JPH0436091A - Oil-sealed rotary vacuum pump - Google Patents

Oil-sealed rotary vacuum pump

Info

Publication number
JPH0436091A
JPH0436091A JP14050690A JP14050690A JPH0436091A JP H0436091 A JPH0436091 A JP H0436091A JP 14050690 A JP14050690 A JP 14050690A JP 14050690 A JP14050690 A JP 14050690A JP H0436091 A JPH0436091 A JP H0436091A
Authority
JP
Japan
Prior art keywords
pump chamber
oil
stage
stage pump
forced
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
Application number
JP14050690A
Other languages
Japanese (ja)
Inventor
Teru Sakazaki
坂崎 輝
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shimadzu Corp
Original Assignee
Shimadzu Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Shimadzu Corp filed Critical Shimadzu Corp
Priority to JP14050690A priority Critical patent/JPH0436091A/en
Publication of JPH0436091A publication Critical patent/JPH0436091A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/021Control systems for the circulation of the lubricant
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/025Lubrication; Lubricant separation using a lubricant pump

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PURPOSE:To prevent an oil-sealed rotary vacuum pump from seizure and so forth during operation under load and from lowering its performance during operation under no load, by connecting a forced oil supply means to a first stage pump chamber by way of a valve adapted to be opened and closed in accordance with a pressure at the suction port the first stage pump chamber. CONSTITUTION:A second stage pump chamber P2 connected thereto with a forced oil feed means 7 is connected to a first pump chamber P1 through a differential pressure oil feed passage 8. The forced oil feed means 7 is connected to the first pump chamber P1 by way of a valve 11 which is adapted to be opened and closed in accordance with a pressure at the suction port 41 of the first pump chamber P1. With this arrangement in which a large volume of oil can be introduced into the first pump chamber 1 from the forced oil feed means 7 during operation under load, the lubrication for the first pump chamber P1 is sufficiently made so as to prevent seizure or the like. Further, since the forced oil feed means 7 is shut off so that the operating mode is shifted into a differential pressure oil feed mode during operation under no load, i is possible of prevent the performance from lowering in a case such as oil being fed after deaeration in order to carry out high vacuum discharge.

Description

【発明の詳細な説明】 [産業上の利用分野コ 本発明は、種々の真空応用分野において利用可能な2段
形の油回転真空ポンプに関するものである。
DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a two-stage oil rotary vacuum pump that can be used in various vacuum application fields.

[従来の技術] 油回転真空ポンプは、排気能力を高めるために第2図に
示すようにポンプ室を2段構成にしていることが多い。
[Prior Art] Oil rotary vacuum pumps often have a pump chamber configured in two stages, as shown in FIG. 2, in order to increase exhaust capacity.

各ポンプ室Pエ (P2)は、シリンダ1□ (1□)
と、このシリンダz  (12)の偏心位置に内接配置
されたロータ2□ (22)と、このロータ21  (
22)に半径方向に突没可能に収容され先端を前記シリ
ンダ11  (12)の内周に摺接させてなるベーン3
□ (32)とによって仕切られている。そして、両ポ
ンプ室P1、P2にポンプ油を充填してロータ21.2
2を回転駆動することにより、吸気口41から吸入した
ガスを先ず第1段ポンプ室P1で圧縮排気し、その後、
第1段ポンプ家出口51から中間連通路6を介して第2
段ポンプ室人口4□にそのガスを移送して、この第2段
ポンプ室P2において引き続き圧縮排気することにより
、排気口52を通じてそのガスを外部に排出するという
周知のポンプ作用を営むことができるようになっている
Each pump chamber Pe (P2) is cylinder 1□ (1□)
, rotor 2□ (22) inscribed in the eccentric position of this cylinder z (12), and this rotor 21 (
22), the vane 3 is accommodated in a radially projectable and retractable manner and has its tip slidingly contacted with the inner periphery of the cylinder 11 (12).
□ It is separated by (32). Then, both pump chambers P1 and P2 are filled with pump oil, and the rotor 21.2 is filled with pump oil.
2, the gas taken in from the intake port 41 is first compressed and exhausted in the first stage pump chamber P1, and then,
From the first stage pump house outlet 51 to the second stage via the intermediate communication path 6.
By transferring the gas to the stage pump chamber 4□ and continuing to compress and exhaust it in the second stage pump chamber P2, the well-known pump action of exhausting the gas to the outside through the exhaust port 52 can be performed. It looks like this.

ところで、第1段ポンプ室P1の吸気口41はチャンバ
等の排気目的に接続されるため、空気を含んだ油を該第
1ポンプ室P1に供給すると油中の空気がポンプ到達圧
力に悪影響を及ぼす。このため、必要以上の油を供給し
てはならないという制約がある。また、このポンプ室P
1においては、第2段ポンプ室P2に十分なポンプ油が
充填されこれにバックアップされておれば、充填される
油が少量であってもポンプとしての作動上特に問題を生
じないという側面もある。このため、従来の給油形態は
、第2段ポンプ室P2に対しては油路7 a ”−油圧
ポンプ7b、フィルタ7 C%タンクT等から構成され
る強制給油手段7を接続して十分な油を供給できるよう
にするが、第1段ポンプ室P1に対しては、第2段ポン
プ室P2に導入されて脱気された後の油を差圧給油路8
を介して潤滑やシールに必要な油量だけ当該第1段ポン
プ室P1に送り込むことができるようにしている。
By the way, since the intake port 41 of the first stage pump chamber P1 is connected to the purpose of exhausting a chamber or the like, if oil containing air is supplied to the first pump chamber P1, the air in the oil will have a negative effect on the ultimate pressure of the pump. affect For this reason, there is a restriction that more oil than necessary must not be supplied. Also, this pump chamber P
1, there is also the aspect that if the second stage pump chamber P2 is filled with sufficient pump oil and backed up by this, even if the amount of oil filled is small, there will be no particular problem in the operation of the pump. . For this reason, in the conventional oil supply system, a forced oil supply means 7 consisting of an oil passage 7a''-hydraulic pump 7b, a filter 7C% tank T, etc. is connected to the second stage pump chamber P2 to ensure sufficient oil supply. However, for the first stage pump chamber P1, the oil that has been introduced into the second stage pump chamber P2 and degassed is sent to the differential pressure oil supply path 8.
Only the amount of oil required for lubrication and sealing can be sent into the first stage pump chamber P1 through the pump.

[発明が解決しようとする課題] ところが、このような構成では、ポンプに大きな負荷が
掛かり高い潤滑性を必要とする排気開始当初等に潤滑が
行われなくなる不具合を生じる。
[Problems to be Solved by the Invention] However, with such a configuration, a problem arises in that lubrication is not performed at the beginning of pumping, etc., when a large load is applied to the pump and high lubricity is required.

すなわち、従来の差圧給油は、排気がある程度進行した
時点に照準を合わせ、両ポンプ室P、、22間の差圧を
利用して第2段ポンプ室P2から第1段ポンプ室P1へ
適量の油が給油されるように設定しである。このため、
吸気口4、が大気圧乃至は大気圧に近い状態にある排気
開始当初は、両ポンプ室P1.22間の差圧が極めて小
さく、有効な差圧給油を行い得ない。この結果、潤滑不
良による焼き付きを起こし易く、ポンプが早期破損に至
る可能性が高いという問題がある。
In other words, conventional differential pressure oil supply aims at the point when exhaust has progressed to a certain extent, and uses the differential pressure between both pump chambers P, 22 to supply an appropriate amount from the second stage pump chamber P2 to the first stage pump chamber P1. It is set so that the oil is supplied. For this reason,
At the beginning of exhaustion when the intake port 4 is at atmospheric pressure or close to atmospheric pressure, the differential pressure between both pump chambers P1.22 is extremely small, and effective differential pressure oil supply cannot be performed. As a result, there is a problem that seizure is likely to occur due to poor lubrication, and there is a high possibility that the pump will be damaged at an early stage.

また、使用目的は高真空排気に限られず、例えば反応性
ガスをチャンバ内にフローさせなから一定圧の下に成膜
を行う半導体製造装置のように、常に一定の負荷を掛け
られた状態で排気を実行するようなものもあり、この場
合は潤滑が終始重要な要素となる。しかも、このような
装置から排気されるガスは凝縮性を有したもの(水蒸気
や反応性ガス)である場合が多(、潤滑性の低下を防ぐ
ためにより大量の給油を行わなければならない。
In addition, the purpose of use is not limited to high vacuum evacuation, but also in situations where a constant load is always applied, such as in semiconductor manufacturing equipment that deposits a film under a constant pressure without allowing reactive gas to flow into the chamber. There are also some that perform exhaust, in which case lubrication is an important factor throughout. Moreover, the gas exhausted from such devices is often condensable (water vapor or reactive gas), and a larger amount of oil must be supplied to prevent deterioration of lubricity.

しかるに、従来の差圧給油は、たとえそれが有効に機能
したとしてもそのような油量を到底賄いきれないし、万
−第2段ポンプ室P2以上の油量を第1段ポンプ室P工
に給油しなければならない事情が生じた場合にもそれを
実現することは不可能である。
However, even if the conventional differential pressure oil supply functioned effectively, it would be impossible to supply such an amount of oil; Even if a situation arises that requires refueling, it is impossible to accomplish this.

本発明は、これらの課題を有効に解決することを目的と
している。
The present invention aims to effectively solve these problems.

[課題を解決するための手段] 本発明は、かかる目的を達成するために、次のような手
段を講じたものである。
[Means for Solving the Problems] In order to achieve the above object, the present invention takes the following measures.

すなわち、本発明に係る油回転真空ポンプは、第2段ポ
ンプ室に強制給油手段を接続し、その第2段ポンプ室を
差圧給油路を介して第1段ポンプ室に連通させてなる2
段形の油回転真空ポンプにおいて、前記第1段ポンプ室
にバルブを介して前記強制給油手段を接続し、そのバル
ブを前記第1段ポンプ室の吸気口圧力の高低に応じて開
閉するようにしたことを特徴としている。
That is, in the oil rotary vacuum pump according to the present invention, a forced oil supply means is connected to a second stage pump chamber, and the second stage pump chamber is communicated with a first stage pump chamber via a differential pressure oil supply path.
In the step-type oil rotary vacuum pump, the forced oil supply means is connected to the first stage pump chamber via a valve, and the valve is opened and closed according to the level of the intake port pressure of the first stage pump chamber. It is characterized by what it did.

[作用] このような構成であれば、吸気口圧力が高い負荷運転時
にはバルブが開となって、第1段ポンプ室に強制給油手
段から直接給油が行われることになり、その油量も適宜
に設定が可能であるため、潤滑不足を有効に解消するこ
とができる(この時点では油中に空気が混入していても
その量は相対的に見れば微量に過ぎず、大勢に影響を及
ぼさない)。次に、吸気口の圧力が低くなり、油中の空
気が排気に影響を及ぼすような無負荷運転状態に近くな
った時には、バルブが閉となって、強制給油手段が遮断
されることになり、第1段ポンプ室には従来の差圧給油
路を介して脱気後の油のみが給油されることになる。こ
のため、給油を通じて導入される空気を必要最小限に抑
え、高真空排気を有効に行うことが可能になる。
[Function] With this configuration, the valve is opened during load operation with high intake port pressure, and the first stage pump chamber is directly supplied with oil from the forced oil supply means, and the amount of oil is adjusted accordingly. Because it can be set to do not have). Next, when the pressure at the intake port becomes low and the air in the oil approaches a no-load operating condition where it affects the exhaust, the valve closes and the forced lubrication means is cut off. Only the degassed oil is supplied to the first stage pump chamber through the conventional differential pressure oil supply path. For this reason, it becomes possible to suppress the air introduced through refueling to the necessary minimum, and to perform high vacuum evacuation effectively.

[実施例] 以下、本発明の一実施例を第1図を参照して説明する。[Example] An embodiment of the present invention will be described below with reference to FIG.

なお、第2図と共通する部分には同一符号を付し、その
説明を省略する。
Note that parts common to those in FIG. 2 are denoted by the same reference numerals, and their explanations will be omitted.

二〇油回転真空ポンプは、前述した構成において、第1
段ポンプ室P1と強制給油手段7とを電磁バルブ11を
介設した油路12によって接続し、そのバルブ11を前
記第1ポンプ室P1の吸気口4、に付帯して設けた真空
スイッチPに連動して開閉するようにしている。具体的
には、該真空スイッチPが作動しない時はバルブ11を
「開」にしておき、真空スイッチPが設定圧を感知して
作動したらバルブ11を「閉」に切り換えるようにして
いる。その設定圧は、第1段ポンプ室P工に給油される
油中の空気によって排気性能が低下し始めるような圧力
(例えば、10−’Torrの排気能力のポンプであれ
ばITorr程度)に設定しである。
20 Oil rotary vacuum pump has the above-mentioned configuration.
The stage pump chamber P1 and the forced oil supply means 7 are connected by an oil passage 12 with an electromagnetic valve 11 interposed therebetween, and the valve 11 is connected to a vacuum switch P attached to the intake port 4 of the first pump chamber P1. They are designed to open and close in conjunction with each other. Specifically, when the vacuum switch P does not operate, the valve 11 is kept open, and when the vacuum switch P senses the set pressure and operates, the valve 11 is switched to the closed position. The set pressure is set at such a pressure that the exhaust performance begins to deteriorate due to the air in the oil supplied to the first stage pump chamber P (for example, about ITorr for a pump with an exhaust capacity of 10-'Torr). It is.

このような油回転真空ポンプであると、排気当初の負荷
運転時等において吸気口41の圧力が高い間はバルブ1
1が「開」となり、第1段ポンプ室P1に強制給油手段
7から直接大量の給油が行われることになる。このため
、潤滑不足を有効に解消することができる。次に、吸気
口41の圧力が設定圧を下回ると、真空スイッチPが作
動してバルブ11が閉となり、第1段ポンプ室P1に在
来の差圧給油路8を介して第2段ポンプ室P2から脱気
後の油のみが必要最少限度において給油されることにな
る。このため、例えばこのポンプの限界到達圧力である
1 0 ’Torrの真空排気を有効に行うことが可能
になる。
With such an oil rotary vacuum pump, the valve 1 is closed while the pressure in the intake port 41 is high during load operation at the beginning of exhaust.
1 is "open", and a large amount of oil is directly supplied to the first stage pump chamber P1 from the forced oil supply means 7. Therefore, insufficient lubrication can be effectively resolved. Next, when the pressure in the intake port 41 falls below the set pressure, the vacuum switch P is activated and the valve 11 is closed, and the second stage pump is supplied to the first stage pump chamber P1 via the conventional differential pressure oil supply path 8. Only the degassed oil is supplied from the chamber P2 to the minimum necessary extent. Therefore, it becomes possible to effectively perform vacuum evacuation at, for example, 10' Torr, which is the ultimate pressure of this pump.

また、このような構成であれば、半導体製造装置等にも
好適に適用が可能となる。すなわち、ガスが常時フロー
しているチャンバに接続される吸気口4、は、運転が定
常状態に入ってもさほど圧力が下がらず、ポンプは持続
的な負荷運転状態を強いられる。このため、設定圧を調
整して真空スイッチPが作動しないようにしておくと、
バルブ11を終始「開」の状態にしておくことができ、
強制給油手段7から大量の油を第1段ポンプ室P1内に
継続して導くことで高い潤滑機能を維持することが可能
になる。勿論、このような手法は凝縮性ガスを排気する
際にも有効に利用できるものとなる。
Further, such a configuration can be suitably applied to semiconductor manufacturing equipment and the like. In other words, the pressure of the inlet port 4 connected to the chamber in which gas is constantly flowing does not decrease significantly even when the operation enters a steady state, and the pump is forced to operate under a continuous load. Therefore, if you adjust the set pressure so that the vacuum switch P does not operate,
The valve 11 can be kept in the "open" state from beginning to end,
By continuously introducing a large amount of oil from the forced oil supply means 7 into the first stage pump chamber P1, it becomes possible to maintain a high lubrication function. Of course, such a method can also be effectively used when exhausting condensable gas.

以上、本発明の一実施例について説明したが、各部の構
成は図示例に限定されるものではなく、本発明の趣旨を
逸脱しない範囲で種々変形が可能である。
Although one embodiment of the present invention has been described above, the configuration of each part is not limited to the illustrated example, and various modifications can be made without departing from the spirit of the present invention.

[発明の効果コ 本発明の油回転真空ポンプは、以上のような構成である
から、負荷運転時に強制給油手段から第1段ポンプ室に
大量の油を導入することができ、これにより該ポンプ室
における潤滑を有効に行って焼き付き等を防止すること
ができる。このため、一般の真空排気における排気開始
当初や、半導体製造装置等のチャンバ排気時、或いは凝
縮性ガス排気時におけるポンプの信頼性を有効に高める
ことが可能になる。また、無負荷運転時に強制給油手段
を遮断して在来の差圧給油に移行し、脱気後の油を送り
込むことができるので、高真空排気を行う場合に性能低
下を来たすことを防止することができる。
[Effects of the Invention] Since the oil rotary vacuum pump of the present invention has the above-described configuration, a large amount of oil can be introduced into the first stage pump chamber from the forced oil supply means during load operation. It is possible to effectively lubricate the chamber and prevent seizure and the like. Therefore, it is possible to effectively improve the reliability of the pump at the beginning of general vacuum evacuation, when evacuating a chamber of semiconductor manufacturing equipment, or when evacuating condensable gas. Additionally, during no-load operation, the forced lubrication means can be shut off and the system can shift to conventional differential pressure lubrication, allowing oil to be pumped in after degassing, which prevents performance deterioration when performing high-vacuum exhaust. be able to.

【図面の簡単な説明】[Brief explanation of drawings]

第1図は本発明の一実施例を示す模式図、第2図は従来
例を示す第1図相当の模式図である。
FIG. 1 is a schematic diagram showing an embodiment of the present invention, and FIG. 2 is a schematic diagram corresponding to FIG. 1 showing a conventional example.

Claims (1)

【特許請求の範囲】[Claims]  第2段ポンプ室に強制給油手段を接続し、その第2段
ポンプ室を差圧給油路を介して第1段ポンプ室に連通さ
せてなる2段形の油回転真空ポンプにおいて、前記第1
段ポンプ室にバルブを介して前記強制給油手段を接続し
、そのバルブを前記第1段ポンプ室の吸気口圧力の高低
に応じて開閉するようにしたことを特徴とする油回転真
空ポンプ。
A two-stage oil rotary vacuum pump in which a forced oil supply means is connected to the second stage pump chamber, and the second stage pump chamber is communicated with the first stage pump chamber via a differential pressure oil supply path.
An oil rotary vacuum pump characterized in that the forced oil supply means is connected to the stage pump chamber via a valve, and the valve is opened and closed depending on the level of the intake port pressure of the first stage pump chamber.
JP14050690A 1990-05-29 1990-05-29 Oil-sealed rotary vacuum pump Pending JPH0436091A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP14050690A JPH0436091A (en) 1990-05-29 1990-05-29 Oil-sealed rotary vacuum pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP14050690A JPH0436091A (en) 1990-05-29 1990-05-29 Oil-sealed rotary vacuum pump

Publications (1)

Publication Number Publication Date
JPH0436091A true JPH0436091A (en) 1992-02-06

Family

ID=15270234

Family Applications (1)

Application Number Title Priority Date Filing Date
JP14050690A Pending JPH0436091A (en) 1990-05-29 1990-05-29 Oil-sealed rotary vacuum pump

Country Status (1)

Country Link
JP (1) JPH0436091A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0597730A1 (en) * 1992-11-13 1994-05-18 The BOC Group plc Two stage vacuum pump
EP1536140A1 (en) * 2003-11-27 2005-06-01 Aisin Seiki Kabushiki Kaisha Multistage dry vacuum pump
US7670119B2 (en) * 2004-04-21 2010-03-02 Alcatel Multistage vacuum pump and a pumping installation including such a pump
JP2017523339A (en) * 2014-06-27 2017-08-17 アテリエ ビスク ソシエテ アノニムAtelier Busch SA Vacuum pumping method and vacuum pump system
FR3112578A3 (en) * 2020-07-20 2022-01-21 Pfeiffer Vacuum Rotary vane vacuum pump, detector and freeze-drying installation

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0597730A1 (en) * 1992-11-13 1994-05-18 The BOC Group plc Two stage vacuum pump
US5573387A (en) * 1992-11-13 1996-11-12 The Boc Group Plc Vacuum pumps
EP1536140A1 (en) * 2003-11-27 2005-06-01 Aisin Seiki Kabushiki Kaisha Multistage dry vacuum pump
US7670119B2 (en) * 2004-04-21 2010-03-02 Alcatel Multistage vacuum pump and a pumping installation including such a pump
JP2017523339A (en) * 2014-06-27 2017-08-17 アテリエ ビスク ソシエテ アノニムAtelier Busch SA Vacuum pumping method and vacuum pump system
FR3112578A3 (en) * 2020-07-20 2022-01-21 Pfeiffer Vacuum Rotary vane vacuum pump, detector and freeze-drying installation

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