JPH0551076B2 - - Google Patents
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- Publication number
- JPH0551076B2 JPH0551076B2 JP59222028A JP22202884A JPH0551076B2 JP H0551076 B2 JPH0551076 B2 JP H0551076B2 JP 59222028 A JP59222028 A JP 59222028A JP 22202884 A JP22202884 A JP 22202884A JP H0551076 B2 JPH0551076 B2 JP H0551076B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- discharge chamber
- discharge
- pressure
- chamber
- 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 - Lifetime
Links
- 238000007906 compression Methods 0.000 claims description 13
- 230000006835 compression Effects 0.000 claims description 12
- 239000012530 fluid Substances 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 238000010586 diagram Methods 0.000 description 10
- 230000007423 decrease Effects 0.000 description 9
- 238000001816 cooling Methods 0.000 description 8
- 238000000034 method Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000007664 blowing Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
Landscapes
- Control Of Positive-Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
オイルフリー式容積形流体機械の吐出温度低減
法に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a method for reducing the discharge temperature of an oil-free positive displacement fluid machine.
容積形流体機械において、吸気量を減らした運
転（部分あるいは無負荷運転という）の際の吐出
ガス温度を低くする方法として、特公昭55−
17236号に示されているように、吐出室に連通し
ない圧縮室に新鮮な空気を注入することが知られ
ている。
In positive displacement fluid machines, a method for lowering the discharge gas temperature during operation with a reduced intake air amount (referred to as partial or no-load operation) was developed in the 1980s.
17236, it is known to inject fresh air into a compression chamber that does not communicate with the discharge chamber.
この方法を容積形流体機械に適用すると、空気
が圧縮室に注入されることになり、注入された空
気は吐出室に至るまでに再圧縮され、これにより
圧縮熱が発生し、この熱のために吐出室に吐出さ
れたときは高温となり、吐出室のガス温度を低く
することは期待できない。 When this method is applied to positive displacement fluid machines, air is injected into the compression chamber, and the injected air is recompressed before reaching the discharge chamber, which generates compression heat. When the gas is discharged into the discharge chamber, the temperature is high, and it cannot be expected to lower the gas temperature in the discharge chamber.
また、注入された空気を再圧縮するので不必要
な圧縮動力を消費する。 Furthermore, since the injected air is recompressed, unnecessary compression power is consumed.
本発明の目的は、無負荷運転時における吐出室
のガス温度を、両ロータ間およびケーシング間の
隙が実質的に零になる温度よりも低く望ましくは
全負荷運転時の吐出ガス温度を著しく超えない程
度に維持できるオイルフリー式容積形流体機械を
提供することにある。
An object of the present invention is to reduce the gas temperature in the discharge chamber during no-load operation to a temperature lower than the temperature at which the gap between both rotors and between the casing becomes substantially zero, and desirably to significantly exceed the discharge gas temperature during full-load operation. The object of the present invention is to provide an oil-free positive displacement fluid machine that can be maintained to a certain degree.
本発明の特徴は、全負荷運転時における吐出ガ
ス温度よりも低温ガスを、吐出室とこれに常時連
らなつている圧縮室を含む吐出領域に吹き出す手
段を備えたことにある。
A feature of the present invention is that it includes means for blowing gas at a temperature lower than the discharge gas temperature during full-load operation into a discharge region including a discharge chamber and a compression chamber that is constantly connected to the discharge chamber.
このように構成すると、温度を低くすべき吐出
領域に、圧縮室を経由することなく、低温ガスが
吹き出されるので、注入ガスは圧縮による圧縮熱
を発生することがなくなり、効果的に吐出領域の
ガス温度を低下させることができる。 With this configuration, low-temperature gas is blown out to the discharge area where the temperature should be kept low, without passing through the compression chamber, so the injected gas does not generate compression heat due to compression, and the temperature is effectively reduced to the discharge area. gas temperature can be lowered.
以下本発明の一実施例を第１図〜第５図により
説明する。
An embodiment of the present invention will be described below with reference to FIGS. 1 to 5.
第１図において、スクリユーロータ１は電動機
２によつて駆動され、吸込室３の空気を吸込んで
圧縮し、高圧の空気を吐出室４に吐出する。全負
荷時には吸込室の弁５は全開され、空気は吸込フ
イルタ６より吸込まれて吸込室３に入る。圧縮機
より吐出された高圧空気は逆止弁７を経てアフタ
ーローラ８に入り、常温ないし60〜70℃程度の温
度まで冷却された後、ラインの配管９に送り出さ
れる。アフタークーラからラインまでの間には、
空気を溜めるタンクが設けられることもある。 In FIG. 1, a screw rotor 1 is driven by an electric motor 2, sucks in air from a suction chamber 3, compresses it, and discharges high-pressure air into a discharge chamber 4. At full load, the valve 5 of the suction chamber is fully opened, and air is sucked through the suction filter 6 and enters the suction chamber 3. High-pressure air discharged from the compressor passes through a check valve 7, enters an after roller 8, is cooled to a temperature ranging from room temperature to about 60 to 70°C, and is then sent to a line piping 9. Between the aftercooler and the line,
A tank for storing air may also be provided.
ラインの空気使用量が多いときには、３方電磁
弁１１のポート１２とポート１３とが接触し、ポ
ート１４は閉じられている。また、２方電磁弁１
５は閉止されている。ラインの空気使用量が減少
する配管９の圧力が上昇するので、これを圧力ス
イツチ１０が検知し、３方電磁弁１１のポート１
３を閉止し、同時にポート１２とポート１４とを
接続する。さらに、２方電磁弁１５を開く。３方
電磁弁のポート１２とポート１４との接続によ
り、配管９の中の高圧空気はシリンダ１６中に送
りこまれ、ピストン１７を押し、吸込室弁５を閉
じる。このため圧縮機の吸込室は真空状態にな
る。一方、２方電磁弁の開放により、吐出室４の
高圧空気は大量に開放され、吐出圧力は低下す
る。アフタークーラからの高圧空気の逆流は逆止
弁７によつて阻止される。この状態では、圧縮機
の吐出し空気量はほぼ零となり、また軸動力も小
さくなる。 When the amount of air used in the line is large, ports 12 and 13 of the three-way solenoid valve 11 are in contact, and port 14 is closed. In addition, 2-way solenoid valve 1
5 is closed. As the pressure in the piping 9 increases as the amount of air used in the line decreases, the pressure switch 10 detects this and the port 1 of the three-way solenoid valve 11 increases.
3 and connect ports 12 and 14 at the same time. Furthermore, the two-way solenoid valve 15 is opened. Due to the connection between ports 12 and 14 of the three-way solenoid valve, high pressure air in the pipe 9 is fed into the cylinder 16, pushing the piston 17 and closing the suction chamber valve 5. Therefore, the suction chamber of the compressor becomes in a vacuum state. On the other hand, by opening the two-way solenoid valve, a large amount of high-pressure air in the discharge chamber 4 is released, and the discharge pressure decreases. A check valve 7 prevents the high pressure air from flowing back from the aftercooler. In this state, the amount of air discharged from the compressor becomes almost zero, and the shaft power also becomes small.
ラインの配管９の中の空気量が減つてくると、
配管中の空気圧力が下がり、圧力スイツチ１０が
これを検知して、２方電磁弁１５を閉じ、同時に
３方電磁弁のポート１４を閉じ、さらにポート１
２とポート１３を接続する。このため、吸込室弁
５が開き、空気が圧縮機に吸込まれ圧縮される。 When the amount of air in the line piping 9 decreases,
The air pressure in the piping decreases, the pressure switch 10 detects this, closes the two-way solenoid valve 15, simultaneously closes the port 14 of the three-way solenoid valve, and then closes the port 1 of the three-way solenoid valve.
Connect 2 and port 13. Therefore, the suction chamber valve 5 opens, and air is sucked into the compressor and compressed.
圧力スイツチ１０によつて操作される第２の２
方電磁弁２０があり、この２方電磁弁の一端は、
アフタークーラ経過後の配管９に、また他端は圧
縮室の吐室に挿入したパイプ２２にそれぞれ接続
している。配管９から２方電磁弁２０を経て吐出
室中の吹吹出し口３９に至る管路の途中には絞り
２１を設けてある。この絞り２１は、必ずしも本
発明の構成要件ではない。 a second 2 operated by pressure switch 10;
There is a two-way solenoid valve 20, and one end of this two-way solenoid valve is
The other end is connected to the pipe 9 after passing through the aftercooler, and the other end is connected to a pipe 22 inserted into the discharge chamber of the compression chamber. A restrictor 21 is provided in the middle of the pipe line from the pipe 9 through the two-way solenoid valve 20 to the air outlet 39 in the discharge chamber. This aperture 21 is not necessarily a component of the present invention.
第４図には吐出室内に設けた吹出し口の一例を
示す。図において、１はロータ、３は吸込室、４
は吐出室である。吹出し口３９につながるパイプ
２２の一端は上記のように第３図の２方電磁弁２
０を介して配管９と接続している。パイプ２２の
他端は第４図のように、吐出室内で、ロータの近
くに口を開けている。 FIG. 4 shows an example of an outlet provided in the discharge chamber. In the figure, 1 is the rotor, 3 is the suction chamber, and 4 is the rotor.
is the discharge chamber. One end of the pipe 22 connected to the outlet 39 is connected to the two-way solenoid valve 2 shown in FIG.
It is connected to piping 9 via 0. As shown in FIG. 4, the other end of the pipe 22 opens in the discharge chamber near the rotor.
第３図において、ラインの空気使用量が減ると
配管９の中の圧力が下がり、圧力スイツチが作動
して、第１図で述べたのと同じように、吸込室弁
５が閉じられ、また、２方電磁弁１５が開いて、
吐出室の高圧空気が大気に開放される。それと同
時に、本実施例では第２の２方電磁弁２０が開放
され、配管９の中の高圧の空気が吹出し口３９か
ら吐出室に吹出される。ロータから吐出される空
気は吹出し口３９から吹出された空気と混合し、
温度が下がる。何故なら、吹出し口３９から吹出
される空気はアフタークーラ８を通過した後の空
気なので温度が低いからである。 In FIG. 3, when the air usage in the line decreases, the pressure in the pipe 9 decreases, and the pressure switch is actuated, closing the suction chamber valve 5 in the same manner as described in FIG. , the two-way solenoid valve 15 opens,
High pressure air in the discharge chamber is released to the atmosphere. At the same time, in this embodiment, the second two-way solenoid valve 20 is opened, and the high-pressure air in the pipe 9 is blown out from the outlet 39 into the discharge chamber. The air discharged from the rotor mixes with the air discharged from the outlet 39,
The temperature drops. This is because the air blown out from the air outlet 39 has a low temperature since it has passed through the aftercooler 8.
吐出室のみでなく、吐出行程中のロータ内の空
気温度も本発明により低くなる。第２図で説明し
たように、無負荷時には、吐出ポートに開口する
直前の作動空間内圧力は一般には吐出室の圧力よ
り低く、吐出ポートに開口した直後に吐出室から
多量の空気が作動空間内に流れこむ。本発明によ
れば上記のように吐出室内の空気温度は低くんつ
ているので、吐出ポートに開口した直後の作動空
間には冷たい空気が流れこみ、ロータ内も冷やさ
れる。 The present invention lowers the air temperature not only in the discharge chamber but also in the rotor during the discharge stroke. As explained in Figure 2, when there is no load, the pressure inside the working space immediately before opening to the discharge port is generally lower than the pressure in the discharge chamber, and a large amount of air flows into the working space from the discharge chamber immediately after opening to the discharge port. Flow inside. According to the present invention, since the air temperature in the discharge chamber is low as described above, cold air flows into the working space immediately after opening to the discharge port, and the inside of the rotor is also cooled.
さらに、吐出室の温度が下がれば、ロータ間あ
るいはロータ・ケーシング間のすきまを通つて吐
出側から低圧側に漏れる空気の温度も低くなるの
で、圧縮行程中の空気温度も下がる。 Furthermore, if the temperature of the discharge chamber decreases, the temperature of the air leaking from the discharge side to the low pressure side through the gap between the rotors or between the rotor and the casing also decreases, so the temperature of the air during the compression stroke also decreases.
第５図は、吐出室への吹出し方法の他の実施例
を示す。本図は、吐出行程中のロータを周方向に
模型的に展開したもので、３０及び３１は互いに
隣りあうローブ、３２はこれらのローブによつて
形成された溝、すなわち作動空間である。ローブ
及び溝はロータの回転に伴つて矢印３３の方向に
移動する。３５はケーシング、３６は吐出室であ
る。吐出室に挿入されパイプ２２は、一端はロー
タの吐出端面に面して口を開け、他端は２方電磁
弁２０（第３図）を介してアフタークーラ後流の
配管９に接続している。パイプ２２の空気吹出し
口３９は、作動空間が圧縮行程を終つて最初に吐
出室に開口する附近に設けられる。 FIG. 5 shows another embodiment of the method of blowing into the discharge chamber. This figure is a schematic diagram of the rotor during the discharge stroke developed in the circumferential direction, with lobes 30 and 31 adjacent to each other, and 32 a groove formed by these lobes, that is, an operating space. The lobes and grooves move in the direction of arrow 33 as the rotor rotates. 35 is a casing, and 36 is a discharge chamber. The pipe 22 inserted into the discharge chamber has one end opened facing the discharge end surface of the rotor, and the other end connected to the piping 9 downstream of the aftercooler via a two-way solenoid valve 20 (Fig. 3). There is. The air outlet 39 of the pipe 22 is provided near where the working space first opens into the discharge chamber after the compression stroke.
ロータが回転し、点３８が点３７を通過する
と、３２の作動空間が吐出室に開口し、無負荷状
態では吐出室の空気が作動空間内に流入するが、
本実施例のように、空気の吹出し口３９を上記の
ような位置に設けておけば、吐出室の空気より
は、パイプ２２内の冷えた空気が優先的に作動空
間内に流れこみ、ロータの冷却は一そう良くな
る。 When the rotor rotates and point 38 passes point 37, the working space 32 opens into the discharge chamber, and under no-load conditions, the air in the discharge chamber flows into the working space;
If the air outlet 39 is provided in the above position as in this embodiment, the cooled air in the pipe 22 will preferentially flow into the working space rather than the air in the discharge chamber, and the rotor The cooling will be much better.
第６図は吐出室の空気吹出し口の、他の例を示
す。本図は、ロータの回転軸に直角な断面内で吐
出ポート附近を切断した図を示し、３６は吐出室
である。雄ロータ４０及び雌ロータ４１がそれぞ
れ矢印４３及び４４のように回転し、雄ロータの
ローブ４５及び雌ロータのローブ４６がそれぞれ
吐出ポートの縁４７及び４８を通過すると、雄ロ
ータ側の作動空間４９及び雌ロータ側の作動空間
５０がそれぞれ吐出室に開口する。２個の空気の
吹出し口３９はそれぞれ図のように、吐出しポー
トの縁４７及び４８にほぼ沿つて設けられる。吹
出し口３９とつながるパイプ２２の他端は前記と
同じく電磁弁２０（第３図）を介してアフターク
ーラ後流の配管９と接続している。無負荷状態で
は、吹出し口３９から冷たい空気が吹出される
が、この流れは、吐出ポートに開口した作動空間
の口に沿つて流れるので、効率良く内へ冷たい空
気が流れ、ロータの冷却効果がさらに良くなる。 FIG. 6 shows another example of the air outlet of the discharge chamber. This figure shows the vicinity of the discharge port cut in a cross section perpendicular to the rotational axis of the rotor, and 36 is a discharge chamber. When the male rotor 40 and the female rotor 41 rotate as indicated by arrows 43 and 44, respectively, and the lobe 45 of the male rotor and the lobe 46 of the female rotor pass the edges 47 and 48 of the discharge port, respectively, the working space 49 on the male rotor side The working space 50 on the female rotor side and the female rotor side respectively open into the discharge chamber. Two air outlets 39 are provided generally along edges 47 and 48 of the outlet ports, respectively, as shown. The other end of the pipe 22 connected to the outlet 39 is connected to the piping 9 downstream of the aftercooler via the electromagnetic valve 20 (FIG. 3), as described above. In a no-load state, cold air is blown out from the outlet 39, but this flow flows along the opening of the working space that opens to the discharge port, so the cold air flows inward efficiently and has a cooling effect on the rotor. It gets even better.
以上の実施例はすべてのアフタークーラ後の圧
力が無負荷時の吐出室圧力より高い場合に適用さ
れるが、第７図に示す実施例では、吐出室圧力よ
り低い圧力の空気でも冷却が可能である。第７図
は第５図と同じく、吐出行程中のロータを周方向
に展開したものである。図において、隣り合うロ
ーブ３０及び３１は、ロータの回転によつて矢印
３３の方向に進み溝３２に先行するローブ３０の
端面３４の最後部３８が吐出ポートの縁３７を通
過した直後から吐出行程が始まるが、冷却用空気
の吹出し口３９は、作動空間３２が吐出行程にか
かる前に、作動空間に口を開ける。無負荷時に
は、第２図に示したように、吐出行程にかかる前
の作動空間内の圧力は真空に近く、吹出し口３９
に供給する空気の圧力は吐出室の圧力より低くで
もよい。したがつて、冷却用の空気は、アフター
クーラ通過後の配管から取る必要はなく、例えば
大気から供給することもできる。真空ポンプの場
合には、吐出室圧力よりも高い圧力は供給できな
いので、この実施例のように吹出し口を設け、冷
却用の空気を大気からとりこむのが有効である。 The above embodiments are applied when the pressure after all aftercoolers is higher than the discharge chamber pressure under no load, but the embodiment shown in Fig. 7 allows cooling even with air at a pressure lower than the discharge chamber pressure. It is. FIG. 7, like FIG. 5, shows the rotor during the discharge stroke expanded in the circumferential direction. In the figure, the adjacent lobes 30 and 31 advance in the direction of arrow 33 due to the rotation of the rotor and begin the discharge stroke immediately after the rearmost part 38 of the end face 34 of the lobe 30 preceding the groove 32 passes the edge 37 of the discharge port. However, the cooling air outlet 39 opens into the working space before the working space 32 starts the discharge stroke. When there is no load, as shown in Fig. 2, the pressure in the working space before the discharge stroke is close to vacuum, and the air outlet 39
The pressure of the air supplied to the discharge chamber may be lower than the pressure of the discharge chamber. Therefore, the cooling air does not need to be taken from the piping after passing through the aftercooler, and can be supplied from the atmosphere, for example. In the case of a vacuum pump, it is not possible to supply a pressure higher than the discharge chamber pressure, so it is effective to provide a blow-off port and take in cooling air from the atmosphere as in this embodiment.
以上の実施例はいずれもスクリユー圧縮機を例
にとつて説明したが、本発明の他の原理のオイル
フリー流体機械、例えばスクロール形流体機械、
可動翼形流体機械あるいはスクリユー真空ポンプ
にもそのまま適用できる。 The above embodiments have all been explained using a screw compressor as an example, but oil-free fluid machines based on other principles of the present invention, such as scroll-type fluid machines,
It can also be applied directly to movable airfoil fluid machines or screw vacuum pumps.
次に第６図に場すPV線図によつて本発明の実
施例の効果をさらに詳細に述べる。 Next, the effects of the embodiment of the present invention will be described in more detail with reference to the PV diagram shown in FIG.
第６図において、実線は、全負荷のPV線図、
点線が無負荷時における本発明の実施例のPV線
図、一点鎖線が無負荷時における従来のものの
PV線図である。 In Figure 6, the solid line is the PV diagram at full load,
The dotted line is the PV diagram of the embodiment of the present invention under no load, and the dashed line is the PV diagram of the conventional one under no load.
It is a PV diagram.
また横軸のVsが吸込完了、VDが吐出開始、VN
が空気の注入位置である。 Also, V s on the horizontal axis is suction completion, V D is discharge start, V N
is the air injection position.
本発明のPV線図A′−B′−C′−E′−D′−A′で囲
まれた面積は、従来のPV線図A′−B′−F″−G″−
C″−E′−D′−A′で囲まれた面積より小さく、本
発明は消費電力が少なくてすむ。また本発明は、
圧縮過程での空気注入がないので、G″→C″まで
圧縮する際の圧縮機が発生しない。従つて、冷却
のために注入されたガスがもつている熱量のすべ
てが冷却に有効に利用できる。 The area surrounded by the PV diagram A'-B'-C'-E'-D'-A' of the present invention is the same as that of the conventional PV diagram A'-B'-F"-G"-
It is smaller than the area surrounded by C″-E′-D′-A′, and the present invention consumes less power.
Since there is no air injection during the compression process, no compressor is generated when compressing from G″ to C″. Therefore, all of the heat contained in the gas injected for cooling can be effectively used for cooling.
以上のように、本発明によれば、オイルフリー
スクリユー圧縮機の無負荷時の異常な温度上昇を
避けることができるので、ロータの焼損の危険性
がなくなるほか、従来のように異常な温度上昇を
見越して必要以上に大きなすきまを設ける必要が
なく、漏れ損失が減り、圧縮機効率が向上する。
As described above, according to the present invention, it is possible to avoid an abnormal temperature rise when the oil-free screw compressor is under no load. There is no need to create an unnecessarily large gap in anticipation of the rise, reducing leakage loss and improving compressor efficiency.
第１図は本発明の一実施例の全体構成図、第２
図は第１図の圧縮機部分の詳細図、第３図及び第
４図はそれぞれ別々の他の実施例における圧縮機
吐出ポート附近の詳細図、第５図はとくに真空ポ
ンプに適した実施例の説明図、第６図はPV線図
である。
１……ロータ、４……吐出し室、２０……２方
電磁弁、２２……パイプ、３９……吹出し口、８
……アフタークーラ、１０……圧力スイツチ。
Fig. 1 is an overall configuration diagram of an embodiment of the present invention, Fig. 2
The figure is a detailed view of the compressor part in Figure 1, Figures 3 and 4 are detailed views of the vicinity of the compressor discharge port in separate other embodiments, and Figure 5 is an embodiment particularly suitable for a vacuum pump. 6 is a PV diagram. 1...Rotor, 4...Discharge chamber, 20...2-way solenoid valve, 22...Pipe, 39...Blowout port, 8
...Aftercooler, 10...Pressure switch.
Claims (1)
開放弁１５を備え、吸込室弁を閉じ、吐出室開放
弁を開放して吸込室圧力及び吐出圧力をともに全
負荷時よりも下げて無負荷運転を行うオイルフリ
ー容積形圧縮機において、無負荷運転時に、アフ
タークーラ後流のガスの一部を吐出室内に吹出さ
せる手段を有することを特徴とするオイルフリー
式容積形流体機械。 ２ 特許請求の範囲第１項において、作動空間が
圧縮行程を終えて最初に吐出し室に開口する位置
近くに、空気の吹出し口３９を設けたことを特徴
とするオイルフリー式容積形流体機械。 ３ 特許請求の範囲第１項において圧力及び温度
ともに吐出室の状態より低いガスを、吐出室に開
いていない作動空間に噴出させることを特徴とす
るオイルフリー式容積形流体機械。[Claims] 1. A suction chamber valve 5, an aftercooler 8, and a discharge chamber release valve 15 are provided, and the suction chamber valve is closed and the discharge chamber release valve is opened to maintain both the suction chamber pressure and the discharge pressure at full load. An oil-free positive displacement compressor that performs no-load operation with a pressure lower than Fluid machinery. 2. An oil-free positive displacement fluid machine according to claim 1, characterized in that an air outlet 39 is provided near the position where the working space first opens into the discharge chamber after the compression stroke. . 3. An oil-free positive displacement fluid machine according to claim 1, characterized in that the gas whose pressure and temperature are both lower than the conditions in the discharge chamber is ejected into a working space that is not open to the discharge chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59222028A JPS61101693A (en) | 1984-10-24 | 1984-10-24 | Oil free displacement type hydraulic machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59222028A JPS61101693A (en) | 1984-10-24 | 1984-10-24 | Oil free displacement type hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61101693A JPS61101693A (en) | 1986-05-20 |
| JPH0551076B2 true JPH0551076B2 (en) | 1993-07-30 |
Family
ID=16775958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59222028A Granted JPS61101693A (en) | 1984-10-24 | 1984-10-24 | Oil free displacement type hydraulic machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61101693A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4812110A (en) * | 1986-08-11 | 1989-03-14 | Kabushiki Kaisha Kobe Seiko Sho | Oil-free screw compressor with bypass of cooled discharged gas |
| JPS6345488A (en) * | 1986-08-11 | 1988-02-26 | Kobe Steel Ltd | Oil-free screw compressor |
| JPH07103854B2 (en) * | 1988-03-25 | 1995-11-08 | 株式会社神戸製鋼所 | Screw type vacuum pump |
| JP2688945B2 (en) * | 1988-09-14 | 1997-12-10 | 北越工業株式会社 | Capacity controller for oil-free screw compressor |
-
1984
- 1984-10-24 JP JP59222028A patent/JPS61101693A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61101693A (en) | 1986-05-20 |
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| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |