JPH0526038B2 - - Google Patents

Info

Publication number
JPH0526038B2
JPH0526038B2 JP59078408A JP7840884A JPH0526038B2 JP H0526038 B2 JPH0526038 B2 JP H0526038B2 JP 59078408 A JP59078408 A JP 59078408A JP 7840884 A JP7840884 A JP 7840884A JP H0526038 B2 JPH0526038 B2 JP H0526038B2
Authority
JP
Japan
Prior art keywords
chamber
bearing
shaft
discharge port
screw
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
Application number
JP59078408A
Other languages
Japanese (ja)
Other versions
JPS60222583A (en
Inventor
Yasuo Takahashi
Kotaro Naya
Tetsuya Sato
Koji Takagi
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP7840884A priority Critical patent/JPS60222583A/en
Publication of JPS60222583A publication Critical patent/JPS60222583A/en
Publication of JPH0526038B2 publication Critical patent/JPH0526038B2/ja
Granted 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
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/026Lubricant separation
    • 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
    • F04C27/00Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009Shaft sealings specially adapted for pumps

Landscapes

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

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、スクリユー真空ポンプに関する。[Detailed description of the invention] [Industrial application field] The present invention relates to screw vacuum pumps.

〔従来の技術〕 半導体を製造するには、真空状態にした容器内
にウエハーを収納して行なわれるが、容器内を真
空状態とするには、容器内に窒素ガス等の不活性
ガスを供給しつつ真空ポンプで吸引し容器内の不
純物(主としてO2)を除去し高真空状態とする
ようになつている。
[Prior art] Semiconductor manufacturing is performed by storing wafers in a vacuum container. To create a vacuum inside the container, an inert gas such as nitrogen gas is supplied into the container. At the same time, a vacuum pump is used to remove impurities (mainly O 2 ) inside the container, creating a high vacuum state.

こういつた半導体製造行程において使用される
高真空ポンプは、効率が高いという点において、
ケーシング内に多量の潤滑油を注入しロータ間の
潤滑および各部のシール効果を持たせた潤滑式ポ
ンプがほとんどである。
These high vacuum pumps used in the semiconductor manufacturing process are highly efficient.
Most pumps are lubricated type, in which a large amount of lubricating oil is injected into the casing to provide lubrication between the rotors and seal the various parts.

〔発明が解決しようとする課題〕[Problem to be solved by the invention]

しかし、この潤滑式ポンプでは、多量の潤滑油
がケーシング内に収納されているので半導体製造
過程で用いる各種ガス(例えば、ヒ素、ガリウム
等)と接触して潤滑油としての寿命が非常に短く
なるという問題があつた。また油分子が半導体製
造容器内に逆拡散して半導体製造工程上好ましく
ないという問題があつた。
However, in this type of lubricating pump, a large amount of lubricating oil is stored in the casing, so it comes into contact with various gases (e.g., arsenic, gallium, etc.) used in the semiconductor manufacturing process, and its life as a lubricating oil is extremely shortened. There was a problem. Further, there was a problem in that oil molecules back-diffused into the semiconductor manufacturing container, which was unfavorable in the semiconductor manufacturing process.

また、作動室を無潤滑とし、軸封装置や軸受を
油潤滑する構造も考えられる。しかし、この場
合、軸封装置の潤滑油はロータ軸端部にて大気に
臨んでいるため大気圧に等しいが、吸込側の軸支
部では大気圧よりかなり低く、軸封装置の両側の
間に差圧が生じ、軸封装置だけでは潤滑油がケー
シング内の作動室に侵入することを確実に防止す
ることができない。そのため油分子が逆拡散して
真空容器内に侵入したり、あるいは軸封部から大
気が侵入したりして効率を低下させる等、従来技
術の問題点を十分に解決するまでには至つていな
い。
Furthermore, a structure in which the working chamber is not lubricated and the shaft sealing device and the bearing are lubricated with oil is also considered. However, in this case, the lubricating oil in the shaft sealing device is exposed to the atmosphere at the end of the rotor shaft, so it is equal to atmospheric pressure, but at the shaft portion on the suction side, the pressure is considerably lower than atmospheric pressure, and between both sides of the shaft sealing device. A differential pressure is generated, and the shaft sealing device alone cannot reliably prevent lubricating oil from entering the working chamber within the casing. As a result, the problems of conventional technology, such as oil molecules back-diffusing and entering the vacuum vessel, or air entering from the shaft seal, reducing efficiency, have yet to be fully resolved. do not have.

さらに、軸封装置の外方の軸受を納めた室を吸
込側に連絡することも考えられるが、この場合、
真空容器に最も近いところに油が混入したガスが
流れることになるので、油の逆拡散を防止するこ
とは難しい。
Furthermore, it is also possible to connect the chamber containing the outer bearing of the shaft sealing device to the suction side, but in this case,
Since gas mixed with oil flows to the area closest to the vacuum container, it is difficult to prevent back diffusion of oil.

実開昭50−66209号公報は、スラスト力調整機
構を備えたスクリユー圧縮機において、そのスラ
スト力調整機構の低圧側(軸受室)とねじロータ
の圧縮工程における吸入圧力に近い位置とを連絡
して、スラスト力調整機構に加わる力をバランス
させた例を開示している。しかし、この例におい
ては、軸受室と吸入口とが連通されており、潤滑
油の吸込側への拡散については何ら配慮されてい
ない。
Utility Model Application No. 50-66209 discloses, in a screw compressor equipped with a thrust force adjustment mechanism, the low pressure side (bearing chamber) of the thrust force adjustment mechanism is connected to a position close to the suction pressure in the compression process of the screw rotor. This discloses an example in which the forces applied to the thrust force adjustment mechanism are balanced. However, in this example, the bearing chamber and the suction port are communicated with each other, and no consideration is given to the diffusion of lubricating oil to the suction side.

また、特公昭41−13226号公報は、油溜り室と
吐出側を通気管で連通され、該通気管に油分離カ
バーが装着されている真空ポンプを開示してい
る。しかし、この例においては、油溜り室とポン
プ吸い込み側の差圧発生に伴う油の真空側への拡
散については配慮されていない。
Further, Japanese Patent Publication No. 41-13226 discloses a vacuum pump in which an oil reservoir chamber and a discharge side are communicated through a ventilation pipe, and an oil separation cover is attached to the ventilation pipe. However, in this example, no consideration is given to the diffusion of oil to the vacuum side due to the generation of a differential pressure between the oil reservoir chamber and the pump suction side.

本発明は前記問題点に鑑みなされたもので、そ
の目的は油の逆拡散を防止できるスクリユー真空
ポンプを提供することにある。
The present invention has been made in view of the above-mentioned problems, and its object is to provide a screw vacuum pump that can prevent back diffusion of oil.

〔課題を解決するための手段〕[Means to solve the problem]

上記の課題は、吸込みポート及び吐出ポートが
形成されているポンプケーシングと、軸部が軸受
によつて支持され、互いに溝部と陸部が噛合つて
回転し、複数の作動室を形成するようにポンプケ
ーシング内に配置された雄、雌一対のスクリユー
ロータと、該一対のスクリユーロータの吐出ポー
ト側軸端に設けられ前記軸受及び同期歯車を納め
た軸受室と、を備えたスクリユー真空ポンプにお
いて、前記軸受と作動室の間に設置された軸封装
置と、前記複数の作動室の内で吸込ポートから遮
断されかつ吐出ポートに連通しない作動室と前記
軸受室とを連絡する抽気通路とが設けられ、該抽
気通路にオイルミストセパレータが設けられてい
ることを特徴とするスクリユー真空ポンプにより
達成される。
The above problem is caused by a pump casing in which a suction port and a discharge port are formed, a shaft part supported by a bearing, and a pump in which the groove part and the land part mesh with each other to rotate and form a plurality of working chambers. A screw vacuum pump comprising a pair of male and female screw rotors disposed in a casing, and a bearing chamber provided at a shaft end on the discharge port side of the pair of screw rotors and housing the bearing and a synchronous gear. , a shaft sealing device installed between the bearing and the working chamber, and an air bleed passage communicating between the bearing chamber and the working chamber that is blocked from the suction port and does not communicate with the discharge port among the plurality of working chambers. This is achieved by a screw vacuum pump characterized in that the air extraction passage is provided with an oil mist separator.

〔作用〕[Effect]

吸込ポート及び吐出ポートから遮断された作動
室と同期歯車を納めた軸受室とが抽気通路により
連通されるので、前記軸受室の圧力は、吸入側の
圧力と吐出側の圧力の中間に保持され、スクリユ
ーロータの吐出側端面から、軸封装置、軸受室、
抽気通路を経て、作動室へ至る気体の流れが形成
され、軸受室の同期歯車潤滑用の油が軸封装置を
経て作動室へ拡散するのが防がれる。
Since the working chamber, which is isolated from the suction port and the discharge port, and the bearing chamber containing the synchronous gear are communicated through the air bleed passage, the pressure in the bearing chamber is maintained between the pressure on the suction side and the pressure on the discharge side. , from the discharge side end face of the screw rotor, the shaft sealing device, the bearing chamber,
A gas flow is formed through the bleed passage to the working chamber, and oil for lubricating the synchronous gear in the bearing chamber is prevented from diffusing into the working chamber through the shaft sealing device.

又、抽気通路にはオイルミストセパレータが設
けられているから、前記スクリユーロータの吐出
側端面から軸受室を経て作動室へ至る抽気通路内
気体の流れにのつて軸受室の前記油が作動室へ拡
散するのが防がれる。
In addition, since an oil mist separator is provided in the bleed passage, the oil in the bearing chamber flows into the working chamber as the gas in the bleed passage flows from the discharge side end face of the screw rotor to the working chamber via the bearing chamber. This prevents it from spreading to.

〔実施例〕〔Example〕

以下、本発明の一実施例を図により説明する。 Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

第1図、第2図a、第2図bにおいて、符号
2,4はケーシング1内において噛み合うように
配設された雌雄一対のスクリユーロータで、それ
ぞれ、複数の陸部36,38および溝部36A,
38Aを有し、それぞれのロータ2,4の軸部は
ラジアル軸受5やスラスト軸受6(6A,6B)
で支承されている。両ロータ2,4の軸部には同
期歯車9,10が設けられ、両ロータ2,4が同
期して回転するようになつており、ポンプケーシ
ング1の上端部に形成された吸込ポート11から
気体が両ロータ2,4に吸入され圧縮されてケー
シング1下端部に形成された吐出ポート12へ吐
き出され、吸込ポート11と連通されている真空
容器(図示せず)内を真空状態とするようになつ
ている。ラジアル軸受5、スラスト軸受6、同期
歯車9,10には潤滑油が供給されており、これ
らの潤滑油が両ロータ2,4の収納されているケ
ーシング内に侵入しないようにロータの軸支部に
はカーボンリングシール14、ねじシール15か
らなる軸封装置16,17が設けられている。
In FIG. 1, FIG. 2a, and FIG. 2b, reference numerals 2 and 4 indicate a pair of male and female screw rotors disposed to mesh with each other in the casing 1, each having a plurality of land portions 36, 38 and groove portions. 36A,
38A, and the shaft of each rotor 2, 4 is equipped with a radial bearing 5 or a thrust bearing 6 (6A, 6B).
It is supported by Synchronous gears 9 and 10 are provided on the shafts of both rotors 2 and 4 so that both rotors 2 and 4 rotate synchronously. Gas is sucked into both rotors 2 and 4, compressed, and discharged to a discharge port 12 formed at the lower end of the casing 1, so that the inside of a vacuum container (not shown) communicating with the suction port 11 is brought into a vacuum state. It's getting old. Lubricating oil is supplied to the radial bearing 5, thrust bearing 6, and synchronous gears 9 and 10, and in order to prevent these lubricating oil from entering the casing in which both rotors 2 and 4 are housed, the rotor shaft supports are supplied with lubricating oil. Shaft seal devices 16 and 17 consisting of a carbon ring seal 14 and a screw seal 15 are provided.

軸受5,6A,6B、同期歯車9,10が収容
されている部屋51は、作動室18中の吸入ポー
ト11および吐出ポート12の何れにも連通しな
い作動室18Aと抽気通路19によつて連絡され
ている。この抽気通路19の途中にはオイルミス
トセパレータ20が設置されている。抽気通路1
9の作動室18への連絡位置すなわち抽気位置
は、軸封装置16のシール能力によつて定められ
るもので、シール能力が低い場合は、軸受室51
の圧力が吸入圧力に接近したものとなるように、
吸入ポート11と遮断された直後の作動室18A
に連通するように、シール能力が高い場合は、軸
受室51の圧力が吐出圧力に接近したものとなる
ように、吐出ポート12に連通する直前の作動室
18Aに連通するように選択される。
The chamber 51 in which the bearings 5, 6A, 6B and the synchronous gears 9, 10 are housed communicates with the working chamber 18A, which does not communicate with either the suction port 11 or the discharge port 12 in the working chamber 18, through a bleed passage 19. has been done. An oil mist separator 20 is installed in the middle of this bleed passage 19. Bleeding passage 1
9 to the working chamber 18, that is, the air bleed position is determined by the sealing ability of the shaft sealing device 16. If the sealing ability is low, the bearing chamber 51
so that the pressure is close to the suction pressure,
Working chamber 18A immediately after being shut off from suction port 11
If the sealing ability is high, the pressure in the bearing chamber 51 is selected to be connected to the working chamber 18A immediately before communicating with the discharge port 12 so that the pressure in the bearing chamber 51 approaches the discharge pressure.

これによつて、軸封装置16のシール能力に適
合した抽気位置を選定することができ、抽気位置
スクリユーロータ2,4の吐出ポート12寄りに
設置することができる。
Thereby, it is possible to select an air bleed position suitable for the sealing capacity of the shaft sealing device 16, and it is possible to install the air bleed position closer to the discharge port 12 of the screw rotors 2, 4.

第3図、第4図は本発明に係る無潤滑式スクリ
ユー真空ポンプの他の実施例を示す図である。
FIGS. 3 and 4 are diagrams showing other embodiments of the non-lubricated screw vacuum pump according to the present invention.

これらの図において、ポンプケーシング21の
円筒形室22内には、互いに噛み合つて回転する
第1のロータ30と第2のロータ40とが平行に
配設されており、第1、第2のロータ30,40
のロータ軸部はそれぞれラジアル軸受31,41
とスラスト軸受32,42とによつて軸線30
A,40Aまわりに回転可能に支持されている。
ロータ軸の一端には互いに噛み合う同期歯車3
3,43が軸着されており、ロータ軸の他端はポ
ンプケーシング21を貫通して突出し増速ピニオ
ン50、カツプリング(図示せず)を介して原動
機(図示せず)に連結されている。ロータ30,
40のロータ軸部には、カーボンリングシール3
4,44とねじシール35,45からなる軸封装
置が設置されており、軸受31,32,41,4
2、軸受室51内に供給されている潤滑油が円筒
形室22内の作動室18に侵入するのを防いでい
る。
In these figures, a first rotor 30 and a second rotor 40 are disposed in parallel in a cylindrical chamber 22 of a pump casing 21 and rotate while meshing with each other. Rotor 30, 40
The rotor shaft portions of are equipped with radial bearings 31 and 41, respectively.
and the thrust bearings 32, 42, the axis 30
It is rotatably supported around A and 40A.
At one end of the rotor shaft are synchronous gears 3 that mesh with each other.
3 and 43, and the other end of the rotor shaft protrudes through the pump casing 21 and is connected to a prime mover (not shown) via a speed increasing pinion 50 and a coupling ring (not shown). rotor 30,
Carbon ring seal 3 is installed on the rotor shaft of 40.
A shaft sealing device consisting of bearings 31, 32, 41, 4 and screw seals 35, 45 is installed.
2. The lubricating oil supplied in the bearing chamber 51 is prevented from entering the working chamber 18 in the cylindrical chamber 22.

第1のロータ30には、互いにねじれ方向逆向
きにして雄スクリユ羽根36と雌スクリユ羽根3
8とが同一軸上に形成されており、一方第2のロ
ータ40にも互いにねじれ方向逆向きとする雄ス
クリユ羽根46と雌スクリユ羽根48とが形成さ
れており、全く同一形状に形成された2本のロー
タの1本を逆向きにして配設されている。この一
対のロータ30,40に形成されている雄雌のス
クリユ羽根36と48、38と46とは互いに噛
み合うが、同期歯車33,43によつて接触する
ことなく互いに逆方向に回転するようになつてい
る。
The first rotor 30 has male screw blades 36 and female screw blades 3 with opposite torsional directions.
8 are formed on the same axis, and on the other hand, the second rotor 40 is also formed with a male screw blade 46 and a female screw blade 48 whose twist directions are opposite to each other, and are formed in the exact same shape. One of the two rotors is arranged in the opposite direction. The male and female screw blades 36 and 48, 38 and 46 formed on the pair of rotors 30 and 40 mesh with each other, but are prevented from coming into contact by the synchronizing gears 33 and 43 so that they rotate in opposite directions. It's summery.

両ロータ30,40間のロータ軸方向中央部に
臨む円筒形室22上部には、吸込口52Aに連通
する吸込ポート52が形成され、一方円筒形室2
2の長手方向両端部下方には吐出口54Aに連通
する吐出ポート54が形成されている。吸込口5
2Aには内部を真空状態にしようとする真空容器
(図示せず)からのびる吸込管56が接続される
ようになつており、両ロータ30,40が噛み合
いながら回転すると、真空容器内のガスは吸込口
52A、吸込ポート52から雌雄のスクリユ羽根
36と48、38と46によつて吸込まれ圧縮さ
れて吐出ポート54から吐出口54Aを経て外部
(大気)に吐出されるようになつている。
A suction port 52 communicating with the suction port 52A is formed in the upper part of the cylindrical chamber 22 facing the center in the rotor axial direction between the two rotors 30 and 40, while the cylindrical chamber 2
A discharge port 54 communicating with the discharge port 54A is formed below both longitudinal ends of the discharge port 2 . Suction port 5
2A is connected to a suction pipe 56 extending from a vacuum container (not shown) whose interior is to be evacuated, and when both rotors 30 and 40 rotate while meshing, the gas in the vacuum container is It is sucked in through the suction port 52A and the suction port 52 by male and female screw blades 36 and 48, 38 and 46, compressed, and then discharged to the outside (atmosphere) through the discharge port 54 and the discharge port 54A.

また、軸受室51内と円筒形室22内の作動室
18A、及び軸受室51が設置されている側と反
対側のケーシングに設置されている軸支部ケーシ
ング60内と円筒形室22内の作動室18Bと
は、管路途中にオイルミストセパレータ62,6
3がそれぞれ設けられている抽気管64,65に
よつて連通されている。円筒形室22内の作動室
18A,18Bの圧力は、第5図に示されるよう
に円筒形室中央部から両端部に向うに従つて高く
なつて両端部で大気圧に等しくなつており、排気
管64,65の円筒形室22内の作動室18A,
18Bへの接続は、互いに噛みあう雄雌ロータの
陸部、溝部および円筒形室22の内周壁面によつ
て画成されて、吸込ポート52とは隔てられた空
間部であつて、円筒形室22の長手方向両端部近
傍位置にしてわずかに大気圧より小さい圧力P1
(第5図参照)となる位置に接続されている。
In addition, the operation chamber 18A in the bearing chamber 51 and the cylindrical chamber 22, and the operation in the shaft support casing 60 and the cylindrical chamber 22 installed in the casing on the opposite side to the side where the bearing chamber 51 is installed. The chamber 18B has oil mist separators 62, 6 in the middle of the pipe.
3 are connected through bleed pipes 64 and 65, respectively. As shown in FIG. 5, the pressure in the working chambers 18A and 18B within the cylindrical chamber 22 increases from the center of the cylindrical chamber toward both ends, and becomes equal to atmospheric pressure at both ends. Working chamber 18A in the cylindrical chamber 22 of the exhaust pipes 64, 65,
The connection to 18B is a space separated from the suction port 52, defined by the land portions of the male and female rotors meshing with each other, the groove portions, and the inner circumferential wall surface of the cylindrical chamber 22, and the cylindrical The pressure P 1 is slightly lower than atmospheric pressure near both ends of the chamber 22 in the longitudinal direction.
(See Figure 5).

オイルミストセパレータ62,63を備えた抽
気管64,65を設けたことにより、軸受室51
内の圧力は、円筒形室22内の作動室18A、軸
受室51側の側壁22Aの位置の圧力P0(これは
大気圧に等しい)よりわずかに低くなり、また軸
支部ケーシング60内の圧力は円筒形室22内の
作動室18Bの軸支部ケーシング60側の側壁2
2B位置の圧力P0(これは大気圧に等しい)より
わずかに低くなるので、軸受31,32,41,
42や軸受室51内に供給されている潤滑油がカ
ーボンリングシール34,44、ねじシール3
5,45からなる軸封装置を通つて円筒形室22
内に侵入することが確実に防止される。更に、オ
イルミストセパレータ62,63が故障したとし
ても、抽気管64,65は吸込みポート52とは
複数の陸部と溝部によつて隔てられた位置に接続
されているので、油分子の上流側(吸入側)への
拡散のおそれは極めて少ない。
By providing air bleed pipes 64 and 65 equipped with oil mist separators 62 and 63, the bearing chamber 51
The pressure inside is slightly lower than the pressure P 0 (which is equal to atmospheric pressure) at the position of the working chamber 18A in the cylindrical chamber 22 and the side wall 22A on the side of the bearing chamber 51, and the pressure inside the shaft support casing 60 is the side wall 2 on the shaft supporting casing 60 side of the working chamber 18B in the cylindrical chamber 22.
Since the pressure at position 2B is slightly lower than P 0 (which is equal to atmospheric pressure), bearings 31, 32, 41,
42 and the bearing chamber 51, the lubricating oil is supplied to the carbon ring seals 34, 44 and the screw seal 3.
The cylindrical chamber 22 is passed through the shaft sealing device consisting of 5 and 45.
Intrusion into the interior is reliably prevented. Furthermore, even if the oil mist separators 62 and 63 fail, the bleed pipes 64 and 65 are connected to the suction port 52 at a position separated by a plurality of land portions and grooves, so that the upstream side of oil molecules The risk of diffusion to the suction side is extremely low.

なお、第1、第2のロータ30,40はいずれ
も両端部が支承され、中央部では一切支承されて
いないが、真空ポンプにおける負荷は非常に小さ
いのでロータの中央部を支承しなくても構造上何
ら問題はない。
Note that both the first and second rotors 30 and 40 are supported at both ends and are not supported at all in the center, but since the load on the vacuum pump is very small, it is not necessary to support the center of the rotor. There are no structural problems.

本実施例によれば、次の効果がある。 According to this embodiment, there are the following effects.

抽気通路の作動室の開口位置を吐出ポート寄
りにできるから潤滑油が円筒形室22内へ侵入
することがなく、油分子の逆拡散が防止され
る。
Since the opening position of the working chamber of the bleed passage can be placed closer to the discharge port, lubricating oil does not enter into the cylindrical chamber 22, and back diffusion of oil molecules is prevented.

また、抽気管64,65を設置したことによ
り、軸封装置の圧力は円筒形室22内の吐出圧
力より低く両側の差圧を小さくすることができ
るため、軸封装置を介して円筒形室内へ油分子
が侵入することも防止できる。
In addition, by installing the air bleed pipes 64 and 65, the pressure of the shaft seal device is lower than the discharge pressure in the cylindrical chamber 22, and the differential pressure on both sides can be reduced. It can also prevent oil molecules from entering the skin.

第3〜第4図の実施例は吸込側に軸支部、軸
封装置がないので吸込側から円筒形室22内に
ガス(大気)が侵入することがなく、圧縮効率
に優れるとともに高真空状態が得られる。した
がつて従来の無潤滑式では得られない広い圧力
範囲での使用が可能となる。
In the embodiments shown in Figures 3 and 4, there is no shaft support or shaft seal device on the suction side, so gas (atmosphere) does not enter into the cylindrical chamber 22 from the suction side, resulting in excellent compression efficiency and a high vacuum state. is obtained. Therefore, it can be used in a wide pressure range that is not possible with conventional non-lubricated systems.

第3〜4図の実施例は、ロータの軸方向に働
くスラストがバランスするのでスラスト軸受3
2,42を小容量にでき、更忍この軸受に供給
する潤滑油量を減らすことができ軸封が容易と
なる。
In the embodiment shown in Figs. 3 and 4, the thrust acting in the axial direction of the rotor is balanced, so the thrust bearing 3
2 and 42 can be reduced in capacity, the amount of lubricating oil supplied to this bearing can be reduced, and shaft sealing can be facilitated.

第3〜4図の実施例は、第1、第2のロータ
30,40は全く同一形状に形成されているの
で、一対の雌雄ロータ加工用ホブだけでロータ
の加工ができ、作業性が極めてよい。
In the embodiment shown in Figs. 3 and 4, the first and second rotors 30 and 40 are formed in exactly the same shape, so the rotors can be machined using only a pair of male and female rotor machining hobs, resulting in extremely high workability. good.

〔発明の効果〕〔Effect of the invention〕

以上の説明から明らかなように本発明によれ
ば、無潤滑式スクリユー真空ポンプにおいて、同
期歯車を備えた軸受室から油が軸封装置を経て作
動室に拡散するのを防止する効果がある。
As is clear from the above description, the present invention has the effect of preventing oil from diffusing from the bearing chamber provided with the synchronous gear into the working chamber via the shaft sealing device in the non-lubricated screw vacuum pump.

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

第1図は本発明の一実施例の縦断平面図、第2
図aは第1図の縦断正面図、第2図bは第2図a
の−断面図、第3図は本発明の他の実施例の
縦断平面図、第4図は第3図の縦断正面図、第5
図はその円筒形室内の長手方向の圧力分布を示す
図である。 1,21…ポンプケーシング、2…雄ロータ、
4…雌ロータ、5…ラジアル軸受、6A,6B…
スラスト軸受、9,10,33,43…同期歯
車、11,52…吸入ポート、12,54A…吐
出ポート、14,34,44…カーボンリングシ
ール、15,35,45…ねじシール、16,1
7…軸封装置、18A,18B…作動室、19,
64,65…抽気管、20,62,63…オイル
ミストセパレータ、36,46,76,86…雄
ロータの陸部または溝部、38,48,78,8
8…雌ロータの溝部または陸部、51…軸受室。
FIG. 1 is a longitudinal sectional plan view of one embodiment of the present invention, and FIG.
Figure a is a vertical sectional front view of Figure 1, Figure 2 b is Figure 2 a
FIG. 3 is a longitudinal sectional plan view of another embodiment of the present invention, FIG. 4 is a longitudinal sectional front view of FIG. 3, and FIG.
The figure shows the pressure distribution in the longitudinal direction of the cylindrical chamber. 1, 21...Pump casing, 2...Male rotor,
4...Female rotor, 5...Radial bearing, 6A, 6B...
Thrust bearing, 9, 10, 33, 43... Synchronous gear, 11, 52... Suction port, 12, 54A... Discharge port, 14, 34, 44... Carbon ring seal, 15, 35, 45... Screw seal, 16, 1
7...Shaft sealing device, 18A, 18B...Working chamber, 19,
64, 65... Air bleed pipe, 20, 62, 63... Oil mist separator, 36, 46, 76, 86... Land part or groove part of male rotor, 38, 48, 78, 8
8... Groove or land portion of female rotor, 51... Bearing chamber.

Claims (1)

【特許請求の範囲】[Claims] 1 吸込ポート及び吐出ポートが形成されている
ポンプケーシングと、軸部が軸受によつて支持さ
れ、互いに溝部と陸部とが噛合つて回転し、複数
の作動室を形成するようにポンプケーシング内に
配置された雄、雌一対のスクリユーロータと、該
1対のスクリユーロータの吐出ポート側軸端に設
けられ前記軸受及び同期歯車を納めた軸受室と、
を備えたスクリユー真空ポンプにおいて、前記軸
受と作動室の間に設置された軸封装置と、前記複
数の作動室の内で吸入ポートから遮断されかつ吐
出ポートに連通しない作動室と前記軸受室とを連
絡する抽気通路と、が設けられ、該抽気通路にオ
イルミストセパレータが設けられていることを特
徴とするスクリユー真空ポンプ。
1. A pump casing in which a suction port and a discharge port are formed, a shaft portion supported by a bearing, and a groove portion and a land portion meshing with each other to rotate and form a plurality of working chambers in the pump casing. a pair of male and female screw rotors disposed; a bearing chamber provided at a shaft end on the discharge port side of the pair of screw rotors and housing the bearing and a synchronous gear;
A screw vacuum pump comprising: a shaft sealing device installed between the bearing and the working chamber; and a working chamber that is shut off from the suction port and does not communicate with the discharge port among the plurality of working chambers, and the bearing chamber. A screw vacuum pump comprising: a bleed passage communicating with the bleed passage; and an oil mist separator provided in the bleed passage.
JP7840884A 1984-04-20 1984-04-20 Screw vacuum pump Granted JPS60222583A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP7840884A JPS60222583A (en) 1984-04-20 1984-04-20 Screw vacuum pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP7840884A JPS60222583A (en) 1984-04-20 1984-04-20 Screw vacuum pump

Publications (2)

Publication Number Publication Date
JPS60222583A JPS60222583A (en) 1985-11-07
JPH0526038B2 true JPH0526038B2 (en) 1993-04-14

Family

ID=13661205

Family Applications (1)

Application Number Title Priority Date Filing Date
JP7840884A Granted JPS60222583A (en) 1984-04-20 1984-04-20 Screw vacuum pump

Country Status (1)

Country Link
JP (1) JPS60222583A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012096057A1 (en) * 2011-01-11 2012-07-19 アネスト岩田株式会社 Dual-shaft rotor pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62261689A (en) * 1986-05-09 1987-11-13 Kobe Steel Ltd Screw type vacuum pump
JP2515831B2 (en) * 1987-12-18 1996-07-10 株式会社日立製作所 Screen vacuum pump
US5281116A (en) * 1993-01-29 1994-01-25 Eaton Corporation Supercharger vent

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57140590A (en) * 1980-12-18 1982-08-31 Pfeiffer Vakuumtechnik Rotary piston pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5066209U (en) * 1973-10-19 1975-06-14

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57140590A (en) * 1980-12-18 1982-08-31 Pfeiffer Vakuumtechnik Rotary piston pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012096057A1 (en) * 2011-01-11 2012-07-19 アネスト岩田株式会社 Dual-shaft rotor pump

Also Published As

Publication number Publication date
JPS60222583A (en) 1985-11-07

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