JP2891047B2 - Vane type vacuum pump - Google Patents
Vane type vacuum pumpInfo
- Publication number
- JP2891047B2 JP2891047B2 JP5194494A JP19449493A JP2891047B2 JP 2891047 B2 JP2891047 B2 JP 2891047B2 JP 5194494 A JP5194494 A JP 5194494A JP 19449493 A JP19449493 A JP 19449493A JP 2891047 B2 JP2891047 B2 JP 2891047B2
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- casing
- oil supply
- vacuum pump
- vane
- 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 - Fee Related
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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-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
- F04C18/34—Rotary-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
- F04C18/344—Rotary-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
- F04C18/3441—Rotary-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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C18/3442—Rotary-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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
-
- 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
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、ベーン式真空ポンプに
係り、特に自動車用真空ポンプ付発電機に直結するに好
適なベーン式真空ポンプに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane type vacuum pump, and more particularly to a vane type vacuum pump suitable for directly connecting to a generator with a vacuum pump for an automobile.
【０００２】[0002]
【従来の技術】従来のベーン式真空ポンプの真空ポンプ
内部の圧力（オイルシール部の圧力）の低減の方法とし
ては、特開平1−170783 号公報または特開昭61−145390
号公報等知られている。2. Description of the Related Art As a method for reducing the pressure inside a vacuum pump (pressure of an oil seal portion) of a conventional vane type vacuum pump, Japanese Patent Application Laid-Open No. 1-170783 or Japanese Patent Application Laid-Open No. 61-145390 has been proposed.
Is known.
【０００３】[0003]
【発明が解決しようとする課題】上記従来技術は、真空
ポンプの回転中における内部の圧力（オイルシール部の
圧力）を低減することが開示されているが、回転停止中
に潤滑油圧が真空ポンプ内部に直接作用し、潤滑油圧の
印加に伴うオイルシールへの弊害については考慮してい
るものでない。The above prior art discloses that the internal pressure (pressure of the oil seal portion) is reduced during rotation of the vacuum pump, but the lubricating oil pressure is reduced during rotation of the vacuum pump. It does not directly consider the adverse effect on the oil seal due to the application of the lubricating oil pressure.
【０００４】本発明の目的は、回転停止中に潤滑油圧が
真空ポンプに直接作用してもオイルシールの位置ずれを
発生しない信頼性の高い真空ポンプを提供することにあ
る。An object of the present invention is to provide a highly reliable vacuum pump which does not cause displacement of an oil seal even if lubricating oil pressure directly acts on the vacuum pump during rotation stop.
【０００５】[0005]
【課題を解決するための手段】上記目的は、円筒状のケ
ーシングと、ケーシングの開口部を覆うプレートと、前
記ケーシングの中心軸と異なる位置に回転軸を設けたロ
ータの外壁面と、前記ロータに設けられた摺動可能なベ
ーンとによって囲まれた外室に吸入口から取り入れた気
体を導入し、前記ロータの回転により前記気体を圧縮
し、圧縮した前記気体を吐出口から吐出するベーン式真
空ポンプであって、前記ケーシングの底部に設けられ、
加圧された潤滑油をケーシング外部より導入する給油穴
と、所定複数のロータ回転角において前記給油穴と前記
ロータ内周部に設けられた内室とを連通させる給油通路
と、前記給油通路により前記給油穴と前記内室が連通し
ている間、前記給油穴が連通している前記内室と前記吐
出口に連通している前記外室とを連通させる通路とを有
することにより達成される。An object of the present invention is to provide a cylindrical casing.
And the plate covering the casing opening,
Rotation shaft provided at a position different from the center axis of the casing
The outer wall surface of the rotor and a slidable
To the outside room surrounded by the air inlet
The body is introduced and the gas is compressed by the rotation of the rotor
And a vane-type tube for discharging the compressed gas from a discharge port.
An empty pump, provided at the bottom of the casing,
Oil supply hole for introducing pressurized lubricating oil from outside the casing
At a plurality of predetermined rotor rotation angles,
An oil supply passage communicating with an inner chamber provided on the inner periphery of the rotor
And the oil supply hole communicates with the inner chamber through the oil supply passage.
While the oil supply hole is in communication with the inner chamber,
A passage communicating with the outside chamber communicating with the outlet.
It is achieved by.
【０００６】[0006]
【作用】潤滑油圧は、給油通路により給油穴と内室が連
通している間、潤滑油圧が作用するが、内室から吐出口
へつながる通路により潤滑油が吐出口へ逃げるため、オ
イルシール部の圧力は減圧される。 [Function] The lubricating oil pressure connects the oil supply hole and the inner chamber by the oil supply passage.
During the passage , the lubricating oil pressure is applied, but since the lubricating oil escapes to the discharge port through the passage from the inner chamber to the discharge port, the pressure in the oil seal portion is reduced .
【０００７】[0007]
【実施例】以下、本発明の一実施例を図１〜図７により
詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to FIGS.
【０００８】実施例は、自動車用真空ポンプ付発電機の
ベーン式真空ポンプに適用したものである。The embodiment is applied to a vane vacuum pump of a generator with a vacuum pump for an automobile.
【０００９】回転軸７は、軸受９により支持されてい
る。回転軸７の端部にはロータ２が嵌装されている。ロ
ータ２は複数個のベーン１を摺動自在に保持する。ロー
タ２,ベーン１は吸入口３ａと吐出口３ｂを持ったケー
シング３に収納されている、ケーシング３の開口端はプ
レート５により塞がれている。プレート５には穴があり
回転軸７が貫通する。ケーシング３の底面には、ケーシ
ング３内を潤滑するための潤滑油が流入する給油穴３ｃ
がある。該給油穴３ｃに対向するようにロータ２の平面
部２ａが位置する、その平面部２ａには、潤滑油の流路
となる給油溝２ｂが複数個ある。ケーシング３とプレー
ト５，プレート５と発電機のブラケット１０間は、Ｏリ
ング１１ａ，１１ｂにより密封されている。回転軸７と
発電機のブラケット１０間は、ブラケット１０の箱部
に、ある保持力を持つために圧入されたオイルシール６
により回転密封されている。オイルシール６の保持力を
増すために、ブラケット１０の箱部の内周部には、オイ
ルシール抜け（位置ずれ）防止用の三角溝１２がある。
オイルシール６は、その保持力により給油穴３ｃを介し
て、供給される潤滑油の潤滑油圧に耐えるようになって
いる。The rotating shaft 7 is supported by a bearing 9. The rotor 2 is fitted on the end of the rotating shaft 7. The rotor 2 slidably holds the plurality of vanes 1. The rotor 2 and the vane 1 are housed in a casing 3 having a suction port 3a and a discharge port 3b. The opening end of the casing 3 is closed by a plate 5. The plate 5 has a hole and the rotating shaft 7 penetrates. An oil supply hole 3c into which a lubricating oil for lubricating the inside of the casing 3 flows is provided on the bottom surface of the casing 3.
There is. The flat portion 2a of the rotor 2 is located so as to face the oil supply hole 3c. The flat portion 2a has a plurality of lubrication grooves 2b serving as lubricating oil flow paths. The space between the casing 3, the plate 5, the plate 5, and the bracket 10 of the generator is sealed by O-rings 11a, 11b. An oil seal 6 press-fitted into the box of the bracket 10 to have a certain holding force is provided between the rotating shaft 7 and the bracket 10 of the generator.
Is sealed by rotation. In order to increase the holding force of the oil seal 6, a triangular groove 12 for preventing the oil seal from coming off (displaced) is provided on the inner periphery of the box of the bracket 10.
The oil seal 6 is adapted to withstand the lubricating oil pressure of the supplied lubricating oil through the oil supply hole 3c by its holding force.
【００１０】通常、ロータ２が回転中においては、図７
に示すように、オイルシール６に印加される圧力は、プ
レート５に設けた第一の溝５ａにより潤滑油が流れるた
め潤滑油圧より低く、オイルシール６の保持力以下であ
り、オイルシール６が位置ずれを起こすことはない。と
ころが、回転停止したとき、例えば、エンジン動力を発
電機に伝達し、発電機を駆動するベルト（図示せず）に
ゆるみ，切損等の障害が生じた場合、潤滑油圧は印加さ
れるが、真空ポンプの回転は停止しているケースが希に
発生する。この場合においては、図６に示すように潤滑
油圧が、直接オイルシール６に印加され、オイルシール
６の位置ずれおよびオイルシールリップ６ａの反転が発
生し、最終的にはオイルシール６よりの潤滑油漏れに至
る。この状態は、図４のようにケーシング３の給油穴３
ｃとロータ２の給油溝２ｂが一致したロータの回転角度
のときに現われる現象である。その他の場合は、図５の
ように、ケーシング３の給油穴３ｃは、ロータ２の平面
部２ａで塞がれるため、発生しない。ケーシング３の給
油穴３ｃとロータ２の給油溝２ｂが合致した場合、ケー
シング３内に流入した潤滑油は、ケーシング３内はベー
ン１，ロータ２，プレート５により仕切られており、従
来の第一の溝５ａだけでは、第一の溝５ａを流れた潤滑
油の逃げ場がないために、図１のロータ２の内周部の室
８ａ及び、ベーン１，ケーシング３，ロータ２，プレー
ト５で仕切られた室８ｂに充満する。このため、ロータ
２の内周部の室８ａと連通しているオイルシール部６ｂ
には潤滑油圧が直接印加されることになる。Normally, when the rotor 2 is rotating, FIG.
As shown in the figure, the pressure applied to the oil seal 6 is lower than the lubricating oil pressure because the lubricating oil flows through the first groove 5 a provided in the plate 5, and is lower than the holding force of the oil seal 6. There is no displacement. However, when the rotation is stopped, for example, when the engine power is transmitted to the generator and a belt (not shown) for driving the generator is loosened or cut off, lubricating oil pressure is applied. In rare cases, the rotation of the vacuum pump is stopped. In this case, as shown in FIG. 6, the lubricating oil pressure is directly applied to the oil seal 6, and the displacement of the oil seal 6 and the reversal of the oil seal lip 6a occur. Oil leaks. In this state, as shown in FIG.
This phenomenon occurs when the rotation angle of the rotor coincides with the oil supply groove 2b of the rotor 2. In other cases, as shown in FIG. 5, the oil supply hole 3c of the casing 3 is closed by the flat portion 2a of the rotor 2, and thus does not occur. When the oil supply hole 3c of the casing 3 matches the oil supply groove 2b of the rotor 2, the lubricating oil flowing into the casing 3 is partitioned by the vane 1, the rotor 2 and the plate 5, and Since there is no escape for the lubricating oil flowing through the first groove 5a only with the groove 5a, the chamber 8a at the inner peripheral portion of the rotor 2 and the vane 1, the casing 3, the rotor 2, and the plate 5 in FIG. The filled room 8b is filled. Therefore, the oil seal portion 6b communicating with the chamber 8a of the inner peripheral portion of the rotor 2
Is directly applied with the lubricating oil pressure.
【００１１】そこで、本実施例のように、吐出口３ｂに
潤滑油を導く、第２の溝５ｂを設けることにより、潤滑
油は、吐出口３ｂに流出するため、オイルシール部６ｂ
の圧力は、オイルシール６の保持力以下の適正な圧力に
低減され、回転停止時においてもオイルシール６の位置
ずれおよびオイルシールリップ６ａの反転の発生は完全
に防止できる。なお、第２の溝５ｂを設ける位置には制
約がある。それは、ケーシング３の給油穴３ｃとロータ
２の給油溝２ｂが一致するロータ２の回転角度のとき、
第２の溝５ｂと吐出口３ｂの開始点Ｐの間にベーン１が
位置しないことである。Therefore, as in this embodiment, by providing the second groove 5b for guiding the lubricating oil to the discharge port 3b, the lubricating oil flows out to the discharge port 3b, so that the oil seal portion 6b
Is reduced to an appropriate pressure equal to or less than the holding force of the oil seal 6, and even when the rotation is stopped, the displacement of the oil seal 6 and the reversal of the oil seal lip 6a can be completely prevented. There is a restriction on the position where the second groove 5b is provided. That is, when the oil supply hole 3c of the casing 3 and the oil supply groove 2b of the rotor 2 coincide with each other, the rotation angle of the rotor 2
The vane 1 is not located between the second groove 5b and the start point P of the discharge port 3b.
【００１２】この範囲（間）にベーン１が位置する条件
がある場合、せっかく第２の溝５ｂを設けても第２の溝
５ｂから流出した潤滑油はベーン１で止められて、吐出
口３ｂに抜けないため、オイルシール部６ｂの圧力は、
従来と同じになってしまう。従って、図２，図３に示す
ようにケーシング３の給油穴３ｃとロータ２の給油溝２
ｂが一致し始めるロータ２の回転角（図２）および一致
が終わるロータ２の回転角（図３）の範囲において、ベ
ーン１は、吐出口の開始点Ｐおよび第２の溝５ｂの位置
より回転方向に進んだ位置に１枚のベーン１ａがあり、
その後のベーン１ｂは、吐出口３ｂの開始点Ｐおよび第
２の溝５ｂの位置より、後にあることが絶対条件とな
る。以上の制約条件を満足すれば、溝の形，穴の形は、
どのようなものでも可である。ようするに、図２，図３
に示すようにケーシング３の給油穴３ｃとロータ２の給
油溝２ｂが一致し始めるロータ２の回転角（図２）およ
び一致が終わるロータ２の回転角（図３）の範囲におい
て、ロータ２の内周部の室８ａにつながる第二の溝５ｂ
は、ケーシング３，ロータ２，ベーン１，プレート５で
仕切られた複数の室８の内、吐出口に連通している室８
ｃに他端はつながっていることが必要である。If there is a condition that the vane 1 is located in this range (between), even if the second groove 5b is provided, the lubricating oil flowing out from the second groove 5b is stopped by the vane 1 and the discharge port 3b , The pressure of the oil seal portion 6b is
It will be the same as before. Therefore, as shown in FIGS. 2 and 3, the oil supply hole 3 c of the casing 3 and the oil supply groove 2
In the range of the rotation angle of the rotor 2 at which b begins to coincide (FIG. 2) and the rotation angle of the rotor 2 at which the coincidence ends (FIG. 3), the vane 1 moves from the start point P of the discharge port and the position of the second groove 5b. There is one vane 1a at the position advanced in the rotation direction,
It is an absolute condition that the subsequent vane 1b is located after the start point P of the discharge port 3b and the position of the second groove 5b. If the above constraints are satisfied, the shape of the groove and hole will be
Anything is possible. As shown in FIGS. 2 and 3
As shown in FIG. 5, the rotation angle of the rotor 2 (FIG. 2) where the oil supply hole 3c of the casing 3 and the oil supply groove 2b of the rotor 2 start to coincide with each other and the rotation angle of the rotor 2 where the coincidence ends (FIG. 3) end. Second groove 5b leading to chamber 8a at the inner periphery
Is a chamber 8 communicating with a discharge port among a plurality of chambers 8 partitioned by a casing 3, a rotor 2, a vane 1, and a plate 5.
The other end needs to be connected to c.
【００１３】本実施例によれば、真空ポンプ回転中のオ
イルシール部６ｂの圧力は、従来よりさらに低減される
ため、オイルシール６と回転軸７の摺接によるオイルシ
ール６の摩耗および回転軸７の摩耗を低減出来、長寿命
化を図れる効果だけではなく、ベルトの障害で発生する
真空ポンプの回転停止のケースにおいても、オイルシー
ル部６ｂに印加される圧力を低減することができるた
め、オイルシール６の位置ずれおよびオイルシールリッ
プ６ａの反転による潤滑油洩れを防止でき、信頼性向上
の効果がある。また、オイルシール６の保持力を増すた
めに、設けていたブラケット１０の箱部の三角溝１２を
廃止することも可能となり、加工工程廃止によるコスト
低減の効果もある。According to this embodiment, since the pressure of the oil seal portion 6b during rotation of the vacuum pump is further reduced, the abrasion of the oil seal 6 due to the sliding contact between the oil seal 6 and the rotation shaft 7 and the rotation of the rotation shaft 7, the pressure applied to the oil seal portion 6b can be reduced not only in the effect of extending the life of the vacuum pump but also in the case where the rotation of the vacuum pump is stopped due to the belt failure. Lubricating oil leakage due to displacement of the oil seal 6 and reversal of the oil seal lip 6a can be prevented, and there is an effect of improving reliability. Further, in order to increase the holding force of the oil seal 6, the triangular groove 12 in the box portion of the bracket 10 provided can be eliminated, and there is also an effect of cost reduction by eliminating the processing step.
【００１４】他の実施例としては、前述の第１の溝５ａ
を廃止し、第２の溝５ｂのみにする案がある。これによ
れば、回転停止時の効果は、前述の場合と同じである
が、回転中のオイルシール部６ｂの圧力は、第１の溝５
ａがある場合より高くなり、その分、前述の効果も小さ
くなる。なお、第１の溝５ａ，第２の溝５ｂは、ケーシ
ング３側に設けても可である。効果は前述の場合と同じ
である。In another embodiment, the first groove 5a is used.
Is abolished and only the second groove 5b is provided. According to this, the effect at the time of rotation stop is the same as the above case, but the pressure of the oil seal portion 6b during rotation is reduced by the first groove 5
a is higher than in the case where a is present, and the effect described above is correspondingly reduced. Note that the first groove 5a and the second groove 5b may be provided on the casing 3 side. The effect is the same as in the case described above.
【００１５】[0015]
【発明の効果】本発明によれば、真空ポンプ回転停止中
に潤滑油圧が真空ポンプに直接印加されるケースが発生
しても、オイルシール部の圧力を効果的に低減できるた
め、オイルシールの位置ずれおよびオイルシールリツプ
の反転に伴い発生する潤滑油洩れの防止を図れ、信頼性
の高い真空ポンプを提供出来る。According to the present invention, even if the lubricating oil pressure is directly applied to the vacuum pump while the vacuum pump stops rotating, the pressure of the oil seal can be effectively reduced. It is possible to prevent the leakage of the lubricating oil caused by the displacement and the reversal of the oil seal lip, and to provide a highly reliable vacuum pump.
【図１】図４のＩ−Ｉ断面図。FIG. 1 is a sectional view taken along the line II of FIG.
【図２】図４のＩ−Ｉ断面図でケーシングの給油穴とロ
ータの給油溝が一致し始めるロータの状態を示す図。FIG. 2 is a sectional view taken along line II of FIG. 4, showing a state of the rotor in which an oil supply hole of a casing and an oil supply groove of the rotor start to coincide with each other.
【図３】図４のＩ−Ｉ断面図でケーシングの給油穴とロ
ータの給油溝が一致し終わるロータの状態を示す図。FIG. 3 is a diagram showing a state of the rotor in which an oil supply hole of a casing and an oil supply groove of the rotor end in the sectional view taken along the line II of FIG. 4;
【図４】真空ポンプの取付け状態を示す縦断面図。FIG. 4 is a vertical cross-sectional view showing a mounted state of a vacuum pump.
【図５】真空ポンプの取付け状態を示す縦断面図で回転
角度を持たせた図。FIG. 5 is a vertical cross-sectional view showing a mounted state of a vacuum pump, with a rotation angle.
【図６】真空ポンプ回転停止時における潤滑油圧とオイ
ルシール部の圧力を示す関係図。FIG. 6 is a relationship diagram showing lubricating oil pressure and oil seal portion pressure when the vacuum pump stops rotating.
【図７】真空ポンプ回転中における回転数に対するオイ
ルシール部の圧力を示す関係図。FIG. 7 is a relationship diagram showing a pressure of an oil seal portion with respect to a rotation speed during rotation of the vacuum pump.
１…ベーン、２…ロータ、２ａ…平面部、２ｂ…給油
溝、３…ケーシング、３ａ…吸入口、３ｂ…吐出口、３
ｃ…給油穴、５…プレート、５ａ…第１の溝（ロータの
内周部の室とロータ，ベーン，ケーシング，プレートに
より仕切られた室をつなぐ溝）、５ｂ…第２の溝（ロー
タの内周部の室と吐出口に連通しているロータ，ベー
ン，ケーシング，プレートにより仕切られた室をつなぐ
溝）、６…オイルシール、７…回転軸、８…ロータ，ベ
ーン，ケーシング，プレートにより仕切られた室、８ａ
…ロータの内周部の室、８ｂ…第１の溝につながってい
るロータ，ベーン，ケーシング，プレートにより仕切ら
れた室、８ｃ…吐出口に連通しているロータ，ベーン，
ケーシング，プレートにより仕切られた室。DESCRIPTION OF SYMBOLS 1 ... vane, 2 ... rotor, 2a ... flat part, 2b ... oil supply groove, 3 ... casing, 3a ... suction port, 3b ... discharge port, 3
c: lubrication hole, 5: plate, 5a: first groove (groove that connects a chamber defined by the inner peripheral portion of the rotor and the rotor, vane, casing, plate), 5b: second groove (of the rotor) A groove connecting the chamber defined by the inner peripheral chamber and the discharge port with a rotor, a vane, a casing, and a plate), 6: an oil seal, 7: a rotating shaft, 8: a rotor, a vane, a casing, and a plate Partitioned room, 8a
... chamber at the inner peripheral portion of the rotor, 8b ... chamber partitioned by a rotor, vane, casing, plate connected to the first groove, 8c ... rotor, vane communicating with the discharge port
A room separated by a casing and a plate.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 秋山 登志勝 茨城県勝田市大字高場2520番地 株式社 日立製作所 自動車機器事業部内 (56)参考文献 特開 平１−170783（ＪＰ，Ａ) 特開 昭63−280887（ＪＰ，Ａ) (58)調査した分野(Int.Cl.6，ＤＢ名) F04C 23/00 - 29/10 F04C 2/30 - 2/352 F04C 18/30 - 18/352 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Toshikatsu Akiyama 2520 Oji Takaba, Katsuta-shi, Ibaraki Hitachi, Ltd. Automotive Equipment Division (56) References JP-A-1-170783 (JP, A) 63-80887 (JP, A) (58) Fields investigated (Int. Cl. 6 , DB name) F04C 23/00-29/10 F04C 2/30-2/352 F04C 18/30-18/352
Claims (1)
部を覆うプレートと、前記ケーシングの中心軸と異なる
位置に回転軸を設けたロータの外壁面と、前記ロータに
設けられた摺動可能なベーンとによって囲まれた外室に
吸入口から取り入れた気体を導入し、前記ロータの回転
により前記気体を圧縮し、圧縮した前記気体を吐出口か
ら吐出するベーン式真空ポンプであって、前記ケーシン
グの底部に設けられ、加圧された潤滑油をケーシング外
部より導入する給油穴と、所定複数のロータ回転角にお
いて前記給油穴と前記ロータ内周部に設けられた内室と
を連通させる給油通路と、前記給油通路により前記給油
穴と前記内室が連通している間、前記給油穴が連通して
いる前記内室と前記吐出口に連通している前記外室とを
連通させる通路とを有するベーン式真空ポンプ。 1. A cylindrical casing, a plate covering an opening of the casing, an outer wall surface of a rotor provided with a rotating shaft at a position different from a center axis of the casing, and a slidable member provided on the rotor. A vane-type vacuum pump for introducing a gas taken in from an inlet into an outer chamber surrounded by a vane, compressing the gas by rotation of the rotor, and discharging the compressed gas from a discharge outlet, wherein the casing An oil supply hole provided at the bottom of the oil supply hole for introducing pressurized lubricating oil from the outside of the casing, and an oil supply passage communicating the oil supply hole with an inner chamber provided at the rotor inner peripheral portion at a plurality of rotor rotation angles. And a passage for communicating the inner chamber with which the oil supply hole communicates and the outer chamber with which the discharge port communicates while the oil supply hole communicates with the inner chamber by the oil supply passage. Vane vacuum pump having.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5194494A JP2891047B2 (en) | 1993-08-05 | 1993-08-05 | Vane type vacuum pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5194494A JP2891047B2 (en) | 1993-08-05 | 1993-08-05 | Vane type vacuum pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0749094A JPH0749094A (en) | 1995-02-21 |
| JP2891047B2 true JP2891047B2 (en) | 1999-05-17 |
Family
ID=16325460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5194494A Expired - Fee Related JP2891047B2 (en) | 1993-08-05 | 1993-08-05 | Vane type vacuum pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2891047B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7014439B2 (en) | 2002-07-29 | 2006-03-21 | Denso Corporation | Vane pump having volume variable pump chambers communicatable with inlet and outlet |
| EP1890040B1 (en) | 2002-11-13 | 2012-06-27 | ixetic Hückeswagen GmbH | Vacuum pump |
-
1993
- 1993-08-05 JP JP5194494A patent/JP2891047B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0749094A (en) | 1995-02-21 |
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