JPH0443891A - Screw fluid machines and multi-stage screw fluid machines - Google Patents
Screw fluid machines and multi-stage screw fluid machinesInfo
- Publication number
- JPH0443891A JPH0443891A JP2148703A JP14870390A JPH0443891A JP H0443891 A JPH0443891 A JP H0443891A JP 2148703 A JP2148703 A JP 2148703A JP 14870390 A JP14870390 A JP 14870390A JP H0443891 A JPH0443891 A JP H0443891A
- Authority
- JP
- Japan
- Prior art keywords
- lubricating oil
- oil
- gas
- cooling means
- fluid machine
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/06—Heating; Cooling; Heat insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/40—Pumps with means for venting areas other than the working chamber, e.g. bearings, gear chambers, shaft seals
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はスクリュー流体機械に係り、とくに該スクリュ
ー流体機械の吐出側軸受を油冷却するための軸受室およ
び油タンク内の油から発生する油煙の低減に好番なスク
リュー流体機械および多段スクリュー流体機械に関する
。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a screw fluid machine, and particularly to oil smoke generated from oil in a bearing chamber and an oil tank for oil cooling the discharge side bearing of the screw fluid machine. The present invention relates to a screw fluid machine and a multi-stage screw fluid machine that are suitable for reducing.
従来のスクリュー流体機械においては、たとえば神鋼技
報Ｖｏ１．３４第１０４頁メカ＝カルシール付スクリュ
ー圧縮機、とくに第２図に図示されているように、油タ
ンクから油ポンプで汲み上げられた潤滑油は油冷却器、
フィルターに通ってスクリューロータの軸受、タイミン
グギヤ、増速機などを潤滑冷却したのち、直接油タンク
に戻る方式が紹介されている。In a conventional screw fluid machine, for example, a screw compressor with mechanical cal seal, as shown in Figure 2, lubricating oil pumped from an oil tank by an oil pump is oil cooler,
A method is introduced in which oil passes through a filter to lubricate and cool screw rotor bearings, timing gears, speed increasers, etc., and then returns directly to the oil tank.
上記従来技術は、油タンクに戻る潤滑油が各軸受、ギヤ
などで発生する摩擦熱、高温のロータ、ケーシングから
の熱を奪い高油となって油タンクに戻る。またロータ内
部の冷却した高温の潤滑油が油タンクに流れ込むことに
なる。さらに軸受およびギヤを包囲する密閉された軸受
室内は高温のロータ軸部、ケーシングからの放熱と高温
部を通過し、非接触軸封部より高温ガスが流入すること
により、油蒸気を含んだ高温ガスが充満し、潤滑油とと
もに油タンクに流入する。In the above conventional technology, the lubricating oil that returns to the oil tank absorbs frictional heat generated by each bearing, gear, etc., heat from the high-temperature rotor and casing, and returns to the oil tank as a high-quality oil. Furthermore, the cooled high-temperature lubricating oil inside the rotor flows into the oil tank. Furthermore, inside the sealed bearing chamber that surrounds the bearing and gears, high-temperature gas containing oil vapor passes through the high-temperature rotor shaft and casing, passes through the high-temperature section, and enters from the non-contact shaft seal. It is filled with gas and flows into the oil tank along with lubricating oil.
そのため、油タンク内は高温潤滑油と高温ガスにより油
蒸気を含む高温ガスが充満した状態となり、上記油タン
ク内あるいは上気軸受室放気部分から多量の油煙が発生
するという問題があった。Therefore, the inside of the oil tank is filled with high-temperature gas containing oil vapor due to the high-temperature lubricating oil and high-temperature gas, and there is a problem in that a large amount of oil smoke is generated from inside the oil tank or from the air release portion of the upper air bearing chamber.
本発明の目的は、軸受室内および油タンク内に発生する
油煙発生量を低減可能とするスクリュー流体機械および
多段スクリュー流体機械を提供することにある。An object of the present invention is to provide a screw fluid machine and a multistage screw fluid machine that can reduce the amount of oil smoke generated in a bearing chamber and an oil tank.
上記目的を達成するために本発明は、スクリュー流体機
械において、軸受などを内蔵する軸受室と油タンクとの
間を接続する潤滑油戻り流路に潤滑油を冷却するための
潤滑油冷却手段を設けたものである。In order to achieve the above object, the present invention provides a lubricating oil cooling means for cooling lubricating oil in a lubricating oil return passage connecting between a bearing chamber containing a bearing etc. and an oil tank in a screw fluid machine. It was established.
また前記軸受室内に発生するガスを大気中に放出するさ
い冷却して放出ガスの流量を減少するため、前記軸受室
からのガスを油タンクあるいは油分離器を介して大気中
に放出するガス放出流路と、該ガス放出流路の前記軸受
室と油タンクあるいは油分離器との間に放出ガスを冷却
するための放出ガス冷却手段を設けたものである。In addition, in order to cool the gas generated in the bearing chamber and reduce the flow rate of the discharged gas when the gas is discharged into the atmosphere, the gas from the bearing chamber is discharged into the atmosphere through an oil tank or an oil separator. A discharge gas cooling means for cooling the discharge gas is provided between the flow path and the bearing chamber of the gas discharge flow path and the oil tank or oil separator.
また前記潤滑油冷却手段とガス冷却手段の製作費を安価
するため、前記潤滑油冷却手段とガス冷却手段とを一体
に構成したものである。Further, in order to reduce the manufacturing cost of the lubricating oil cooling means and the gas cooling means, the lubricating oil cooling means and the gas cooling means are integrally constructed.
また前記油タンク内の潤滑油の落差を大きくとれるとと
もに、潤滑油が前記油タンク内に噴出するさいに油ミス
トの飛散を防止するため、前記潤滑油戻り流路の油タン
ク側端部を潤滑油油面より下方に位置させたものである
。In addition, in order to increase the head of the lubricating oil in the oil tank and to prevent oil mist from scattering when the lubricating oil is spouted into the oil tank, the end of the lubricating oil return flow path on the oil tank side is lubricated. It is located below the oil level.
また放出ガスが前記油タンク内潤滑油中に浸入するのを
防止するため、ガス放出流路の油タンク側端部を前記油
タンク内潤滑油油面より上方に位置させたものである。Further, in order to prevent the released gas from penetrating into the lubricating oil in the oil tank, the end of the gas releasing flow path on the oil tank side is positioned above the level of the lubricating oil in the oil tank.
また前記潤滑油冷却手段の構成を簡略化するとともに前
記軸受室内の油蒸気の発生量を低減するため、該軸受室
の油溜め部に潤滑油冷却手段（以下第２潤滑油冷却手段
という）を設けたものである。In addition, in order to simplify the configuration of the lubricating oil cooling means and to reduce the amount of oil vapor generated in the bearing chamber, a lubricating oil cooling means (hereinafter referred to as a second lubricating oil cooling means) is installed in the oil reservoir of the bearing chamber. It was established.
また前記潤滑油冷却手段および前記放出ガス冷却手段の
構成を簡略するため、前記第２潤滑油冷却手段を前記軸
受室と一体に構成したものである。Further, in order to simplify the configurations of the lubricating oil cooling means and the discharged gas cooling means, the second lubricating oil cooling means is constructed integrally with the bearing chamber.
また上気目的を達成するために、本発明は多段スクリュ
ー流体機械において、各段の潤滑油冷却手段および放出
ガス冷却手段を一体に構成したものである。Further, in order to achieve the above purpose, the present invention provides a multi-stage screw fluid machine in which the lubricating oil cooling means and discharged gas cooling means of each stage are integrally constructed.
〔作 用〕
本発明によるスクリュー流体機械においては、軸受室内
の高温の潤滑油を油タンク内に戻すさいに潤滑油冷却手
段によって冷却するため、油タンク内の油温を低くする
ことができ、これによって油蒸気の発生を低減すること
ができる。[Function] In the screw fluid machine according to the present invention, the high-temperature lubricating oil in the bearing chamber is cooled by the lubricating oil cooling means when returning it to the oil tank, so the oil temperature in the oil tank can be lowered. This can reduce the generation of oil vapor.
また、潤滑油を前記軸受室から前記タンクに戻す潤滑油
戻り流路とは別に前記軸受室からの高温ガスを大気に放
出するガス放出流路と、該ガス放出流路の前記軸受室と
前記軸タンクとの間に放出ガス冷却手段を設けたので前
記油タンク内の雰囲気温度が低下するとともにガスの体
積流量が減少するため、前記油タンクから大気に放出す
る量を減少することができる。Further, in addition to a lubricating oil return passage that returns lubricating oil from the bearing chamber to the tank, a gas discharge passage that releases high-temperature gas from the bearing chamber to the atmosphere; Since the discharged gas cooling means is provided between the shaft tank and the oil tank, the atmospheric temperature inside the oil tank is lowered and the volumetric flow rate of the gas is reduced, so that the amount discharged from the oil tank to the atmosphere can be reduced.
また前記潤滑油戻り流路の前記油タンク側端部を潤滑油
油面より低く位置させているので、油タンクに戻る潤滑
油の落下を大きくとれるとともに潤滑油が前記油タンク
内に噴出するさいに油ミストの飛散を防止することがで
き、これによって前記油タンク内のガス中の油分が増加
するのを防止することができ、かつ前記油タンク内の潤
滑油の温度が均一になりやすく、油面付近の油温を高く
することがなく油蒸気の分圧を低くすることができる。In addition, since the end of the lubricating oil return flow path on the oil tank side is located lower than the lubricating oil level, the lubricating oil returning to the oil tank can be largely prevented from falling, and when the lubricating oil is spouted into the oil tank. The oil mist can be prevented from scattering, thereby preventing the oil content in the gas in the oil tank from increasing, and the temperature of the lubricating oil in the oil tank can be easily made uniform. The partial pressure of oil vapor can be lowered without increasing the oil temperature near the oil surface.
以下、本発明の一実施例である無給油スクリュ−圧縮機
を示す第１図および第２図について説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 and FIG. 2, which show an oil-free screw compressor according to an embodiment of the present invention, will be explained below.
第１図および第２図に示すように、ケーシング２内の圧
縮室２ａ内には、互いに噛合って回転する１組の雄ロー
タ、雌ロータから愈るスクリューロータ１が設置されて
いる。上記雄ロータはモータ９の駆動により増速ギヤ８
を介して回転する。As shown in FIGS. 1 and 2, a screw rotor 1 is installed in a compression chamber 2a in a casing 2, which is comprised of a pair of male and female rotors that rotate in mesh with each other. The above male rotor is driven by the motor 9 and is driven by the speed increasing gear 8.
Rotate through.
上記雄ロータは、タイミングギヤ４を介して上記雄ロー
タと同期回転し、これにより吸入口６から吸入して空気
を圧縮して吐出ロアより吐出する。The male rotor rotates in synchronization with the male rotor via a timing gear 4, thereby sucking in air from the suction port 6, compressing the air, and discharging it from the discharge lower.
上記雄ロータおよび雌ロータと上記ケーシング２の上記
圧縮室２ａの両側との間には、上記圧縮室２ａ内の圧縮
空気が漏洩するのを防止するための軸封装［５ａ、５ｂ
と上記雌ロータおよび雄ロータを回転自在に支持するた
めの吐出側軸受３ａ、吸入側軸受３ｂを設置している。Between the male rotor and female rotor and both sides of the compression chamber 2a of the casing 2, shaft seals [5a, 5b] are provided to prevent compressed air in the compression chamber 2a from leaking.
A discharge side bearing 3a and a suction side bearing 3b are installed to rotatably support the female rotor and male rotor.
また上記ケーシング２の吸入側端面には、上方部に上記
ギヤ８を内蔵するとともに上記モータ９を支持し、底部
に油タンク１０ａを構成するギヤケース１０を支持して
いる６また上記ケーシング２の吐出側端面には、上記吐
出側軸受３ａおよび上記同期歯車４を内蔵する軸受室１
１を支持している。つぎに潤滑油の経路は第１図に１点
鎖線で示すように上記油タンク１０ａより油ポンプ１８
で圧送された潤滑油は油主冷却器１９で冷却され、油フ
ィルタ２０でろ過されたのち。Further, the suction side end face of the casing 2 has the gear 8 built-in in the upper part and supports the motor 9, and the bottom part supports the gear case 10 constituting the oil tank 10a. A bearing chamber 1 containing the discharge side bearing 3a and the synchronous gear 4 is provided on the side end surface.
1 is supported. Next, the lubricating oil route is from the oil tank 10a to the oil pump 18 as shown by the dashed line in FIG.
The lubricating oil pressure-fed is cooled by an oil main cooler 19 and filtered by an oil filter 20.
上記吐出側軸受３ａ、上記吸入側軸受３ｂ、上記ギヤケ
ース１０内の上記増速ギヤ８および上記軸受室１１内の
上記タイミングギヤ４に供給される。ついで、上記吸入
側軸受３ｂおよび上記増速ギヤ８を潤滑した潤滑油はそ
のまま下方の油タンク１０ａに自然落下して戻る。この
場合、吸入側軸受３ｂの近傍は吸入空気によって冷却さ
れ低温で上記雄ロータおよび雌ロータとの摩擦熱のみで
あるから、該吸入側軸受３ｂを潤滑した潤滑油は低温に
なっている。そのため潤滑油を上記油タンク１０ａに戻
しても油タンク１０ａ内の潤滑油の温度上昇は少ない。It is supplied to the discharge side bearing 3a, the suction side bearing 3b, the speed increasing gear 8 in the gear case 10, and the timing gear 4 in the bearing chamber 11. Then, the lubricating oil that has lubricated the suction side bearing 3b and the speed increasing gear 8 naturally falls back into the lower oil tank 10a. In this case, the vicinity of the suction side bearing 3b is cooled by the suction air and is at a low temperature due to only the frictional heat between the male and female rotors, so the lubricating oil that lubricates the suction side bearing 3b is at a low temperature. Therefore, even if the lubricating oil is returned to the oil tank 10a, the temperature of the lubricating oil in the oil tank 10a does not rise much.
また上記吸入口６からの吸入空気は低圧、低温であるか
ら、上記吸入側軸封装置５６から上記吸入側軸受３ｂを
通って上記油タンク１０ａ内に漏れる空気量は少量であ
る。また増速ギヤ８の回転による潤滑油の温度上昇も極
めて少ない。したがって上記吸入側軸受３ｂおよび上記
増速ギヤ８を潤滑した潤滑油を直接上記油タンクＩＯａ
に戻しても潤滑油の温度上昇は少く、実用上問題になら
ない。Furthermore, since the intake air from the suction port 6 is at low pressure and low temperature, the amount of air leaking from the suction side shaft sealing device 56 through the suction side bearing 3b into the oil tank 10a is small. Furthermore, the temperature rise of the lubricating oil due to the rotation of the speed increasing gear 8 is extremely small. Therefore, the lubricating oil that lubricates the suction side bearing 3b and the speed increasing gear 8 is directly supplied to the oil tank IOa.
Even if the temperature is returned to 1, the temperature rise of the lubricating oil is small and does not pose a practical problem.
一方上記吐出側軸受３ａの近傍は上記雄ロータおよび雌
ロータによって圧縮された高温の空気により熱せられて
高温となっており、さらに高温の潤滑油はケーシング１
から熱を奪って高温となる。On the other hand, the area near the discharge side bearing 3a is heated to a high temperature by the high temperature air compressed by the male rotor and female rotor, and the high temperature lubricating oil is in the casing 1.
It takes heat from the body and becomes high temperature.
これに加えて圧縮室ｌａ内の圧縮された高温の空気が上
記吐出側軸封装＠ ５ ａから上記吐出側軸受３ａを通
って上記軸受室１１内に漏れるので上記軸受室１１内は
油蒸気を含んだ高温空気で充満する。In addition, the compressed high-temperature air in the compression chamber la leaks from the discharge side shaft seal @5a into the bearing chamber 11 through the discharge side bearing 3a, so that the inside of the bearing chamber 11 is filled with oil vapor. Filled with high temperature air.
高温の潤滑油は上記軸受室１１の底部に形成された排出
口１３より排出され油冷却器１４ａで冷却されて油戻り
口１５より上記油タンク１０ａに戻る。また軸受室１１
内の油蒸気を含む高温空気は、該軸受室１１の上方部に
形成された排気口１２より排出され、油煙冷却器１４ｂ
で冷却さ°れてその体積流量が減少するとともに油蒸気
の１部が凝縮されて上記ギヤケース１０の上記油タンク
１０ａ内の潤滑油油面より上方位置に形成された通気口
１６より上記ギヤケース１０内に流入する。The high temperature lubricating oil is discharged from a discharge port 13 formed at the bottom of the bearing chamber 11, cooled by an oil cooler 14a, and returned to the oil tank 10a from an oil return port 15. In addition, the bearing chamber 11
The high temperature air containing oil vapor in the bearing chamber 11 is discharged from the exhaust port 12 formed in the upper part of the bearing chamber 11, and is discharged from the oil smoke cooler 14b.
The oil vapor is cooled by water, its volumetric flow rate decreases, and a portion of the oil vapor is condensed, and the oil vapor is transferred to the gear case 10 through a vent hole 16 formed above the level of the lubricating oil in the oil tank 10a of the gear case 10. flow inside.
そのため、上記ギヤケース１０および上記油タンク１０
ａ内は低温に保持され、かつ圧力上昇も少いので、上記
ギヤケース１０の上方部に形成された排気口１７より排
出される排煙量は少量となり、かつ油含有量も減少する
、したがって上記排気口１７より排出される排煙に対す
る処理も簡単な装置によって行なうことができる。また
本実施例においては、油冷却器１４ａと油煙冷却器１４
ｂを一体に構成されているので、安価で製作することが
できる。また上記油戻り口１５を上記油タンク１０内の
潤滑油油面よりも下方位置に設置しているので、潤滑油
の落下を大きくとれるとともに上記油戻り口１５から上
記油タンク１０内に潤滑油が噴出するさいに油ミストの
飛散を防止し、これによって上記ギヤケース１０内の空
気中に潤滑油が混入するのを低下することができる。さ
らに上記油タンク１０ａ内の潤滑油の温度が均一化にな
りやすく、油面付近の温度を高くすることがないので、
油蒸気の分圧を低くすることができる、なお第２図に示
す２８は潤滑油をタイミングギヤ４に噴出するためのノ
ズルである。Therefore, the gear case 10 and the oil tank 10
Since the inside of a is kept at a low temperature and the pressure rise is small, the amount of exhaust gas discharged from the exhaust port 17 formed in the upper part of the gear case 10 is small, and the oil content is also reduced. The exhaust smoke discharged from the exhaust port 17 can also be treated with a simple device. Further, in this embodiment, the oil cooler 14a and the oil smoke cooler 14
Since b is integrally constructed, it can be manufactured at low cost. Furthermore, since the oil return port 15 is installed at a position below the level of the lubricating oil in the oil tank 10, a large amount of lubricating oil can be prevented from falling, and the lubricating oil can flow from the oil return port 15 into the oil tank 10. This prevents the oil mist from scattering when the lubricating oil is ejected, thereby reducing the amount of lubricating oil mixed into the air inside the gear case 10. Furthermore, the temperature of the lubricating oil in the oil tank 10a tends to become uniform, and the temperature near the oil surface does not become high.
Reference numeral 28 in FIG. 2 is a nozzle for spouting lubricating oil to the timing gear 4, which can lower the partial pressure of oil vapor.
つぎに本発明による軸受室付近の他の一実施例を示す第
３図について説明する。Next, FIG. 3 showing another embodiment near the bearing chamber according to the present invention will be described.
第３図に示す実施例においては、軸受室１１内底部に構
成された油溜め部１１ａに第２油冷却器２２を設置して
いる。上記第２油冷却器２２には冷却器２７で冷却され
た冷却水がポンプ２６で圧送供給され、油溜め部２２内
の高温の潤滑油を冷却し加熱されたのち、再び上記部器
２７で冷却され、以下上記作用を繰返すようにしている
。In the embodiment shown in FIG. 3, a second oil cooler 22 is installed in an oil reservoir 11a formed at the inner bottom of the bearing chamber 11. Cooling water cooled by the cooler 27 is pumped and supplied to the second oil cooler 22 by a pump 26, and after cooling and heating the high temperature lubricating oil in the oil reservoir 22, the cooling water is supplied to the second oil cooler 22 again by the oil cooler 27. After cooling, the above operation is repeated.
したがって本実施例では第１図に示す油冷却器１４ａの
構成を簡略化することができるとともに上記軸受室１１
内での油蒸気の発生量を低減することができる。Therefore, in this embodiment, it is possible to simplify the structure of the oil cooler 14a shown in FIG.
The amount of oil vapor generated inside the tank can be reduced.
つぎに本発明による軸受室付近の他の一実施例を示す第
４図について説明する。Next, FIG. 4 showing another embodiment near the bearing chamber according to the present invention will be described.
第４図に示す実施例においては、上記軸受室１１の周囲
を囲むように冷却水ジャケット２３を設け、かつ上記軸
受室１１内上方面と側面にそれぞれフィン２４を設けて
いる。上記冷却水ジャケット２３内には冷却器２７にて
冷却された水がポンプ２６で圧送供給され、上記軸受室
１１内の高温の潤滑油および高温の油煙を冷却し、加熱
されたのち、再び上記冷却器２７で冷却され、以下上記
作用を繰返すようにしている。In the embodiment shown in FIG. 4, a cooling water jacket 23 is provided to surround the bearing chamber 11, and fins 24 are provided on the upper and side surfaces of the bearing chamber 11, respectively. Water cooled by a cooler 27 is pumped into the cooling water jacket 23 by a pump 26, cools the high-temperature lubricating oil and high-temperature oil smoke in the bearing chamber 11, and is then heated again. It is cooled by a cooler 27, and the above-mentioned operation is repeated thereafter.
したがって本実施例においては第１図に示す油冷却器１
４ａおよび油煙冷却器１４ｂの構成を簡略化することが
できる。Therefore, in this embodiment, the oil cooler 1 shown in FIG.
4a and the structure of the oil smoke cooler 14b can be simplified.
つぎに本発明による軸受室付近のさらに他の一実施例を
示す第５図について説明する。Next, a description will be given of FIG. 5 showing still another embodiment near the bearing chamber according to the present invention.
第５図に示す実施例においては、蒸気軸受室１１内に発
生した高温の油煙を排気口１２より排出して油煙冷却器
１４ｂで冷却したのち、油分離器２５で潤滑油分を除去
して大気に放出するようにしている。In the embodiment shown in FIG. 5, the high temperature oil smoke generated in the steam bearing chamber 11 is discharged from the exhaust port 12 and cooled by the oil smoke cooler 14b, and then the lubricating oil is removed by the oil separator 25. It is released into the atmosphere.
したがって本実施例においては、上記ギヤケースｌＯの
上方部の排気口１７から大気に放出される油煙量をさら
に低減することができる。Therefore, in this embodiment, the amount of oil smoke released into the atmosphere from the exhaust port 17 in the upper part of the gear case IO can be further reduced.
なお上記各実施例においては単段のスクリュー圧縮機に
ついて説明したが、これにＰＲｆｆｉピｎるものでなく
多段スクリュー圧縮機の各段に使用することも可能であ
る。この場合、各段の油冷却器および油煙冷却器を一体
に構成することが考えられ、これによって省スペース化
をはかることができる。In each of the above embodiments, a single-stage screw compressor has been described, but the PRffi pin is not limited to this and can also be used in each stage of a multi-stage screw compressor. In this case, it is conceivable to configure the oil cooler and the oil smoke cooler at each stage in one piece, thereby saving space.
本発明は以上述べたように構成されているので、以下に
記載されるような効果を奏する。Since the present invention is configured as described above, it produces the effects described below.
（１）軸受室と油タンクの間を接続する潤滑油戻り流路
に潤滑油冷却手段を設けたので、油タンク内の潤滑油の
温度を低下することができ、これによって油蒸気の発生
を低減することができる。(1) Since a lubricating oil cooling means is provided in the lubricating oil return passage connecting between the bearing chamber and the oil tank, the temperature of the lubricating oil in the oil tank can be lowered, thereby reducing the generation of oil vapor. can be reduced.
（２）前記軸受室からのガスを油タンクあるいは油分離
器のいずれか一方を介して大気中に放出するガス放出流
路を前記潤滑油戻り流路とは別に設け、該ガス放出流路
に放出ガス冷却手段を設けたので、ガスの体積流量を減
少し、これによって大気中に放出するガスの流量を減少
することができ、かつガス放出流路の途中に油タンクが
設置されている場合には油タンク内の雰囲気温度を低下
し、大気中に放出するガスの流量を減少することができ
る。(2) A gas discharge channel for discharging gas from the bearing chamber into the atmosphere via either an oil tank or an oil separator is provided separately from the lubricating oil return channel; Since a discharge gas cooling means is provided, the volumetric flow rate of gas can be reduced, thereby reducing the flow rate of gas released into the atmosphere, and if an oil tank is installed in the middle of the gas discharge channel. It is possible to lower the atmospheric temperature inside the oil tank and reduce the flow rate of gas released into the atmosphere.
（３）前記潤滑油冷却手段と放出ガス冷却手段とを一体
に構成したので、冷却手段の製作費を安価することがで
きる。(3) Since the lubricating oil cooling means and the discharged gas cooling means are integrally constructed, the manufacturing cost of the cooling means can be reduced.
（４）前記潤滑油戻り流路の油タンク側端部を潤滑油油
面より下方に位置させたので、油タンクに戻る潤滑油の
落下を大きくとれるとともに潤滑油戻り流路から油タン
ク内に噴出するさいに油ミストの飛散を防止することが
でき、かつ油タンク内のガス中に含まれる潤滑油の量を
減少することができ、かつ油タンク内の潤滑油の温度が
均一化になりやすくするとともに油面付近の油温が高く
釘ることがなく油蒸気の分圧を低くすることができかる
。(4) Since the end of the lubricating oil return flow path on the oil tank side is located below the lubricant oil surface, the lubricant returning to the oil tank can be largely prevented from falling, and the lubricant can also flow from the lubricant return flow path into the oil tank. It can prevent oil mist from scattering when it is ejected, reduce the amount of lubricating oil contained in the gas in the oil tank, and even out the temperature of the lubricating oil in the oil tank. In addition, the oil temperature near the oil surface is high and the partial pressure of oil vapor can be lowered.
（５）前記ガス放出流路の油タンク側端部を油タンク内
潤滑油油量より上方に位置させたので、放出ガスが油タ
ンク内の潤滑油中に浸入するのを防止することができる
。(5) Since the end of the gas release channel on the oil tank side is located above the amount of lubricating oil in the oil tank, it is possible to prevent the released gas from penetrating into the lubricating oil in the oil tank. .
（６）前記軸受室の底部に油溜め部を形成し該油溜め部
に第２潤滑油冷却手段を設けたので、軸受室と油タンク
とを接続する潤滑油戻り流路に設けた潤滑油冷却手段の
構成を簡略化するとともに軸受室内の油蒸気の発生を低
減することができる。(6) Since an oil reservoir is formed at the bottom of the bearing chamber and a second lubricant cooling means is provided in the oil reservoir, the lubricant is provided in the lubricant return passage connecting the bearing chamber and the oil tank. The configuration of the cooling means can be simplified and the generation of oil vapor within the bearing chamber can be reduced.
（７）多段スクリュー流体機械において、各段の潤滑油
冷却手段と放出ガス冷却手段を一体に構成したので、省
スペース化および価格低減化をはかることができる。(7) In the multi-stage screw fluid machine, since the lubricating oil cooling means and the discharged gas cooling means of each stage are integrated, it is possible to save space and reduce the cost.
第１図は本発明の一実施例である無給油スクリュー圧縮
機を示す断面図、第２図は第１図に示す軸受室の拡大断
面図、第３図乃至第５図はそれぞれ本発明による軸受室
の他の一実施例を示す断面図である。
１・・・スクリューロータ、２・・・ケーシング、３・
・・軸受、４・・・タイミングギヤ、１０・・・ギヤケ
ーシング、１１・・・軸受室、１４ａ・・・潤滑油冷却
器、１４ｂ・・・油煙冷却器、１８・・・油ポンプ、１
９・・・油冷却器、２０・・・油フィル先
スクリュ−ロータ
２ザーンンク
３ｆｉ由焚
４タイミ／ダ〜ぺ
５Ｉ由封袋工
第１図
１０と“僕甲−し／７゛
１０ａ ン白 ５７／フ
１１ 軸檗Ｖ
４ａ７５滑泊射Ｐ器
１４ｂ泊違々痔器
８泊ｘ、゛ンフ′
１９シｄコ冷弧゛Ｐ炙
２０浦フ１ルタ
代理人弁理士 秋 本 正 実
第２
図
第
図
１又クリニーロータ
３０吐出側１更
４ グイミング次パべ
５ａ’仁を二８ゴｉイ？゛」 軸（ヒＳ＠針！１１軸９
虻
１２ｊ４ト気口
１３２ト蝕口
２８潤殴シφコ積 弘 ２ ヌご）Ｖ
３０吐払４１１’Ｊ軸ン
４ タイミ／グぞイ
５ａ ｐｉ！ｔ４ｆ’ＪｂＵｉｉ
１３セ一戯口
２３ン−１２゛ノ：）コ５→して：ン・（グーノ）−２
４フイ し／Fig. 1 is a sectional view showing an oil-free screw compressor according to an embodiment of the present invention, Fig. 2 is an enlarged sectional view of the bearing chamber shown in Fig. 1, and Figs. 3 to 5 are each according to the present invention. FIG. 7 is a sectional view showing another embodiment of the bearing chamber. 1... Screw rotor, 2... Casing, 3...
...Bearing, 4...Timing gear, 10...Gear casing, 11...Bearing chamber, 14a...Lubricating oil cooler, 14b...Oil smoke cooler, 18...Oil pump, 1
9...Oil cooler, 20...Oil fill tip screw rotor 2 Zank 3fi Yuki 4 Taimi/Da~pe 5I Yufu bag factory Figure 1 10 and "Boku-shi/7゛10a" 57/F11 Axial box V 4a75 Sliding radiation P device 14b nights Different hemorrhoid device 8 nights Fig. 1 Also, Cliny rotor 30 discharge side 1 change 4 Guiming next page 5a' needle 28 goi?'' Axis (HiS @ needle! 11 axis 9
12j4 To air opening 132 To Eclipse opening 28 Jun punch shiφ Kosumi Hiroshi 2 Nugo) V 30 Discharge 411'J axis 4 Taimi/Guzoi 5a pi! t4f'JbUii 13th seichigoguchi 23n-12゛ノ:)ko5→shita:n・(guno)-2
4Fish/
Claims (1)
する軸受部からの高温の潤滑油を油タンクに戻す潤滑油
戻り流路に潤滑油を冷却する潤滑油冷却手段を備えたこ
とを特徴とするスクリュー流体機械。 ２、スクリュー流体機械において、一対のロータを支持
する軸受部内に発生したガスを大気中に放出するガス放
出流路にガスを冷却するガス冷却手段を備えたことを特
徴とするスクリュー流体機械。 ３、スクリュー流体機械において、一対のロータを支持
する軸受内に発生したガスを油タンクもしくは油分離器
のいずれか一方を介して大気中に放出するガス放出経路
を前記軸受部内に接続し、ガスを冷却するガス冷却手段
を備えたことを特徴とするスクリュー流体機械。 ４、前記潤滑油冷却手段は、前記放出ガス冷却手段と一
体に構成されたことを特徴とする請求項２もしくは３記
載のスクリュー流体機械。 ５、前記潤滑油戻り流路は、油タンク側端部が油タンク
内の潤滑油油面より下方に位置されていることを特徴と
する請求項１もしくは４記載のスクリュー流体機械。 ６、前記ガス放出流路は、ガスを油タンク内を介して大
気に放出するとき、その油タンク側端部が油タンク内の
潤滑油油面より上方に位置されていることを特徴とする
請求項２記載のスクリュー流体機械。 ７、前記軸受部のうち、吐出側軸受部は軸受室に内蔵さ
れ該軸受室は前記潤滑油戻り流路およびガス放出流路の
端部に接続されていることを特徴とする請求項２、３、
４、５、６のいずれかに記載されたスクリュー流体機械
。 ８、前記軸受室はその底部に油溜め部を備え、該油溜め
部に前記潤滑油冷却手段とは別の潤滑油冷却手段を備え
ていることを特徴とする請求項７記載のスクリュー流体
機械。 ９、多段スクリュー流体機械において、各段にそれぞれ
一対のロータを支持する軸受部からの高温の潤滑油を油
タンクに戻す潤油戻り流路に潤滑油を冷却する潤滑油冷
却手段と、前記軸受部内で発生するガスを油タンクある
いは油分離器のいずれかが一方を介して大気に放出する
ガス放出流路にガスを冷却するガス冷却手段とを備え、
かつ前記各段の潤滑油冷却手段および前記各段のガス冷
却手段を一体に構成したことを特徴とする多段スクリュ
ー流体機械。 １０、螺旋状の陸部と溝部をそれぞれ有する一対の雄ロ
ータおよび雌ロータが互いにケーシング内を噛み合いな
がら回転し、吸入口から吸入された流体を圧縮あるいは
膨張させて吐出口より吐出するスクリュー流体機械にお
いて、前記雄ロータおよび雌ロータの吐出側に設けられ
た吐出側軸受を内蔵し、油タンクからの潤滑油にて前記
吐出側軸受を冷却する軸受室と、該軸受室からの潤滑油
を上記油タンクに戻す潤滑油戻り流路と該潤滑油戻り流
路に設けられ、潤滑油を冷却する潤滑油冷却手段とを設
けたことを特徴とするスクリュー流体機械。 １１、前記軸受室からのガスを油タンクあるいは油分離
器のいずれか一方を介して大気中に放出するガス放出流
路を前記軸受室に接続し、該ガス放出流路に放出ガス冷
却手段を設けたことを特徴とする請求項１記載のスクリ
ュー流体機械。 １２、前記潤滑油冷却手段は前記放出ガス冷却手段と一
体に構成されたことを特徴とする請求項１０記載のスク
リュー流体機械。 １３、前記潤滑油戻り流路は油タンク側端部を油タンク
内の潤滑油油面より下方に位置されていることを特徴と
する請求項１０記載のスクリュー流体機械。 １４、前記ガス放出流路はガスを油タンク内を通して大
気に放出するように構成したとき、その油タンク側端部
が油タンク内の潤滑油油面より上方に位置されているこ
とを特徴とする請求項１１記載のスクリュー流体機械。 １５、前記軸受室はその底部に油溜め部を形成し、該油
溜め部に前記潤滑油冷却手段とは別の潤滑油冷却手段を
設けたことを特徴とする請求項１１記載のスクリュー流
体機械。 １６、各段毎に螺旋状の陸路と溝部をそれぞれ有する一
対の雄ロータおよび雌ロータが互いにケーシング内に噛
み合いながら回転し、吸入口から吸入された流体を圧縮
あるいは膨張させて吐出口より吐出する多段スクリュー
流体機械において、前記雄ロータおよび雌ロータの吐出
側端部に有する吐出側軸受を内蔵し、油タンクからの潤
滑油にて上記吐出側軸受を冷却する軸受室と、該軸受室
からの潤滑油を上記タンクに戻すための潤滑油戻り流路
、および該軸受室からのガスを油タンクあるいは油分離
器のうち少なくとも一方を通して大気に放出するガス放
出流路を設け、前記潤滑油戻り流路に潤滑油冷却手段を
、ガス放出流路に放出ガス冷却手段を設け、かつ前記各
段の潤滑油冷却手段および放出ガス冷却手段とを一体に
構成したことを特徴とする多段スクリュー流体機械。[Scope of Claims] 1. In a screw fluid machine, a lubricating oil return flow path that returns high-temperature lubricating oil from a bearing that supports a pair of rotors to an oil tank is provided with a lubricating oil cooling means for cooling the lubricating oil. A screw fluid machine characterized by: 2. A screw fluid machine, characterized in that a gas cooling means for cooling the gas is provided in a gas discharge channel for discharging the gas generated in the bearing portion supporting the pair of rotors into the atmosphere. 3. In a screw fluid machine, a gas release path for releasing gas generated in the bearings that support a pair of rotors into the atmosphere via either an oil tank or an oil separator is connected inside the bearing part, and the gas A screw fluid machine characterized by being equipped with a gas cooling means for cooling. 4. The screw fluid machine according to claim 2 or 3, wherein the lubricating oil cooling means is constructed integrally with the discharged gas cooling means. 5. The screw fluid machine according to claim 1 or 4, wherein the lubricating oil return passage has an end on the oil tank side located below the lubricating oil level in the oil tank. 6. The gas release flow path is characterized in that when gas is released into the atmosphere through the oil tank, the oil tank side end thereof is located above the lubricating oil level in the oil tank. The screw fluid machine according to claim 2. 7. Among the bearing sections, the discharge side bearing section is built into a bearing chamber, and the bearing chamber is connected to the ends of the lubricating oil return channel and the gas discharge channel. 3,
4. The screw fluid machine according to any one of 4, 5 and 6. 8. The screw fluid machine according to claim 7, wherein the bearing chamber is provided with an oil reservoir at its bottom, and the oil reservoir is provided with a lubricating oil cooling means different from the lubricating oil cooling means. . 9. In a multi-stage screw fluid machine, a lubricating oil cooling means for cooling the lubricating oil from a bearing section supporting a pair of rotors in each stage to a lubricating oil return flow path that returns high-temperature lubricating oil to an oil tank, and the bearings. A gas cooling means for cooling the gas is provided in a gas discharge channel through which either the oil tank or the oil separator releases the gas generated within the unit to the atmosphere,
A multi-stage screw fluid machine characterized in that the lubricating oil cooling means at each stage and the gas cooling means at each stage are integrally constructed. 10. A screw fluid machine in which a pair of male and female rotors, each having a spiral land portion and a groove portion, rotate while meshing with each other inside a casing, compressing or expanding the fluid sucked in from the suction port, and discharging the fluid from the discharge port. , a bearing chamber that includes a built-in discharge side bearing provided on the discharge side of the male rotor and the female rotor, and that cools the discharge side bearing with lubricating oil from an oil tank; A screw fluid machine comprising: a lubricating oil return flow path for returning the lubricating oil to an oil tank; and a lubricating oil cooling means provided in the lubricating oil return flow path for cooling the lubricating oil. 11. A gas discharge channel for discharging gas from the bearing chamber into the atmosphere via either an oil tank or an oil separator is connected to the bearing chamber, and a discharged gas cooling means is provided in the gas discharge channel. 2. A screw fluid machine according to claim 1, further comprising: a screw fluid machine. 12. The screw fluid machine according to claim 10, wherein the lubricating oil cooling means is constructed integrally with the discharged gas cooling means. 13. The screw fluid machine according to claim 10, wherein the lubricating oil return passage has an end on the oil tank side located below the lubricating oil level in the oil tank. 14. When the gas discharge channel is configured to discharge gas into the atmosphere through the oil tank, the end thereof on the oil tank side is located above the level of the lubricating oil in the oil tank. The screw fluid machine according to claim 11. 15. The screw fluid machine according to claim 11, wherein the bearing chamber has an oil reservoir formed at its bottom, and the oil reservoir is provided with a lubricating oil cooling means different from the lubricating oil cooling means. . 16. A pair of male and female rotors, each having a spiral land path and groove at each stage, rotate while meshing with each other in the casing, compressing or expanding the fluid sucked in from the suction port, and then discharging it from the discharge port. A multi-stage screw fluid machine includes a bearing chamber in which discharge-side bearings are built in at the discharge-side ends of the male rotor and the female rotor, and in which the discharge-side bearings are cooled with lubricating oil from an oil tank; A lubricating oil return flow path for returning the lubricating oil to the tank, and a gas discharge flow path for releasing gas from the bearing chamber to the atmosphere through at least one of the oil tank and the oil separator, and the lubricating oil return flow path A multi-stage screw fluid machine characterized in that a lubricating oil cooling means is provided in the passage, a discharged gas cooling means is provided in the gas discharge passage, and the lubricating oil cooling means and discharged gas cooling means of each stage are integrally constructed.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2148703A JPH0443891A (en) | 1990-06-08 | 1990-06-08 | Screw fluid machines and multi-stage screw fluid machines |
| EP91109051A EP0460578A1 (en) | 1990-06-08 | 1991-06-03 | Screw fluid machine |
| KR1019910009208A KR920001120A (en) | 1990-06-08 | 1991-06-04 | Screw Fluid Machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2148703A JPH0443891A (en) | 1990-06-08 | 1990-06-08 | Screw fluid machines and multi-stage screw fluid machines |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0443891A true JPH0443891A (en) | 1992-02-13 |
Family
ID=15458710
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2148703A Pending JPH0443891A (en) | 1990-06-08 | 1990-06-08 | Screw fluid machines and multi-stage screw fluid machines |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0460578A1 (en) |
| JP (1) | JPH0443891A (en) |
| KR (1) | KR920001120A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002155879A (en) * | 2000-11-22 | 2002-05-31 | Hitachi Ltd | Oil-free screw compressor |
| JP2004346864A (en) * | 2003-05-23 | 2004-12-09 | Taiko Kikai Industries Co Ltd | Expansion engine for recovering waste heat |
| JP2007205358A (en) * | 2007-03-26 | 2007-08-16 | Hitachi Industrial Equipment Systems Co Ltd | Oil-free screw compressor and its operating method |
| JP2009108696A (en) * | 2007-10-26 | 2009-05-21 | Kobe Steel Ltd | Screw compressor |
| JP2011047327A (en) * | 2009-08-27 | 2011-03-10 | Hitachi Industrial Equipment Systems Co Ltd | Screw compressor |
| JP2011149439A (en) * | 2011-03-28 | 2011-08-04 | Kobe Steel Ltd | Screw compressor |
| JP2012163068A (en) * | 2011-02-08 | 2012-08-30 | Kobe Steel Ltd | Water injection type screw compressor |
| JP2014046897A (en) * | 2012-09-04 | 2014-03-17 | Panasonic Corp | Vehicular heat pump device |
| WO2018079196A1 (en) * | 2016-10-25 | 2018-05-03 | 株式会社神戸製鋼所 | Oil-free screw compressor |
| JP2023541126A (en) * | 2020-09-02 | 2023-09-28 | イートン インテリジェント パワー リミテッド | Rear wheel drive EGR pump |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5401149A (en) * | 1992-09-11 | 1995-03-28 | Hitachi, Ltd. | Package-type screw compressor having coated rotors |
| CN1062056C (en) * | 1994-02-19 | 2001-02-14 | 株式会社日立制作所 | Box type screw compressor |
| BE1014461A3 (en) * | 2001-11-08 | 2003-10-07 | Atlas Copco Airpower Nv | Oil injected screw compressor, has separate oil supply system with cooler for lubricating rotor bearings |
| JP2012127253A (en) * | 2010-12-15 | 2012-07-05 | Kobe Steel Ltd | Screw compressor |
| WO2018193325A1 (en) * | 2017-04-21 | 2018-10-25 | Atlas Copco Airpower, Naamloze Vennootschap | Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB393977A (en) * | 1931-12-16 | 1933-06-16 | Thomas Winter Nichols | Improvements in rotary air pumps or compressors |
| GB785860A (en) * | 1955-01-17 | 1957-11-06 | Manfred Dunkel | Improvements in or relating to rotary piston blowers |
| DE3344953A1 (en) * | 1983-12-13 | 1985-06-20 | Leybold-Heraeus GmbH, 5000 Köln | TWO-SHAFT VACUUM PUMP WITH GEARBOX EVACUATION |
-
1990
- 1990-06-08 JP JP2148703A patent/JPH0443891A/en active Pending
-
1991
- 1991-06-03 EP EP91109051A patent/EP0460578A1/en not_active Withdrawn
- 1991-06-04 KR KR1019910009208A patent/KR920001120A/en not_active Ceased
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002155879A (en) * | 2000-11-22 | 2002-05-31 | Hitachi Ltd | Oil-free screw compressor |
| JP2004346864A (en) * | 2003-05-23 | 2004-12-09 | Taiko Kikai Industries Co Ltd | Expansion engine for recovering waste heat |
| JP2007205358A (en) * | 2007-03-26 | 2007-08-16 | Hitachi Industrial Equipment Systems Co Ltd | Oil-free screw compressor and its operating method |
| JP2009108696A (en) * | 2007-10-26 | 2009-05-21 | Kobe Steel Ltd | Screw compressor |
| JP2011047327A (en) * | 2009-08-27 | 2011-03-10 | Hitachi Industrial Equipment Systems Co Ltd | Screw compressor |
| JP2012163068A (en) * | 2011-02-08 | 2012-08-30 | Kobe Steel Ltd | Water injection type screw compressor |
| JP2011149439A (en) * | 2011-03-28 | 2011-08-04 | Kobe Steel Ltd | Screw compressor |
| JP2014046897A (en) * | 2012-09-04 | 2014-03-17 | Panasonic Corp | Vehicular heat pump device |
| WO2018079196A1 (en) * | 2016-10-25 | 2018-05-03 | 株式会社神戸製鋼所 | Oil-free screw compressor |
| JP2018071373A (en) * | 2016-10-25 | 2018-05-10 | 株式会社神戸製鋼所 | Oil free screw compressor |
| TWI649499B (en) * | 2016-10-25 | 2019-02-01 | 日商神戶製鋼所股份有限公司 | Oil-free screw compressor |
| CN109844320A (en) * | 2016-10-25 | 2019-06-04 | 株式会社神户制钢所 | Oil free screw compressor |
| CN109844320B (en) * | 2016-10-25 | 2020-07-14 | 株式会社神户制钢所 | Oil-free screw compressor |
| JP2023541126A (en) * | 2020-09-02 | 2023-09-28 | イートン インテリジェント パワー リミテッド | Rear wheel drive EGR pump |
| US12338817B2 (en) | 2020-09-02 | 2025-06-24 | Eaton Intelligent Power Limited | Rear drive EGR pump |
| US20250297609A1 (en) * | 2020-09-02 | 2025-09-25 | Eaton Intelligent Power Limited | Rear drive egr pump |
Also Published As
| Publication number | Publication date |
|---|---|
| KR920001120A (en) | 1992-01-30 |
| EP0460578A1 (en) | 1991-12-11 |
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