JPH05302582A - Lubrication type screw compressor - Google Patents
Lubrication type screw compressorInfo
- Publication number
- JPH05302582A JPH05302582A JP10642192A JP10642192A JPH05302582A JP H05302582 A JPH05302582 A JP H05302582A JP 10642192 A JP10642192 A JP 10642192A JP 10642192 A JP10642192 A JP 10642192A JP H05302582 A JPH05302582 A JP H05302582A
- Authority
- JP
- Japan
- Prior art keywords
- air
- rotor
- pressure
- oil mist
- oil
- 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]
【産業上の利用分野】本発明は、給油式スクリュー圧縮
機とスクリュー式冷凍機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil supply type screw compressor and a screw type refrigerator.
【０００２】[0002]
【従来の技術】従来技術を図４〜図６に従って説明す
る。2. Description of the Related Art A conventional technique will be described with reference to FIGS.
【０００３】図４は、給油式スクリュー２段空気圧縮機
ユニットの系統図である。本図において、吸入絞り弁３
から吸われた空気は、１段側圧縮機１で約２kgf／cm2g
まで圧縮された後、２段側圧縮機２に吸われ、ここで７
kgf／cm2g に圧縮されて吐出され、オイルセパレータ４
で空気中の油を分離した後、調圧弁５，逆止弁６を通
り、アフタークーラ７で冷やされて吐出される。オイル
セパレータ４の下部に溜った油は、オイルセパレータ４
内の圧力と圧縮機の給油口の圧力との差圧により流れ、
オイルクーラ８で冷やされた後、フィルタ９を通って、
１段側圧縮機１と２段側圧縮機２に給油される。アフタ
ークーラ７の出口での空気消費量が減少すると圧縮機の
容量制御のためにアンロード運転を行なう。アンロード
運転方法は消費空気量の減少による吐出圧力の上昇によ
って圧力調整弁１０が開き、オイルセパレータ４内の空
気を吸入絞り弁３へ送り、弁の開度を調整して吸入空気
量を制御するｓアン運転と、消費空気量が非常に少なく
なった場合、アフタークーラ出口側の圧力上昇を圧力ス
イッチ１３で検出し放気電磁弁１１を開くことによりオ
イルセパレータ４内の空気を吸入絞り弁３へ送り弁を全
閉にし、オイルセパレータ４内の空気を放気サイレンサ
１２から大気へ放気し吐出圧力を下げて負荷を軽減する
ｉアン運転がある。ｓアン運転時で吸入絞り弁３が全閉
の状態、及びｉアン運転時には１段側圧縮機１の吸入，
吐出圧力は負圧となり、吸入圧力は約“−”７２０mmＨ
ｇ，吐出圧力は約“−”６４０mmＨｇと、真空に近い圧
力である。２段側圧縮機２の吐出圧力は、ｓアン時で約
８kgf／cm2g ，ｉアン時で約２kgf／cm2g である。FIG. 4 is a system diagram of a refueling screw two-stage air compressor unit. In this figure, the suction throttle valve 3
The air sucked from the 1st stage compressor 1 is about 2 kgf / cm 2 g
After being compressed to 2, it is sucked by the second stage compressor 2 and
Compressed to kgf / cm 2 g and discharged, the oil separator 4
After the oil in the air is separated by, the oil passes through the pressure regulating valve 5 and the check valve 6, is cooled by the after cooler 7, and is discharged. The oil accumulated in the lower part of the oil separator 4 is
Flows due to the pressure difference between the internal pressure and the pressure at the oil filler port of the compressor,
After being cooled by the oil cooler 8, it passes through the filter 9,
Oil is supplied to the first-stage compressor 1 and the second-stage compressor 2. When the air consumption at the outlet of the aftercooler 7 decreases, unloading operation is performed to control the capacity of the compressor. In the unloading operation method, the pressure adjusting valve 10 is opened by the increase of the discharge pressure due to the decrease of the consumed air amount, the air in the oil separator 4 is sent to the intake throttle valve 3, and the opening degree of the valve is adjusted to control the intake air amount. When the air consumption is very low, the pressure increase on the outlet side of the aftercooler is detected by the pressure switch 13 and the air release solenoid valve 11 is opened to suck the air in the oil separator 4 into a throttle valve. 3, the feed valve is fully closed, the air in the oil separator 4 is discharged from the discharge silencer 12 to the atmosphere, and the discharge pressure is reduced to reduce the load. The intake throttle valve 3 is fully closed during s-an operation, and the intake of the first-stage compressor 1 during i-an operation,
The discharge pressure is negative and the suction pressure is about "-" 720 mmH.
The discharge pressure is about "-" 640 mmHg, which is close to a vacuum. The discharge pressure of the two-stage compressor 2 is about 8 kgf / cm 2 g, about at the time i en 2 kgf / cm 2 g in a time s Ann.
【０００４】図５は１段側圧縮機１のスクリューロータ
の吐出側端面で、吸入側から見たロータの噛合状況を示
すロータの軸の断面図である。本図において、雄ロータ
１４と雌ロータ１５の歯溝間の空気と油が吐出ポートか
ら吐出された後には、雄ロータ１４と雌ロータ１５の歯
溝間には図中に示す僅かな閉込空間が残る。この閉込空
間は、雄ロータ１４と雌ロータ１５の噛合いによって形
成されるシールライン１７（ロータの軸直角断面に投影
した線）と、Ｄケーシング１６の吐出端面の間で囲まれ
た空間で図５のＡ−Ａ断面（雄ロータ１４と雌ロータ１
５のそれぞれの軸心を結ぶ線上の断面）を図６に示す。
この閉込空間はロータの回転に伴って縮小し、雄ロータ
の回転角が０°の時に空間はなくなる。この閉込空間内
には、吐出空気と１段側圧縮機に給油された油ミストが
含まれ、空間の縮小に伴って、空気と油ミストは、シー
ルライン１７を通って図中の矢印の方向で吸入側へ噴出
する（ロータ端面とＤケーシング１６との間のＤギャッ
プから吸入側へも噴出するが、Ｄギャップでの抵抗はシ
ールライン１７と比べて大きいため、シールライン１７
からの噴出量が圧倒的に多い）。図６で、ロータの回転
に伴って、雄ロータ１４の歯面と雌ロータ１６の歯面は
それぞれ矢印の方向へ進み、それぞれの歯面の進み速度
をｖM，ｖFとする。又、閉込空間内の油ミストが、閉込
空間から吸入側へ噴出する速度をＶとするとＶは閉込空
間内の圧力と吸入圧力との差圧により決まり、差圧が大
きければＶは大きくなる。FIG. 5 is a cross-sectional view of the rotor shaft showing the meshing condition of the rotor as seen from the suction side at the discharge side end surface of the screw rotor of the first-stage compressor 1. In this figure, after the air and oil between the tooth grooves of the male rotor 14 and the female rotor 15 are discharged from the discharge port, the slight gap shown in the figure is inserted between the tooth grooves of the male rotor 14 and the female rotor 15. The space remains. The enclosed space is a space surrounded by a seal line 17 (a line projected on a cross section perpendicular to the axis of the rotor) formed by the engagement of the male rotor 14 and the female rotor 15 and a discharge end surface of the D casing 16. AA cross section of FIG. 5 (the male rotor 14 and the female rotor 1
FIG. 6 shows a cross section on a line connecting the respective axis centers of No. 5).
This confined space shrinks as the rotor rotates, and disappears when the rotation angle of the male rotor is 0 °. The enclosed space contains the discharge air and the oil mist supplied to the first-stage compressor. As the space is reduced, the air and the oil mist pass through the seal line 17 and are indicated by arrows in the figure. Is ejected toward the intake side in the direction (ejects from the D gap between the rotor end surface and the D casing 16 to the intake side as well, but the resistance in the D gap is larger than that of the seal line 17, so the seal line 17
The overwhelming amount of squirt from). In FIG. 6, the tooth surface of the male rotor 14 and the tooth surface of the female rotor 16 advance in the directions of the arrows as the rotor rotates, and the advancing speeds of the respective tooth surfaces are v M and v F. Further, when the speed at which the oil mist in the confined space is ejected from the confined space to the suction side is V, V is determined by the pressure difference between the pressure in the confined space and the suction pressure, and if the pressure difference is large, then V is growing.
【０００５】閉込空間内の油ミストがロータ間のシール
ライン１７から噴出する時に、油ミストがロータ歯面に
衝突する速度は、相対速度差として、雄ロータ側は、ｖ
M −Ｖ、雌ロータ側はｖF −Ｖで表わされる。この衝突
速度が大きいと、時間の経過とともに次第に、ロータ歯
面が油ミストの衝突エネルギにより侵食される要因にな
る（特願平1−260746 号明細書）。When the oil mist in the enclosed space is jetted from the seal line 17 between the rotors, the speed at which the oil mist collides with the tooth flanks of the rotor is the relative speed difference.
M -V, female rotor side is expressed by v F -V. If the collision speed is high, the rotor tooth surface gradually becomes eroded by the collision energy of the oil mist with the passage of time (Japanese Patent Application No. 1-260746).
【０００６】[0006]
【発明が解決しようとする課題】従来技術の問題点とし
て次のことがあげられる。The problems of the prior art are as follows.
【０００７】１段側圧縮機において、ｓアン及びｉアン
運転時には吐出圧力は“−”６４０mmＨｇ、吸入圧力は
“−”７２０mmＨｇ程度の負圧であり、この差圧が８０
mmＨｇと小さい（全負荷時は約２kgf／cm2g ）ため、閉
込空間内の圧力（閉込開始時は吐出圧力と同値であり、
縮小に伴って吸入圧力まで減圧する）と吸入圧力との差
圧が小さい。このために、前述の噴出速度Ｖが小さくな
り、油ミストがロータ歯面に衝突する速度ｖM−Ｖある
いはｖF−Ｖが大きくなるため、ロータ歯面が油ミスト
の衝突エネルギによって経時的に侵食され易くなる。In the first-stage compressor, the discharge pressure is "-" 640 mmHg and the suction pressure is "-" 720 mmHg at the time of s Anne and i Anne operation, and the differential pressure is 80
Since it is as small as mmHg (approx. 2 kgf / cm 2 g at full load), the pressure in the confined space (same as the discharge pressure at the start of confinement
The pressure difference between the suction pressure and the suction pressure is small as the pressure decreases. For this reason, the jet velocity V described above decreases, and the velocity v M −V or v F −V at which the oil mist collides with the rotor tooth surface increases, so that the rotor tooth surface changes with time due to the collision energy of the oil mist. Easily eroded.
【０００８】又、別の要因として、ｓアン及びｉアン運
転時には、吐出圧力が、“−”640mmＨｇと真空に近い
状態であるため、油ミストがロータ歯面に衝突する際
に、エアクッション効果が薄れて、衝撃が増すことによ
り歯面が侵食され易くなる。Further, as another factor, the discharge pressure is "-" 640 mmHg, which is close to a vacuum during s- and i-ann operation, so that when the oil mist collides with the rotor tooth surface, the air cushion effect is produced. The tooth surface is apt to be eroded due to the increase in the impact due to the thinning.
【０００９】本発明の目的は、ロータ歯面の油ミストに
よる侵食を防止することにある。An object of the present invention is to prevent the erosion of the rotor tooth surface by oil mist.
【００１０】[0010]
【課題を解決するための手段】閉込空間に通じる導入穴
を吐出側ケーシングに設け、この導入穴を通して、アン
ロード運転時に圧縮空気を供給できる構造とする。A discharge side casing is provided with an introduction hole communicating with a confined space, and compressed air can be supplied through the introduction hole during unloading operation.
【００１１】[0011]
【作用】アンロード運転時にオイルセパレータ内の圧縮
空気を、導入穴を通して閉込空間内に送り込む。これに
より、閉込空間内の負圧を緩和し圧力を高めて、油ミス
トがロータ歯面に衝突する速度を小さくするとともに、
エアクッション効果によって、衝突エネルギを緩和させ
る。[Operation] During the unloading operation, the compressed air in the oil separator is sent into the enclosed space through the introduction hole. This reduces the negative pressure in the confined space and increases the pressure to reduce the speed at which the oil mist collides with the rotor tooth surface, and
The air cushion effect reduces the collision energy.
【００１２】[0012]
【実施例】本発明の実施例を図１〜図３に従って説明す
る。Embodiments of the present invention will be described with reference to FIGS.
【００１３】図１は給油式スクリュー２段空気圧縮機ユ
ニットの系統図である。吸入絞り弁３から吸われた空気
は、１段側圧縮機１で約２kgf／cm2g まで圧縮された
後、２段側圧縮機２に吸われ、ここで７kgf／cm2g に圧
縮されて吐出され、オイルセパレータ４で空気中の油を
分離した後調圧弁５，逆止弁６を通り、アフタークーラ
７で冷やされて吐出される。オイルセパレータ４の下部
に溜った油は、オイルセパレータ４内の圧力と圧縮機の
給油口との圧力差で流れ、オイルクーラ８で冷やされた
後、フィルタ９を通って、１段側圧縮機１と２段側圧縮
機２へ給油される。アフタークーラ７の出口での空気消
費量が減少すると圧縮機の容量制御のためにアンロード
運転を行なう。FIG. 1 is a system diagram of a refueling screw two-stage air compressor unit. The air sucked from the suction throttle valve 3 is compressed by the first-stage compressor 1 to about 2 kgf / cm 2 g, and then sucked by the second-stage compressor 2, where it is compressed to 7 kgf / cm 2 g. The oil in the air is separated by the oil separator 4, and after passing through the pressure regulating valve 5 and the check valve 6, the oil is cooled by the after cooler 7 and discharged. The oil accumulated in the lower portion of the oil separator 4 flows due to the pressure difference between the pressure inside the oil separator 4 and the oil supply port of the compressor, and after being cooled by the oil cooler 8, it passes through the filter 9 and the first stage compressor. Oil is supplied to the first and second stage compressors 2. When the air consumption at the outlet of the aftercooler 7 decreases, unloading operation is performed to control the capacity of the compressor.
【００１４】アンロード運転方法は、消費空気量の減少
による吐出圧力の上昇により圧力調整弁１０が開きオイ
ルセパレータ４内の空気を吸入絞り弁３へ送り、弁の開
度を調整して吸入空気量を制御するサクションアンロー
ド運転（以下ｓアン運転と称する）と消費空気量が非常
に少なくなった場合、アフタークーラ出口側の圧力上昇
を圧力スイッチ１３で検出し放気電磁弁１１を開くこと
により、オイルセパレータ４内の空気を吸入絞り弁３へ
送り弁を全閉にするとともに、オイルセパレータ４内の
空気を放気サイレンサ１２から放気し吐出圧力を下げて
負荷を軽減するインテグラルアンロード運転（以下ｉア
ン運転と称する）の２通りの方法がある。In the unloading operation method, the pressure adjusting valve 10 is opened by the increase of the discharge pressure due to the decrease of the consumed air amount, the air in the oil separator 4 is sent to the intake throttle valve 3, and the opening degree of the valve is adjusted to adjust the intake air. When the suction unload operation (hereinafter referred to as s unload operation) that controls the amount and the consumed air amount become very small, the pressure switch 13 detects the pressure increase at the outlet side of the aftercooler and the air release solenoid valve 11 is opened. In this way, the air in the oil separator 4 is sent to the suction throttle valve 3 to fully close the valve, and the air in the oil separator 4 is discharged from the discharge silencer 12 to reduce the discharge pressure and reduce the load. There are two methods of operation (hereinafter referred to as i-an operation).
【００１５】本発明では、圧力調整弁１０の出口側と放
気電磁弁１１の出口側は後述する１段側圧縮機１の吐出
側の閉込空間に通じる導入穴に配管１４で結ばれてい
る。このため、アンロード時に、オイルセパレータ４内
の圧縮空気を閉込空間へ供給できる系統になっている。In the present invention, the outlet side of the pressure control valve 10 and the outlet side of the discharge solenoid valve 11 are connected by piping 14 to an introduction hole leading to a closed space on the discharge side of the first-stage compressor 1 described later. There is. For this reason, the system is such that compressed air in the oil separator 4 can be supplied to the confined space during unloading.
【００１６】図２は１段側圧縮機のスクリューロータの
吐出側端面において吸入側から見たロータの噛合状況を
示すロータの軸の断面図である。雄ロータ１５と雌ロー
タ１６の歯溝間の空気と油が吐出ポートから吐出された
後には雄ロータ１５と雌ロータ１６の歯溝間には図中に
示す僅かな閉込空間が残る。この閉込空間は雄ロータ１
５と雌ロータ１６の噛合いによって形成されるシールラ
イン１９（ロータの軸直角断面に投影した線）と、Ｄケ
ーシング１７の吐出端面の間で囲まれた空間である。FIG. 2 is a sectional view of the rotor shaft showing a meshing state of the rotor seen from the suction side at the discharge side end surface of the screw rotor of the first-stage compressor. After the air and oil between the tooth grooves of the male rotor 15 and the female rotor 16 are discharged from the discharge port, a small confined space shown in the figure remains between the tooth grooves of the male rotor 15 and the female rotor 16. This enclosed space is the male rotor 1
5 is a space surrounded by a seal line 19 (a line projected on a cross section perpendicular to the axis of the rotor) formed by the meshing of 5 and the female rotor 16 and the discharge end surface of the D casing 17.
【００１７】図２のＡ−Ａ断面（雄ロータ１５と雌ロー
タ１６のそれぞれの軸心を結ぶ線上の断面）を図３に示
す。ロータの吐出側端面を形成するＤケーシング１７に
は、閉込空間につながる位置に、圧縮空気導入穴１８が
設けてある。この穴を、上述の図１における圧力調整弁
１０と放気電磁弁１１の出口側の配管１４と連通するこ
とによって、アンロード時に圧縮空気を導入穴１８を通
して閉込空間へ供給することができる。FIG. 3 shows an AA cross section of FIG. 2 (a cross section on a line connecting the respective axial centers of the male rotor 15 and the female rotor 16). The D casing 17 forming the discharge side end surface of the rotor is provided with a compressed air introduction hole 18 at a position connected to the closed space. By communicating this hole with the pressure adjusting valve 10 and the pipe 14 on the outlet side of the discharge solenoid valve 11 in FIG. 1 described above, compressed air can be supplied to the confined space through the introduction hole 18 during unloading. ..
【００１８】これによって、アンロード運転時の閉込空
間内の圧力を、従来技術の場合の負圧“−”６４０mmＨ
ｇに対して、ｓアン時で約８kgf／cm2g に又、ｉアン時
で約２kgf／cm2g に高めることができる。As a result, the pressure in the confined space during the unloading operation is reduced to the negative pressure "-" 640 mmH in the case of the prior art.
With respect to g, it can be increased to about 8 kgf / cm 2 g at s-an and about 2 kgf / cm 2 g at i-an.
【００１９】この圧力は圧縮空気の供給量をオリフィス
等で調整することにより変えることは可能である。This pressure can be changed by adjusting the supply amount of compressed air with an orifice or the like.
【００２０】[0020]
【発明の効果】閉込空間内の油ミストがロータの回転に
伴ってシールラインから噴出する時に油ミストがロータ
歯面に衝突する速度は相対速度差として雄ロータ側はｖ
M −Ｖ，雌ロータ側はｖF −Ｖとなる（ここで、Ｖは閉
込空間内の圧力と吸入側の圧力との差圧により決まる油
ミストの噴出速度、ｖM，ｖFはそれぞれ雄ロータと雌ロ
ータの歯面の進み速度である）。油ミストがロータ歯面
に衝突することによって生じる侵食を防止するために
は、ｖM，ｖFが一定で小さくできない条件下では上述の
Ｖを大きくして衝突速度を小さくすることが得策であ
る。The speed at which the oil mist collides with the tooth flank of the rotor when the oil mist in the confined space is ejected from the seal line as the rotor rotates is expressed as a relative speed difference by v on the male rotor side.
M −V, v F −V on the female rotor side (here, V is the jet speed of the oil mist determined by the pressure difference between the pressure in the confined space and the suction side, and v M and v F are respectively The speed of advance of the tooth surface of the male and female rotors). In order to prevent the erosion caused by the collision of the oil mist with the tooth surface of the rotor, it is a good idea to increase the above-mentioned V to reduce the collision speed under the condition that v M and v F are constant and cannot be reduced. ..
【００２１】本発明の実施によって、アンロード運転時
に閉込空間内の圧力を高めることによって吸入側圧力と
の差圧が大となりＶを大きくすることができる。このた
め油ミストがロータ歯面に衝突する速度を小さくするこ
とができる。又、閉込空間内に供給する圧縮空気による
エアークッション効果によって、油ミストがロータ歯面
に衝突する衝撃を緩和することができる。By implementing the present invention, by increasing the pressure in the enclosed space during unloading operation, the differential pressure from the suction side pressure becomes large and V can be increased. Therefore, the speed at which the oil mist collides with the tooth surface of the rotor can be reduced. Further, the impact of the oil mist colliding with the tooth surface of the rotor can be alleviated by the air cushion effect of the compressed air supplied into the enclosed space.
【００２２】以上のことから、油ミストがロータ歯面に
衝突することにより生じる侵食を防止することが可能で
ある。From the above, it is possible to prevent the erosion caused by the oil mist colliding with the rotor tooth surface.
【図１】本発明の実施例における給油式スクリュー２段
空気圧縮機の系統図。FIG. 1 is a system diagram of a refueling screw two-stage air compressor according to an embodiment of the present invention.
【図２】本発明の実施例における１段側圧縮機のスクリ
ューロータの吐出側端面において吸入側から見たロータ
の軸の断面。FIG. 2 is a cross-sectional view of the rotor shaft as seen from the suction side at the discharge-side end surface of the screw rotor of the first-stage compressor in the embodiment of the present invention.
【図３】図２のＡ−Ａ断面図。3 is a sectional view taken along line AA of FIG.
【図４】従来技術における給油式スクリュー２段空気圧
縮機の系統図。FIG. 4 is a system diagram of a refueling screw two-stage air compressor according to a conventional technique.
【図５】従来技術における１段側圧縮機のスクリューロ
ータの吐出側端面において吸入側から見たロータの軸の
断面図。FIG. 5 is a cross-sectional view of the rotor shaft as seen from the suction side at the discharge-side end surface of the screw rotor of the conventional one-stage compressor.
【図６】図５のＡ−Ａ断面図。6 is a cross-sectional view taken along the line AA of FIG.
１５…雄ロータ、１６…雌ロータ、１７…Ｄケーシン
グ、１８…圧縮空気導入穴、１９…シールライン。15 ... Male rotor, 16 ... Female rotor, 17 ... D casing, 18 ... Compressed air introduction hole, 19 ... Seal line.
Claims (1)
機の吐出側端面で、前記雄雌ロータ間と吐出端面との間
に構成される閉込空間内に通じる導入穴を設け、前記閉
込空間内の負圧を緩和させるため前記導入穴を通して、
アンロード運転中に、空間内に圧縮空気を供給したこと
を特徴とする給油式スクリュー圧縮機。1. A screw compressor comprising a pair of male and female rotors, wherein a discharge side end face is provided with an introduction hole communicating with a closed space formed between the male and female rotors and the discharge end face, Through the introduction hole to relieve the negative pressure in the space,
A refueling screw compressor characterized in that compressed air is supplied into the space during unloading operation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10642192A JPH05302582A (en) | 1992-04-24 | 1992-04-24 | Lubrication type screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10642192A JPH05302582A (en) | 1992-04-24 | 1992-04-24 | Lubrication type screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05302582A true JPH05302582A (en) | 1993-11-16 |
Family
ID=14433204
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10642192A Pending JPH05302582A (en) | 1992-04-24 | 1992-04-24 | Lubrication type screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05302582A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100704700B1 (en) * | 2005-06-01 | 2007-04-09 | (주) 정수엔지니어링 | Corrosion Prevention Device and Method Thereof |
| CN101900119A (en) * | 2009-05-28 | 2010-12-01 | 株式会社日立工业设备技术 | Oil free screw compressor |
-
1992
- 1992-04-24 JP JP10642192A patent/JPH05302582A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100704700B1 (en) * | 2005-06-01 | 2007-04-09 | (주) 정수엔지니어링 | Corrosion Prevention Device and Method Thereof |
| CN101900119A (en) * | 2009-05-28 | 2010-12-01 | 株式会社日立工业设备技术 | Oil free screw compressor |
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