axial direction at the high pressure stage. A compact oil-cooled screw compressor is obtained. According to the present invention,
An oil-cooled screw compressor with easy maintenance can be obtained. Further, according to the present invention, it is easy to design a series of rotors, and it is possible to reduce the manufacturing cost by using common components.
【図１】本発明に係る油冷式スクリュー圧縮機の一実施
例の縦断面図。FIG. 1 is a longitudinal sectional view of one embodiment of an oil-cooled screw compressor according to the present invention.
【図２】図１に示した油冷式スクリュー圧縮機のＡ−Ａ
断面図。FIG. 2 is a sectional view of the oil-cooled screw compressor shown in FIG.
Sectional view.
１；ケーシング、２；低圧段雄ロータ、３；低圧段雌ロ
ータ、４；高圧段雄ロータ、５；高圧段雌ロータ、６；
吸込口、７；円筒ころ軸受、８；低圧段ラジアル吐出ポ
ート、９；低圧段アキシャル吐出ポート、１０；中間段
通路、１１；高圧段吸込ポート、１２；円筒ころ軸受、
１３；アンギュラ玉軸受、１４；アンギュラ玉軸受、１
５；高圧段ラジアル吐出ポート、１６；高圧段アキシャ
ル吐出ポート、１７；低圧段Ｄケーシング、１８；高圧
段Ｄケーシング、１９；ブルギヤ、２０；低圧段ピニオ
ンギヤ、２１；高圧段ピニオンギヤ、２２；ギヤケーシ
ング、２３；駆動軸、２４；オイルシール、２５；軸
受。1; casing; 2; low-pressure stage male rotor; 3; low-pressure stage female rotor; 4; high-pressure stage male rotor; 5; high-pressure stage female rotor;
Suction port, 7; cylindrical roller bearing, 8; low-pressure stage radial discharge port, 9; low-pressure stage axial discharge port, 10; intermediate stage passage, 11; high-pressure stage suction port, 12: cylindrical roller bearing,
13; angular contact ball bearing, 14; angular contact ball bearing, 1
5; high pressure stage radial discharge port, 16; high pressure stage axial discharge port, 17; low pressure stage D casing, 18; high pressure stage D casing, 19; bull gear, 20; low pressure stage pinion gear, 21; high pressure stage pinion gear, 22; gear casing , 23; drive shaft, 24; oil seal, 25; bearing.
Claims (4)
の対を2組回転自在に収納し、一方のロータ対が低圧
段、他方のロータ対が高圧段を形成する油冷式スクリュ
ー圧縮機において、前記低圧段は作動ガスの吸込み方向
がラジアル方向であり、前記高圧段は作動ガスの吸込み
方向がアキシャル方向であることを特徴とする油冷式ス
クリュー圧縮機。1. An oil-cooled screw compressor in which two pairs of a male rotor and a female rotor are rotatably housed in the same casing, one rotor pair forming a low pressure stage and the other rotor pair forming a high pressure stage. 3. The oil-cooled screw compressor according to claim 1, wherein the low-pressure stage has a working gas suction direction in a radial direction, and the high-pressure stage has a working gas suction direction in an axial direction.
向が軸方向であることを特徴とする請求項１に記載の油
冷式スクリュー圧縮機。2. The oil-cooled screw compressor according to claim 1, wherein the discharge directions of the high-pressure stage and the low-pressure stage are both axial directions.
雄ロータと雌ロータ対を水平に配列し、低圧段から吐出
される吐出ガスを高圧段に導く通路を前記ロータ対の下
部に配置し、さらにその下部に高圧段の雄ロータと雌ロ
ータ対を水平に配列したことを特徴とする請求項１に記
載の油冷式スクリュー圧縮機。3. A pair of a male rotor and a female rotor forming the low-pressure stage are horizontally arranged at an upper portion of the casing, and a passage for guiding discharge gas discharged from the low-pressure stage to a high-pressure stage is arranged at a lower portion of the rotor pair. 2. The oil-cooled screw compressor according to claim 1, wherein a male rotor and a female rotor pair of a high pressure stage are horizontally arranged at a lower portion thereof.
タ対を支持する軸受を保持する高圧段Ｄケーシングと、
低圧段のロータ対を支持する軸受を保持する低圧段Ｄケ
ーシングとを設け、この低圧段Ｄケーシングに、低圧段
から吐出される吐出ガスを前記ケーシングの中段に形成
された前記通路に導く空間形成し、前記高圧段Ｄケーシ
ングには吐出口を形成したことを特徴とする請求項３に
記載の油冷式スクリュー圧縮機。4. A high-pressure stage D casing for holding a bearing for supporting a high-pressure stage rotor pair on a discharge side of the casing;
A low-pressure stage D casing for holding a bearing for supporting a pair of low-pressure stage rotors, wherein space is formed in the low-pressure stage D casing to guide discharge gas discharged from the low-pressure stage to the passage formed in the middle stage of the casing; The oil-cooled screw compressor according to claim 3, wherein a discharge port is formed in the high-pressure stage D casing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28067498A JP4248055B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28067498A JP4248055B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000110760A true JP2000110760A (en) | 2000-04-18 |
| JP4248055B2 JP4248055B2 (en) | 2009-04-02 |
Family
ID=17628359
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28067498A Expired - Lifetime JP4248055B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4248055B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100829665B1 (en) * | 2005-07-06 | 2008-05-16 | 가부시키가이샤 고베 세이코쇼 | Two stage type screw compressor |
| JP2016008509A (en) * | 2014-06-20 | 2016-01-18 | 株式会社神戸製鋼所 | Screw compressor |
| EP3315779B1 (en) | 2016-10-28 | 2018-12-26 | ALMiG Kompressoren GmbH | Two-stage oil-injected screw air compressor |
| CN115751772A (en) * | 2022-11-15 | 2023-03-07 | 秦皇岛盛桐科技有限公司 | Screw two-stage compressed air source heat pump |
-
1998
- 1998-10-02 JP JP28067498A patent/JP4248055B2/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100829665B1 (en) * | 2005-07-06 | 2008-05-16 | 가부시키가이샤 고베 세이코쇼 | Two stage type screw compressor |
| JP2016008509A (en) * | 2014-06-20 | 2016-01-18 | 株式会社神戸製鋼所 | Screw compressor |
| EP3315779B1 (en) | 2016-10-28 | 2018-12-26 | ALMiG Kompressoren GmbH | Two-stage oil-injected screw air compressor |
| CN115751772A (en) * | 2022-11-15 | 2023-03-07 | 秦皇岛盛桐科技有限公司 | Screw two-stage compressed air source heat pump |
| CN115751772B (en) * | 2022-11-15 | 2023-09-15 | 大同云清科技有限公司 | Screw two-stage compressed air source heat pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4248055B2 (en) | 2009-04-02 |
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