JP2000110766A - Oil cooled screw compressor - Google Patents
Oil cooled screw compressorInfo
- Publication number
- JP2000110766A JP2000110766A JP10280673A JP28067398A JP2000110766A JP 2000110766 A JP2000110766 A JP 2000110766A JP 10280673 A JP10280673 A JP 10280673A JP 28067398 A JP28067398 A JP 28067398A JP 2000110766 A JP2000110766 A JP 2000110766A
- Authority
- JP
- Japan
- Prior art keywords
- pressure stage
- oil
- screw compressor
- low
- 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、作動ガスの冷却に
油を使用する油冷式のスクリュー圧縮機に係り、特に２
段に構成された油冷式の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 screw compressor using oil for cooling a working gas, and more particularly to an oil-cooled screw compressor.
The present invention relates to an oil-cooled screw compressor configured in stages.
【０００２】[0002]
【従来の技術】油冷式スクリュー圧縮機では、ロード運
転中には雄ロータの回転に対し雌ロータが負荷となり、
負荷トルクが作用する。そして、雌ロータが吸収するト
ルクは、雄ロータに与えられたトルクの５％程度と非常
に小さい。一方、アンロード運転時には、雌ロータを回
転方向に進めようとする負のトルクが発生する。そのた
め、雌ロータが本来の被駆動側歯面から離れる歯面分離
現象が生じる。この歯面分離現象は一旦生じると、ロー
タの回転方向のギャップを限度として繰り返し生じやす
い。この場合、周期的な回転速度変動となり、耳障りな
騒音が発生する。そして、最悪の事態では、ロータの歯
面損傷を引き起こす。2. Description of the Related Art In an oil-cooled screw compressor, a female rotor becomes a load with respect to a rotation of a male rotor during a load operation.
Load torque acts. The torque absorbed by the female rotor is very small, about 5% of the torque applied to the male rotor. On the other hand, during the unloading operation, a negative torque is generated to move the female rotor in the rotation direction. For this reason, a tooth surface separation phenomenon occurs in which the female rotor separates from the original driven tooth surface. Once this tooth flank separation phenomenon occurs, it is likely to occur repeatedly within a gap in the rotation direction of the rotor. In this case, the rotation speed changes periodically, and annoying noise is generated. And, in the worst case, the tooth surface of the rotor is damaged.
【０００３】圧縮機をアンロード運転する方法には、吸
込み絞り弁を閉止する方法と吸込絞り弁を閉止すると同
時に吐出圧力を減圧する方法がある。このいずれの方法
を用いても、アンロード運転時には雌ロータに働く負荷
トルクが大幅に低下する。そのため、ロータの全回転角
において負荷トルクをプラスに保つことが困難になり、
歯面分離現象を生じ易くなる。There are two methods of unloading the compressor: a method of closing the suction throttle valve and a method of closing the suction throttle valve and simultaneously reducing the discharge pressure. Either of these methods significantly reduces the load torque acting on the female rotor during unload operation. Therefore, it becomes difficult to keep the load torque positive at all rotation angles of the rotor,
The tooth surface separation phenomenon easily occurs.
【０００４】そこで、特開昭５８−１１３９５号公報な
どには、ロータの歯形を変えて歯面分離を起こりにくく
したスクリュー圧縮機が開示されている。また、スクリ
ュー真空ポンプにおいて雌ロータに作用するトルクを常
時負にし、これによりポンプの振動や騒音の発生を低減
することが特開平２-２５２９９１号公報に記載されて
いる。さらに、スクリュー圧縮機の雌ロータの軸端にダ
イナミックダンパーや減衰機構を取り付け、歯面分離の
発生を防止することが特開昭５５−５７６８８号公報や
特開昭５５−９６３９１号公報に開示されている。Therefore, Japanese Patent Laid-Open Publication No. Sho 58-11395 discloses a screw compressor in which the tooth profile of the rotor is changed so that tooth surface separation hardly occurs. Japanese Patent Application Laid-Open No. 2-252991 describes that a torque acting on a female rotor in a screw vacuum pump is always made negative, thereby reducing the vibration and noise of the pump. Further, it is disclosed in JP-A-55-57688 and JP-A-55-96391 that a dynamic damper and a damping mechanism are attached to a shaft end of a female rotor of a screw compressor to prevent occurrence of tooth surface separation. ing.
【０００５】[0005]
【発明が解決しようとする課題】大型の油冷式スクリュ
ー圧縮機は消費電力が大きいので、高効率が得られる２
段圧縮機が使用される。この２段の油冷式スクリュー圧
縮機において、アンロード運転のために吸込側の弁を閉
止すると、低圧段の吸込圧力は絶対圧力で０．０１MPa
以下の真空圧まで低下する（以下本明細書中において
は、圧力の表記は全て絶対圧力で行う）。それととも
に、低圧段の吐出圧力も０．０３MPa程度となり、大気
圧以下の圧力となる。一方、高圧段においては、吸込圧
力が約０．０３MPaであり、吸込絞り方式を用いると吐
出圧力は８MPa程度の圧力となる。したがって高圧段側
は、単段機のアンロード運転条件に類似している。この
場合、負のトルクが発生し、吸込圧力を極端に真空圧に
近づけると、歯面分離により振動や騒音が発生しやすく
なる。一方、低圧段側は圧縮機の吸込側および吐出側と
もに大気圧より低い圧力となり、吐出側で雌ロータを被
駆動歯面に押し付けるためのトルクがますます発生しに
くい。そのため、高圧段よりさらに雌ロータが被駆動歯
面から離れがちであり、歯面分離現象により騒音や振動
が発生しやすい。Since a large oil-cooled screw compressor consumes large power, high efficiency can be obtained.
A stage compressor is used. In this two-stage oil-cooled screw compressor, when the suction-side valve is closed for unload operation, the suction pressure in the low-pressure stage becomes 0.01 MPa in absolute pressure.
The pressure is reduced to the following vacuum pressure (hereinafter, in the present specification, all pressures are expressed in absolute pressure). At the same time, the discharge pressure in the low pressure stage is also about 0.03 MPa, which is lower than the atmospheric pressure. On the other hand, in the high pressure stage, the suction pressure is about 0.03 MPa, and the discharge pressure is about 8 MPa when the suction throttle method is used. Therefore, the high-pressure stage side is similar to the unload operation condition of the single-stage machine. In this case, when a negative torque is generated and the suction pressure is extremely close to the vacuum pressure, vibration and noise are likely to be generated due to tooth surface separation. On the other hand, on the low pressure stage side, both the suction side and the discharge side of the compressor have a pressure lower than the atmospheric pressure, and the discharge side is less likely to generate torque for pressing the female rotor against the driven tooth surface. Therefore, the female rotor tends to be further away from the driven tooth surface than the high pressure stage, and noise and vibration are likely to occur due to the tooth surface separation phenomenon.
【０００６】この歯面分離現象を抑制するために提案さ
れた上記種々の方法の中で、特開昭５８-１１３９５４
号公報に記載された歯形を修正する方法では、吸込側お
よび吐出側の圧力条件によっては、必ずしも雌ロータに
負のトルクが発生するのを抑制できず、運転条件が限ら
れるという不具合がある。また、特開平２−２５２９９
１号公報に記載の方法は、圧縮機のアンロード運転に相
当する状態のみが実行される真空ポンプでのみ成立する
ものであり、ロード運転とアンロード運転が繰返される
スクリュー圧縮機には不適である。[0006] Among the various methods proposed to suppress this tooth surface separation phenomenon, Japanese Patent Application Laid-Open No. 58-113954 discloses
In the method of correcting the tooth profile described in Japanese Patent Application Laid-Open Publication No. H11-157, there is a problem that the generation of negative torque on the female rotor cannot be necessarily suppressed depending on the pressure conditions on the suction side and the discharge side, and the operating conditions are limited. In addition, Japanese Patent Application Laid-Open
The method described in Japanese Patent Application Publication No. 1-305 is applicable only to a vacuum pump in which only a state corresponding to the unload operation of the compressor is executed, and is not suitable for a screw compressor in which the load operation and the unload operation are repeated. is there.
【０００７】さらに、圧縮機の雌ロータ軸端にダイナミ
ックダンパーや減衰機構を取り付けて歯面分離を防止す
る特開昭５５−５７６８８号公報および特開昭５５−９
６３９１号公報に記載の方法では、トーションバーのチ
ューニングや強度評価が困難であること、所望の減衰力
および耐久性を得ることが困難であること等の不具合が
ある。Further, a dynamic damper and a damping mechanism are attached to a shaft end of a female rotor of a compressor to prevent separation of tooth surfaces, and are disclosed in JP-A-55-57688 and JP-A-55-9.
The method described in Japanese Patent No. 6391 has disadvantages such as difficulty in tuning and evaluating the strength of the torsion bar, and difficulty in obtaining desired damping force and durability.
【０００８】本発明は上記従来技術の不具合に鑑みなさ
れたものであり、その目的は油冷式スクリュー圧縮機に
おいて、低圧段の雌ロータの歯面分離振動の発生を抑制
することにある。本発明の他の目的は、信頼性の高い油
冷式２段スクリュー圧縮機を提供することにある。The present invention has been made in view of the above-mentioned disadvantages of the related art, and has as its object to suppress occurrence of tooth surface separation vibration of a low-pressure stage female rotor in an oil-cooled screw compressor. Another object of the present invention is to provide a highly reliable oil-cooled two-stage screw compressor.
【０００９】[0009]
【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、油冷式スクリュー圧縮機のオ
イルポンプを圧縮機本体の雌ロータの軸端に配設したも
のである。そして好ましくは、圧縮機本体は低圧段及び
高圧段を有し、オイルポンプを低圧段に設けたものであ
る。A first feature of the present invention to achieve the above object is that an oil pump of an oil-cooled screw compressor is disposed at a shaft end of a female rotor of a compressor body. is there. Preferably, the compressor body has a low pressure stage and a high pressure stage, and the oil pump is provided in the low pressure stage.
【００１０】上記目的を達成するための本発明の第２の
特徴は、各々雄ロータ、雌ロータ、及びこれら雄ロータ
と雌ロータとを収納するケーシングとを有する低圧段お
よび高圧段を備えた油冷式スクリュー圧縮機において、
ケーシングとそれぞれのロータとの間に軸封機構を配設
し、この軸封機構とこのロータとの間にたまる油を吸引
するオイルポンプを、低圧段の雌ロータの軸端に配設し
たものである。そして好ましくは、オイルポンプの出口
を、前記低圧段の吸込側、前記高圧段の吸込側、または
高圧段の吐出側のいずれかに接続するものである。な
お、上記何れの特徴においても、ロータのいずれかにモ
ータ軸をオーバーハング状に取り付け、このモータ軸の
一方側にのみこのモータ軸を支承する軸受を配設するこ
とが望ましい。A second feature of the present invention to achieve the above object is that an oil having a low pressure stage and a high pressure stage each having a male rotor, a female rotor, and a casing accommodating the male rotor and the female rotor. In a cold screw compressor,
A shaft sealing mechanism is disposed between a casing and each rotor, and an oil pump for sucking oil accumulated between the shaft sealing mechanism and the rotor is disposed at a shaft end of a low-pressure stage female rotor. It is. Preferably, the outlet of the oil pump is connected to one of the suction side of the low-pressure stage, the suction side of the high-pressure stage, and the discharge side of the high-pressure stage. In any of the above features, it is preferable that the motor shaft is mounted in an overhang shape on one of the rotors, and a bearing for supporting the motor shaft is provided only on one side of the motor shaft.
【００１１】なお、オイルポンプを駆動する動力は常に
低圧段の雌ロータの負荷として作用するから、負荷トル
クが増大し負のトルクの発生を抑制できる。またこのオ
イルポンプにより生ずる負荷の大きさを、オイルポンプ
の出口を接続する位置を変えるることにより変化させる
ことができる。Since the power for driving the oil pump always acts as a load on the female rotor at the low pressure stage, the load torque increases and the generation of negative torque can be suppressed. Further, the magnitude of the load generated by the oil pump can be changed by changing the position where the outlet of the oil pump is connected.
【００１２】[0012]
【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スクリュー
圧縮機の一実施例の模式図であり、作動ガス及び潤滑油
の流れを併せ示す図、図２は本発明に係る油冷式スクリ
ュー圧縮機の一実施例の上面図を断面で示した図、図３
は図２に示した油冷式スクリュー圧縮機の正面図を断面
で示した図である。DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic view of one embodiment of an oil-cooled screw compressor according to the present invention, showing the flow of working gas and lubricating oil together. FIG. FIG. 3 is a sectional view showing a top view of the embodiment.
FIG. 3 is a sectional view showing a front view of the oil-cooled screw compressor shown in FIG. 2.
【００１３】２段の油冷式スクリュー圧縮機は、低圧段
４５及び高圧段５０を備えている。低圧段４５を構成す
る低圧段雄ロータ２および低圧段雌ロータ３は、円筒こ
ろ軸受１５、１６により吸込側軸部を回転可能に支持さ
れ、アンギュラ玉軸受１３、１４により吐出側軸部を回
転可能に支持されている。そして、円筒ころ軸受１５、
１６及びアンギュラ玉軸受１３、１４はケーシング１内
に保持されている。The two-stage oil-cooled screw compressor has a low-pressure stage 45 and a high-pressure stage 50. The low-pressure stage male rotor 2 and the low-pressure stage female rotor 3 constituting the low-pressure stage 45 are rotatably supported on the suction-side shaft by cylindrical roller bearings 15 and 16, and rotate on the discharge-side shaft by angular ball bearings 13 and 14. Supported as possible. And the cylindrical roller bearing 15,
16 and the angular ball bearings 13 and 14 are held in the casing 1.
【００１４】作動ガスは吸込フィルタ６から吸込絞り弁
７を経由して、低圧段雄ロータ２及び低圧段雌ロータ３
に吸込まれる。吸込まれたガスに低圧段４５の圧縮過程
で油が注入される。低圧段４５から吐出された作動ガス
は、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３２へ流入する。この中間段通路３２中にも
油が噴射され、圧縮ガスを冷却する。冷却された圧縮ガ
スは、高圧段雄ロータ４および高圧段雌ロータ５により
形成される空間に吸込まれる。高圧段雄ロータ４および
高圧段雌ロータ５は、円筒ころ軸受１９，２０により吸
込側軸部を回転可能に支持され、アンギュラ玉軸受１
７、１８により吐出側軸部を回転可能に支持される。低
圧段の軸受と同様に、これらの軸受はケーシング１に保
持される。高圧段雄ロータ４および高圧段雌ロータ５に
より、さらに所定の圧力まで昇圧された作動ガスは、高
圧段吐出口３１から吐出される。The working gas is supplied from the suction filter 6 via the suction throttle valve 7 to the low-pressure male rotor 2 and the low-pressure female rotor 3.
Sucked into. Oil is injected into the sucked gas during the compression process of the low pressure stage 45. The working gas discharged from the low pressure stage 45 flows into the intermediate stage passage 32 which is a space between the low pressure stage and the high pressure stage of the casing. Oil is also injected into the intermediate stage passage 32 to cool the compressed gas. The cooled compressed gas is sucked into a space formed by the high-pressure stage male rotor 4 and the high-pressure stage female rotor 5. The high-pressure step male rotor 4 and the high-pressure step female rotor 5 are rotatably supported on the suction-side shaft by cylindrical roller bearings 19 and 20, and the angular ball bearing 1
The discharge side shaft portion is rotatably supported by 7 and 18. These bearings, like the low-pressure stage bearings, are held in the casing 1. The working gas further raised to a predetermined pressure by the high-pressure stage male rotor 4 and the high-pressure stage female rotor 5 is discharged from the high-pressure stage discharge port 31.
【００１５】低圧段雄ロータ２と高圧段雄ロータ４に
は、それぞれ低圧段被駆動歯車１０と高圧段被駆動歯車
１１が取り付けられている。さらに駆動軸３７には駆動
歯車１２が取り付けられており、この駆動歯車を挟んで
一方側を円錐ころ軸受２２が、他方側を円筒ころ軸受２
１が回転可能に支持している。駆動軸３７がギヤケーシ
ング９の外部に延在している部分には軸封機構２３が設
けられており、ギヤケース２２内の油が外部へ流出する
のを防止している。低圧段および高圧段の吸込側の軸受
１５、１６、１９、２０、駆動軸の軸受２２、２１、お
よび歯車１０、１１、１２は潤滑油で強制潤滑されてい
る。そして、軸受及び歯車を潤滑した後の油は、ギヤケ
ース９の下部に落下する。A low-pressure stage driven gear 10 and a high-pressure stage driven gear 11 are attached to the low-pressure stage male rotor 2 and the high-pressure stage male rotor 4, respectively. Further, the drive gear 12 is attached to the drive shaft 37, and the tapered roller bearing 22 is provided on one side and the cylindrical roller bearing 2 is provided on the other side across the drive gear.
1 is rotatably supported. A shaft sealing mechanism 23 is provided at a portion where the drive shaft 37 extends outside the gear casing 9 to prevent oil in the gear case 22 from flowing out. The low-pressure stage and high-pressure stage suction-side bearings 15, 16, 19, 20, drive shaft bearings 22, 21, and gears 10, 11, 12 are forcibly lubricated with lubricating oil. Then, the oil after lubricating the bearings and the gears falls to the lower part of the gear case 9.
【００１６】低圧段４５の雌ロータ３の軸端にはオイル
ポンプ８が接続されている。このオイルポンプ８は雌ロ
ータ３によって回転駆動される。ギヤケーシング９の下
部とオイルポンプ８の吸込口２５は配管２７で接続され
ており、ギヤケース３の下部に溜まった潤滑油をオイル
ポンプ８が吸引する。オイルポンプ８の吐出口２６には
配管２８が接続されており、ギヤケース下部から吸引し
た潤滑油は低圧段４５の吸込側に回収される。An oil pump 8 is connected to the shaft end of the female rotor 3 of the low-pressure stage 45. The oil pump 8 is driven to rotate by the female rotor 3. The lower part of the gear casing 9 and the suction port 25 of the oil pump 8 are connected by a pipe 27, and the oil pump 8 sucks the lubricating oil accumulated in the lower part of the gear case 3. A pipe 28 is connected to the discharge port 26 of the oil pump 8, and the lubricating oil sucked from the lower part of the gear case is collected on the suction side of the low-pressure stage 45.
【００１７】オイルポンプ８が、ギヤケース９内に油が
充満することを防止する。それとともに、ギヤケース９
内は、オイルポンプ８の吸引作用により、ほぼ大気圧か
それより低い圧力に保持される。これにより、軸封装置
２３に作用する圧力を低く抑えることができる。The oil pump 8 prevents the gear case 9 from being filled with oil. At the same time, gear case 9
The inside is maintained at substantially the atmospheric pressure or a pressure lower than the atmospheric pressure by the suction action of the oil pump 8. Thus, the pressure acting on the shaft sealing device 23 can be kept low.
【００１８】油冷式２段スクリュー圧縮機は１５０ｋW
以上の大型機が一般的であり、駆動軸３７も大型化す
る。特に図３に示したように、駆動軸３７にモータロー
タ３５をオーバーハング状に接続した場合、強度を確保
するために駆動軸３７を太くしなければならない。その
結果、軸封装置２３の軸封部の周速は速くなるので、軸
封部の信頼性を確保するために、ギヤケース２４の内部
の圧力を極力低く抑える必要がある。The oil-cooled two-stage screw compressor is 150 kW
The large-sized machine described above is generally used, and the drive shaft 37 is also increased in size. In particular, as shown in FIG. 3, when the motor rotor 35 is connected to the drive shaft 37 in an overhang shape, the drive shaft 37 must be made thick to ensure strength. As a result, the peripheral speed of the shaft sealing portion of the shaft sealing device 23 is increased. Therefore, in order to ensure the reliability of the shaft sealing portion, it is necessary to keep the pressure inside the gear case 24 as low as possible.
【００１９】以下、一般的な空気圧縮機の場合を例とし
て説明する。この一般的な空気圧縮機の吐出圧力は０．
８Mpaである。圧縮機がアンロード運転状態になると、
吸込絞り弁７を閉状態にする。このとき、低圧段ロータ
２，３の吸込側は、０．０１MPa前後の真空圧力に低下
する。これとともに低圧段の吐出圧力も０．０３MPa程
度の真空圧力になる。上述したように、全負荷状態にお
いても雌ロータに吸収されるトルクは、雄ロータの入力
トルクの５％程度である。したがって、圧力レベルが低
下したアンロード運転状態では、低圧段の雌ロータでは
被駆動歯面に押し付けるトルクがほとんど発生しない。
その結果、ロータの回転位置によっては負のトルクが発
生し、雌ロータは歯面分離振動をおこしやすくなり、圧
縮機の騒音増大の大きな原因となる。 高圧段５０側に
おいても同様な現象が発生しやすくなるが、アンロード
運転時の高圧段の吐出圧力は低圧段の吐出圧力よりも必
ず高いので、２段圧縮機の場合のアンロード時の騒音源
は低圧段の雌ロータ３が主となる。そこで、本発明では
オイルポンプ８を低圧段雌ロータ３の回転軸に取付け、
低圧段雌ロータ３に伝達されたトルクでオイルポンプ８
を駆動している。Hereinafter, a case of a general air compressor will be described as an example. The discharge pressure of this general air compressor is 0.
8 Mpa. When the compressor enters the unload operation state,
The suction throttle valve 7 is closed. At this time, the suction side of the low-pressure stage rotors 2, 3 drops to a vacuum pressure of about 0.01 MPa. At the same time, the discharge pressure of the low pressure stage also becomes a vacuum pressure of about 0.03 MPa. As described above, the torque absorbed by the female rotor even in the full load state is about 5% of the input torque of the male rotor. Therefore, in the unloading operation state in which the pressure level is reduced, the torque for pressing the driven tooth surface is hardly generated in the female rotor at the low pressure stage.
As a result, a negative torque is generated depending on the rotational position of the rotor, and the female rotor is liable to cause tooth separation vibration, which is a major cause of an increase in compressor noise. A similar phenomenon is likely to occur on the high pressure stage 50 side. However, since the discharge pressure of the high pressure stage during the unload operation is always higher than the discharge pressure of the low pressure stage, noise during unloading in the case of the two-stage compressor is used. The source is mainly a low-pressure stage female rotor 3. Therefore, in the present invention, the oil pump 8 is attached to the rotating shaft of the low-pressure stage female rotor 3,
The oil pump 8 is driven by the torque transmitted to the low-pressure stage female rotor 3.
Is driving.
【００２０】オイルポンプ８を低圧段雌ロータ３の回転
軸に取付けることにより、ロード運転時でもアンロード
運転時でも、一定のトルクが低圧段雌ロータ３部で消費
される。オイルポンプ８は大形の圧縮機、特に図２及び
図３に示した大径の駆動軸を有し、モータをオーバーハ
ング状に取付けた圧縮機の軸封部の信頼性を向上させる
上で不可欠である。したがって、この不可欠な部品の配
置を変えるだけで、余分な動力を必要としないので、省
エネルギの下に騒音の発生を低減できる。By mounting the oil pump 8 on the rotating shaft of the low-pressure stage female rotor 3, a constant torque is consumed in the low-pressure stage female rotor 3 during both the load operation and the unload operation. The oil pump 8 has a large-sized compressor, in particular, a large-diameter drive shaft shown in FIGS. 2 and 3, and is used to improve the reliability of the shaft seal of the compressor in which the motor is mounted in an overhang shape. It is essential. Therefore, only by changing the arrangement of the indispensable parts, no extra power is required, and the generation of noise can be reduced while saving energy.
【００２１】ロード運転時における雌ロータへの伝達ト
ルクは５％程度と小さいが、この小さい伝達トルクで歯
面分離を防止できることは知られている。一方、アンロ
ード運転時に雌ロータに発生する負のトルクは、ロータ
歯形を適切に選定すれば、それ程大きくはない。したが
って、アンロード運転時の負トルクをカバーし、さらに
ロード運転時の雌ロータへの伝達トルクに相当する分を
オイルポンプの吸収トルクで補償することは十分可能で
ある。これにより、雌ロータの歯面分離振動と騒音の増
加を防止することができる。The torque transmitted to the female rotor during the load operation is as small as about 5%, but it is known that tooth surface separation can be prevented with this small transmitted torque. On the other hand, the negative torque generated in the female rotor during the unload operation is not so large if the rotor tooth profile is properly selected. Therefore, it is sufficiently possible to cover the negative torque during the unload operation and to compensate for the transmission torque to the female rotor during the load operation by the absorption torque of the oil pump. As a result, it is possible to prevent an increase in the tooth surface separation vibration and noise of the female rotor.
【００２２】図１において、オイルポンプ８の出口２６
を、配管２８により圧縮機の吸込側に接続するか、ある
いは配管２９により低圧段吐出側に接続するか、または
配管３０を用いて高圧段吐出側に接続する。これによ
り、オイルポンプ８の吸収トルクを調整することが可能
になる。つまり、ギヤケース２４の底部から回収した油
をどの位置に戻すかによって、オイルポンプ８の出口２
６の圧力が変化するので、吸収するトルクの調整が可能
になる。オイルポンプ８の吸収トルクを調整する他の方
法としては、オイルポンプ８の吸引能力を落とさない範
囲内で、オイルポンプ出口２６側に流動抵抗を付加する
方法がある。In FIG. 1, the outlet 26 of the oil pump 8
Is connected to the suction side of the compressor by a pipe 28, or to the discharge side of a low pressure stage by a pipe 29, or to the discharge side of a high pressure stage by a pipe 30. As a result, the absorption torque of the oil pump 8 can be adjusted. In other words, depending on where the oil collected from the bottom of the gear case 24 is to be returned, the outlet 2 of the oil pump 8
Since the pressure of 6 changes, it is possible to adjust the torque to be absorbed. As another method of adjusting the absorption torque of the oil pump 8, there is a method of adding a flow resistance to the oil pump outlet 26 side as long as the suction capacity of the oil pump 8 is not reduced.
【００２３】以上述べたように本実施例によれば、圧縮
機の吸込圧力が変化しても、吸込圧力の変化に応じた配
管接続をすれば、低圧段雌ロータの負のトルク発生によ
る歯面分離振動を防止でき、圧縮機の騒音の増大を防止
できる。As described above, according to this embodiment, even if the suction pressure of the compressor changes, if the piping is connected in accordance with the change in the suction pressure, the teeth due to the generation of the negative torque of the low-pressure stage female rotor can be reduced. Surface separation vibration can be prevented, and an increase in compressor noise can be prevented.
【００２４】[0024]
【発明の効果】本発明によれば、２段の油冷式スクリュ
ー圧縮機において、アンロード時に低圧段の雌ロータに
発生する歯面分離振動とそれに伴う騒音の発生を抑制で
きる。また、軸封部の信頼性を高めることができる。According to the present invention, in a two-stage oil-cooled screw compressor, tooth surface separation vibration generated in a low-pressure stage female rotor during unloading and the accompanying noise can be suppressed. Further, the reliability of the shaft sealing portion can be improved.
【図１】本発明に係る油冷式スクリュー圧縮機の一実施
例の模式図。FIG. 1 is a schematic view of one embodiment of an oil-cooled screw compressor according to the present invention.
【図２】本発明に係る油冷式圧縮機の一実施例の縦断面
図であり、その上面図。FIG. 2 is a longitudinal sectional view of one embodiment of the oil-cooled compressor according to the present invention, and is a top view thereof.
【図３】図２に示した実施例の縦断面図であり、その正
面図。3 is a longitudinal sectional view of the embodiment shown in FIG. 2, and a front view thereof.
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；
吸込フィルタ、７；吸込絞り弁、８；オイルポンプ、１
０；低圧段被駆動歯車、１１；高圧段被駆動歯車、１
２；駆動歯車、１３〜２２；軸受、２３；軸封、２４；
ギヤケース、２５；オイルポンプ入口、２６；オイルポ
ンプ出口、２７；油吸込配管、２８〜３０；油出口配
管、３１；高圧段吐出、３２；低圧段吐出、３５；モー
タロータ、３６；モータステータ、３７；駆動軸、４
５；低圧段、５０；高圧段。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 filter, 7; suction throttle valve, 8; oil pump, 1
0: low-pressure driven gear, 11: high-pressure driven gear, 1
2; drive gear, 13 to 22; bearing, 23; shaft seal, 24;
Gear case, 25; Oil pump inlet, 26; Oil pump outlet, 27; Oil suction pipe, 28 to 30; Oil outlet pipe, 31; High pressure discharge, 32; Low pressure discharge, 35; Motor rotor, 36; Drive shaft, 4
5; low pressure stage, 50; high pressure stage.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 高野 正彦 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 (72)発明者 内田 利一 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 Ｆターム(参考） 3H029 AA03 AA09 AA17 AA21 AB02 AB08 BB16 BB21 BB41 BB42 BB51 CC05 CC16 CC20 CC22 CC34 CC51 CC54 CC61 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Masahiko Takano 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Within the Air Conditioning Systems Division, Hitachi, Ltd. (72) Inventor Toshiichi Uchida 502, Kandachicho, Tsuchiura-shi, Ibaraki Prefecture Hitachi, Ltd. 3H029 AA03 AA09 AA17 AA21 AB02 AB08 BB16 BB21 BB41 BB42 BB51 CC05 CC16 CC20 CC22 CC34 CC51 CC54 CC61
Claims (5)
端に配設した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, wherein an oil pump is provided at a shaft end of a female rotor of a compressor body.
し、前記オイルポンプを低圧段に設けたことを特徴とす
る請求項１に記載の油冷式スクリュー圧縮機。2. The oil-cooled screw compressor according to claim 1, wherein said compressor body has a low pressure stage and a high pressure stage, and said oil pump is provided in a low pressure stage.
ータと雌ロータとを収納するケーシングとを有する低圧
段および高圧段を備えた油冷式スクリュー圧縮機におい
て、前記ケーシングと前記それぞれのロータとの間に軸
封機構を配設し、この軸封機構とこのロータとの間にた
まる油を吸引するオイルポンプを、前記低圧段の雌ロー
タの軸端に配設したことを特徴とする油冷式スクリュー
圧縮機。3. An oil-cooled screw compressor having a low pressure stage and a high pressure stage each having a male rotor, a female rotor, and a casing accommodating the male rotor and the female rotor, wherein the casing and the respective rotors are provided. And an oil pump for sucking oil accumulated between the shaft sealing mechanism and the rotor is provided at a shaft end of the female rotor at the low pressure stage. Oil-cooled screw compressor.
吸込側、前記高圧段の吸込側、または高圧段の吐出側の
いずれかに接続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. The oil according to claim 3, wherein an outlet of the oil pump is connected to one of a suction side of the low pressure stage, a suction side of the high pressure stage, and a discharge side of the high pressure stage. Cold screw compressor.
ーハング状に取り付け、このモータ軸の一方側にのみこ
のモータ軸を支承する軸受を配設したことを特徴とする
請求項１ないし４の何れか１項に記載の油冷式スクリュ
ー圧縮機。5. A motor shaft according to claim 1, wherein a motor shaft is mounted on one of said rotors in an overhang shape, and a bearing for supporting said motor shaft is provided only on one side of said motor shaft. The oil-cooled screw compressor according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28067398A JP4185598B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28067398A JP4185598B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000110766A true JP2000110766A (en) | 2000-04-18 |
| JP4185598B2 JP4185598B2 (en) | 2008-11-26 |
Family
ID=17628344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28067398A Expired - Lifetime JP4185598B2 (en) | 1998-10-02 | 1998-10-02 | Oil-cooled screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4185598B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002519574A (en) * | 1998-06-17 | 2002-07-02 | スベンスカ・ロツタア・マスキナア・アクチボラグ | Two-stage compressor and method for cooling such a compressor |
| JP2004504537A (en) * | 2000-07-18 | 2004-02-12 | アルカテル | Monoblock housing for vacuum pump |
| CN103423165A (en) * | 2013-08-26 | 2013-12-04 | 天津商业大学 | Vertical type totally closed double-stage screw rod refrigerating compressor |
| CN104454545A (en) * | 2014-11-27 | 2015-03-25 | 西安交通大学 | Compressor oil injector having gas suction function |
| CN107956686A (en) * | 2017-12-07 | 2018-04-24 | 无锡锡压压缩机有限公司 | A kind of dry screw compressor structure of integrated oil path |
| CN109578275A (en) * | 2018-12-27 | 2019-04-05 | 珠海格力电器股份有限公司 | Two-stage screw compressor and its twin-stage rotor set mounting structure used |
| CN111749896A (en) * | 2020-07-07 | 2020-10-09 | 杭州派祺空气净化科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
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-
1998
- 1998-10-02 JP JP28067398A patent/JP4185598B2/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002519574A (en) * | 1998-06-17 | 2002-07-02 | スベンスカ・ロツタア・マスキナア・アクチボラグ | Two-stage compressor and method for cooling such a compressor |
| JP2004504537A (en) * | 2000-07-18 | 2004-02-12 | アルカテル | Monoblock housing for vacuum pump |
| CN103423165A (en) * | 2013-08-26 | 2013-12-04 | 天津商业大学 | Vertical type totally closed double-stage screw rod refrigerating compressor |
| CN104454545A (en) * | 2014-11-27 | 2015-03-25 | 西安交通大学 | Compressor oil injector having gas suction function |
| CN104454545B (en) * | 2014-11-27 | 2016-07-06 | 西安交通大学 | A kind of compressor fuel injector with air suction function |
| CN107956686A (en) * | 2017-12-07 | 2018-04-24 | 无锡锡压压缩机有限公司 | A kind of dry screw compressor structure of integrated oil path |
| CN109578275A (en) * | 2018-12-27 | 2019-04-05 | 珠海格力电器股份有限公司 | Two-stage screw compressor and its twin-stage rotor set mounting structure used |
| CN111749896A (en) * | 2020-07-07 | 2020-10-09 | 杭州派祺空气净化科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
| CN111749896B (en) * | 2020-07-07 | 2022-11-08 | 山东顺和新材料科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
| CN112879290A (en) * | 2021-01-25 | 2021-06-01 | 马鞍山赛力文机械有限公司 | Double-screw main machine structure driven by front end gear and rear end gear |
| CN112879290B (en) * | 2021-01-25 | 2022-06-14 | 马鞍山赛力文机械有限公司 | Double-screw main machine structure driven by front end gear and rear end gear |
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