JPS60145478A - Oil feeding apparatus for rotary vane type compressor - Google Patents
Oil feeding apparatus for rotary vane type compressorInfo
- Publication number
- JPS60145478A JPS60145478A JP25136483A JP25136483A JPS60145478A JP S60145478 A JPS60145478 A JP S60145478A JP 25136483 A JP25136483 A JP 25136483A JP 25136483 A JP25136483 A JP 25136483A JP S60145478 A JPS60145478 A JP S60145478A
- Authority
- JP
- Japan
- Prior art keywords
- passage
- pressure
- valve body
- chamber
- oil supply
- 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.)
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- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明はベーン回転式圧縮機における給油装置に関する
もので、特に自動車用空調装置に供されるベーン回転式
圧縮機に使用する場合に適した給油装置を提供するもの
である。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a lubricating device for a vane rotary compressor, and is particularly suitable for use in a vane rotary compressor used in an automobile air conditioner. It provides:
従来例の構成とその問題点
周知のようにベーン回転式圧縮機においてはロータの回
転に伴なってベーンがその先端をシリンダ内壁に接して
回転摺動運動をするようベーン底部に常時高圧の潤滑油
を作用させる構造が用いられている。Conventional configuration and problems As is well known, in vane rotary compressors, high-pressure lubrication is constantly applied to the bottom of the vane so that as the rotor rotates, the vane rotates and slides with its tip in contact with the inner wall of the cylinder. A structure that allows oil to act is used.
これを実現する手段として一般に、圧縮機の駆動軸上に
装備したポンプ等により強制的に給油する強制給油式と
、圧縮機により圧縮された高圧流体の圧力を利用して圧
縮機の高低圧力差により給油する差圧給油式とが広く利
用されている。Generally, the means to achieve this are the forced lubrication system, which uses a pump installed on the drive shaft of the compressor to forcibly supply lubrication, and the other, which uses the pressure of high-pressure fluid compressed by the compressor to create a pressure difference between the high and low pressures of the compressor. A differential pressure lubrication system is widely used.
しかしながら、強制給油式では圧縮機の回転数上昇に伴
なって給油量も増大しベーンに作用する遠心力とあいま
ってベーンを過度にシリンダ内壁５ ・ ノ
に押接せしめベーン先端部およびシリンダ内壁の摩耗増
と圧縮機の入力増をひき起こす結果となり、圧縮機の耐
久性や効率を悪くするという欠点がある。However, in the forced lubrication type, the amount of lubrication increases as the rotational speed of the compressor increases, and this, combined with the centrifugal force acting on the vanes, causes the vanes to be excessively pressed against the cylinder inner wall 5. This results in increased wear and input to the compressor, which has the disadvantage of deteriorating the durability and efficiency of the compressor.
一方、差圧給油式では上記強制給油式の場合と同様の欠
点をひき起こす過剰な給油を排して、給油通路に給油量
を制限する機構を設けることによって上記現象を軽減し
ている。On the other hand, in the differential pressure lubrication type, the above-mentioned phenomenon is alleviated by eliminating excessive lubrication, which causes the same drawbacks as in the case of the forced lubrication type, and by providing a mechanism in the lubrication passageway to limit the amount of lubrication.
第１図、第２図は従来の差圧給油式の給油装置を有する
ベーン回転式圧縮機の具体構成を示すもので、１は円筒
内壁を有するシリンダ、２はその外周の一部がシリンダ
１内壁と微小隙間を形成すルロータ、３はロータ２に設
けられたベーンスロ・シト４内に摺動自在に挿入された
複数のベーン、５はロータ２と一体的に形成され回転自
在に軸支される駆動軸、６および７はそれぞれシリンダ
１の両端を閉塞して内部に作動室８を形成する前部側板
および後部側板、９は低圧側の作動室に連通する吸入口
、１０は高圧側の作動室８に連通ずる吐出口、１１は吐
出口１０に配設された吐出弁、１２は高圧通路１３に連
通しその内部に高圧室１４を形成し圧縮された高圧流体
中の潤滑油を分離捕捉するスクリーン１５を配設した高
圧ケース、１６は高圧室１４下方の油溜り部とベーン底
部空間１７とを連通する給油通路、１８は給油量を制限
する通路である。Figures 1 and 2 show the specific configuration of a vane rotary compressor with a conventional differential pressure oil supply system, in which 1 is a cylinder with a cylindrical inner wall, and 2 is a cylinder with a part of its outer periphery. 3 is a plurality of vanes slidably inserted into a vane slot 4 provided on the rotor 2, and 5 is integrally formed with the rotor 2 and rotatably supported. 6 and 7 are front and rear side plates that respectively close both ends of the cylinder 1 to form a working chamber 8 inside; 9 is an inlet that communicates with the working chamber on the low-pressure side; and 10 is the inlet that communicates with the working chamber on the high-pressure side. A discharge port communicating with the working chamber 8, 11 a discharge valve disposed in the discharge port 10, 12 communicating with a high pressure passage 13 and forming a high pressure chamber 14 therein to separate lubricating oil from the compressed high pressure fluid. A high pressure case is provided with a screen 15 to capture the oil, 16 is an oil supply passage that communicates the oil reservoir below the high pressure chamber 14 with the vane bottom space 17, and 18 is a passage that limits the amount of oil supplied.
以上のように構成されたベーン回転式圧縮機の給油装置
について、以下その動作を説明する。エンジンなどの駆
動源より動力伝達を受けて駆動軸５およびロータ２が第
２図において時計方向に回転すると、これに伴な１低圧
流体が吸入口９より作動室８内に流入する。ロータ２の
回転に伴ない圧縮された高圧流体は吐出口１０より吐出
弁１１を押し上げて高圧通路１３より高圧室１４に流入
し、スクリーン１６によって潤滑油を分離捕捉される。The operation of the vane rotary compressor oil supply system configured as described above will be described below. When the drive shaft 5 and rotor 2 rotate clockwise in FIG. 2 due to power transmission from a drive source such as an engine, low-pressure fluid flows into the working chamber 8 through the suction port 9. The high-pressure fluid compressed as the rotor 2 rotates pushes up the discharge valve 11 through the discharge port 10 and flows into the high-pressure chamber 14 through the high-pressure passage 13, where the lubricating oil is separated and captured by the screen 16.
高圧流体中より分離された潤滑油は高圧室１４下方に貯
えられ、差圧によって給油通路１６および通路１８から
ベーン底部空間１７へ供給されてベーン３の押圧に供さ
れる。The lubricating oil separated from the high-pressure fluid is stored below the high-pressure chamber 14, and is supplied to the vane bottom space 17 from the oil supply passage 16 and the passage 18 due to the differential pressure, and is used to press the vane 3.
しかしながら圧縮機が停止してからある時間が７・“−
ブ
経過して低圧側の流体の圧力と高圧側の流体の圧力とが
等しくなった場合に圧縮機を始動すると、圧縮機始動直
後の差圧が小さ−ため、上記従来の給油装置では特に圧
縮機始動時の回転数が低い場合にベーンの抑圧不足を生
じベーンがシリンダの内壁から遊離し再び衝突する周知
の不調現象や流体を圧縮しない圧縮不良現象が生ずると
いう欠点があり、まだ圧縮機運転中においても高低圧力
差が小さく十分な油量を確保できない場合にもベーンの
不調現象が生ずるという欠点があった。However, a certain period of time after the compressor stops is 7・“−
When the compressor is started after the pressure of the fluid on the low-pressure side becomes equal to the pressure of the fluid on the high-pressure side, the pressure difference immediately after starting the compressor is small. If the rotation speed at engine startup is low, the vane may not be sufficiently suppressed, causing the vane to separate from the inner wall of the cylinder and collide with it again, a well-known malfunction phenomenon or a compression failure phenomenon in which the fluid is not compressed. Among these, there is a drawback in that vane failure occurs even when the difference between high and low pressures is small and a sufficient amount of oil cannot be secured.
発明の目的
本発明は上記欠点に鑑み特に圧縮機の高低圧力差が無い
か小さい場合に低速回転で圧縮機を運転した場合でもベ
ーンの不調現象や圧縮不良現象を防止できかつ耐久性や
効率を損なわないベーン回転式圧縮機の給油装置を提供
するものである。Purpose of the Invention In view of the above-mentioned drawbacks, the present invention has been developed to prevent vane malfunction and compression failure even when the compressor is operated at low speed when there is no or small pressure difference between the compressor and the pressure difference between the high and low pressures, and to improve durability and efficiency. To provide a vane rotary compressor lubrication system that does not damage the vane rotary compressor.
発明の構成
本発明はベーン回転式圧縮機におけるベーン押圧のだめ
の潤滑油を高圧室の油溜り部からベーン底部空間へ供給
する給油装置として、通路断面積特開昭ＧＯ−１４５４
７８（３）
の犬なる第１通路と通路断面積の小なる第２通路とを各
々独立に有しさらに給油通路と第１通路とを連通遮断し
かつ少なくとも第１通路と給油通路とを遮断している場
合には第２通路と給油通路とを連通する弁体を設けたも
のである。Structure of the Invention The present invention is an oil supply device for supplying lubricating oil from a vane pressing reservoir in a vane rotary compressor to a vane bottom space from an oil reservoir in a high pressure chamber.
78(3), each having a first passage having a dog shape and a second passage having a small passage cross-sectional area independently, and further blocking communication between the refueling passage and the first passage, and at least blocking the first passage and the refueling passage. In this case, a valve body is provided to communicate the second passage and the oil supply passage.
この構成によって圧縮機の高低圧力差が無いか小さい場
合は前記第１及び第２通路または第１通路から、高低圧
力差が大きい場合は前記第２通路のみから潤滑油を供給
し、圧縮機の高低圧力差が無いか小さい場合に低速回転
で圧縮機を始動あるいは運転した場合でもベーンの不調
現象や圧縮不良現象を防止できるという特有の効果を有
する。With this configuration, lubricating oil is supplied from the first and second passages or the first passage when there is no or small pressure difference between the high and low pressures of the compressor, and from only the second passage when the difference between high and low pressures is large. It has the unique effect of preventing vane malfunction or poor compression even when the compressor is started or operated at low rotation speed when there is no or small difference in pressure between high and low pressures.
実施例の説明
以下本発明の一実施例について、図面を参照しながら説
明する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.
第３図〜第６図は本発明の第１の実施例におけるベーン
回転式圧縮機の給油装置を示すもので、同図に示す部品
のうち前記従来のベーン回転式圧縮機の給油装置と同一
の部品でかつ同一の作用効果を有するものは同一の符号
を記して説明を省略９弓
する。Figures 3 to 6 show a vane rotary compressor oil supply system according to the first embodiment of the present invention, and among the parts shown in the figures, the same parts as the conventional vane rotary compressor oil supply system are shown. Parts having the same functions and effects are designated by the same reference numerals, and the description thereof will be omitted.
同図において、２ｏは給油通路１６を横切って形成され
だ摺動室、２１は摺動室２ｏ内に摺動自在に配設された
弁体、２２および２３は各々独立して弁体２１に設けら
れた通路断面積の大なる第１通路および通路断面積の小
なる第２通路、２４は摺動室２０の両端を閉塞して弁体
の両端にそれぞれ第１摺動室２０ａ および第２摺動室
２０ｂ を形成する栓体、２５は第１摺動室２０ａ と
吸入口９とを連通して第１摺動室２０ａ に吸入口９よ
り低圧流体の圧力を導入する第１圧力導入路、２６は第
２摺動室２０ｂ と高圧室１４とを連通して第２摺動室
２０ｂ に高圧流体の圧力を導入する第２圧力導入路、
２７は第１摺動室２０ａ 内に設けられ弁体２１を第２
摺動室２Ｏｂ 側へ付勢しようとするバネである。In the figure, 2o is a sliding chamber formed across the oil supply passage 16, 21 is a valve body slidably disposed within the sliding chamber 2o, and 22 and 23 are each independently attached to the valve body 21. A first passage with a large cross-sectional area and a second passage with a small passage cross-sectional area are provided, and the first passage 24 closes both ends of the sliding chamber 20 to form a first sliding chamber 20a and a second passage at both ends of the valve body, respectively. A stopper 25 forming the sliding chamber 20b is a first pressure introduction path that communicates the first sliding chamber 20a with the suction port 9 and introduces the pressure of low-pressure fluid from the suction port 9 into the first sliding chamber 20a. , 26 is a second pressure introduction path that communicates the second sliding chamber 20b with the high pressure chamber 14 and introduces the pressure of high pressure fluid into the second sliding chamber 20b.
27 is provided in the first sliding chamber 20a and connects the valve body 21 to the second sliding chamber 20a.
This is a spring that tends to bias the sliding chamber 2Ob side.
以上のように構成されだベーン回転式圧縮機の給油装置
について以下その動作を説明する。The operation of the vane rotary compressor oil supply system constructed as described above will be described below.
圧縮機の運転中は、第１摺動室２Ｏａ 内には第１圧力
導入路２６により低圧流体が、第２摺動室１０ 。During operation of the compressor, low-pressure fluid is introduced into the first sliding chamber 2Oa through the first pressure introduction path 26 and into the second sliding chamber 10.
２Ｏｂ 内には第２圧力導入路２６により高圧流体がそ
れぞれ導入されているため、弁体２１の両端の圧力差が
バネ２７の付勢力に打ち勝って弁体２１は第１摺動室２
Ｏａ 側へ移動しており、弁体２１に設けられた第１通
路２２は給油通路１６と遮断されて、ベーン３の抑圧に
必要な潤滑油は通路断面積の小なる第２通路２３を通っ
て給油通路１６からベーン底部空間１７へ供給される。2Ob, high pressure fluid is introduced into the first sliding chamber 2 by the second pressure introduction path 26, so the pressure difference between both ends of the valve body 21 overcomes the biasing force of the spring 27, and the valve body 21 moves into the first sliding chamber 2.
Oa side, the first passage 22 provided in the valve body 21 is cut off from the oil supply passage 16, and the lubricating oil necessary for suppressing the vane 3 passes through the second passage 23, which has a small passage cross-sectional area. The oil is supplied from the oil supply passage 16 to the vane bottom space 17.
第２通路２３はこの場合実質的に給油量を制限する役目
を持つ通路であって、前記従来のベーン回転式圧縮機の
給油装置と実質的に同等である。In this case, the second passage 23 is a passage that serves to substantially limit the amount of oil supply, and is substantially equivalent to the oil supply system of the conventional vane rotary compressor.
一方、圧縮機が停止して弁体２１の両端の圧力差が徐々
に小さくなっていく場合には、圧力差がある一定の値以
下になると弁体２１はバネ２７によって第６図に示され
る状態すなわち第２摺動室２０ｂ 側へ付勢された状態
となり、この時弁体２１に設けられた通路断面積の大な
る第１通路２２は給油通路１６と連通する。この状態か
ら圧縮機を始動した場合、始動直後にはベーン底部空間
１７の容積増大によるわずかな圧力差によって高圧室１
１ 、−
１４よりベーン底部空間１７に潤滑油が供給されるので
あるが、高圧室１４とベーン底部空間１７とを連通ずる
第１通路２２の断面積が犬であるため、このわずかな差
圧によってもベーン抑圧に必要な潤滑油量が供給できる
のである。さらに運転を継続すると高圧室１４の圧力が
徐々に増大し吸入口９の圧力は低下するので弁体２１両
端の圧力差も徐々に増大し圧力差がある一定の値以上に
なると弁体２１はバネ２７の付勢力に打ち勝って弁体２
１を第１摺動室２Ｏａ 側へ移動させ、潤滑油は第２通
路２３からベーン底部空間１７へ供給されるのである。On the other hand, when the compressor is stopped and the pressure difference between both ends of the valve body 21 gradually decreases, when the pressure difference becomes less than a certain value, the valve body 21 is moved by the spring 27 as shown in FIG. In other words, the state is such that the second sliding chamber 20b is urged toward the side, and at this time, the first passage 22 provided in the valve body 21 and having a large passage cross-sectional area communicates with the oil supply passage 16. When the compressor is started in this state, immediately after the start, a slight pressure difference due to the increase in volume of the vane bottom space 17 causes the high pressure chamber to
Lubricating oil is supplied to the vane bottom space 17 from 1 and 14, but since the first passage 22 that communicates the high pressure chamber 14 and the vane bottom space 17 has a cross-sectional area of 100 mm, this slight pressure difference This also makes it possible to supply the amount of lubricating oil necessary for vane suppression. As the operation continues, the pressure in the high pressure chamber 14 gradually increases and the pressure in the suction port 9 decreases, so the pressure difference between both ends of the valve body 21 gradually increases, and when the pressure difference exceeds a certain value, the valve body 21 The valve body 2 overcomes the biasing force of the spring 27.
1 to the first sliding chamber 2Oa side, and lubricating oil is supplied from the second passage 23 to the vane bottom space 17.
以上のように本実施例によれば、ベーン回転式圧縮機に
おいてベーン底部空間と高圧室を連通ずる給油通路を横
切って摺動室と、との摺動室内に摺動自在に配設された
弁体と、弁体に各々独立して設けられた通路断面積の犬
なる第１通路および通路断面積の小なる第２通路と、摺
動室の両端を閉塞して弁体の両端に第１摺動室と第２摺
動室を形成する栓体と、第１摺動室と吸入口とを連通す
る第１圧力導入路と、第２摺動室と高圧室とを連通する
第２圧力導入路と、弁体を第２摺動室側へ付勢しようと
するバネとを設けることにより、圧縮機の始動時あるい
は運転時において高低圧力差が無いか小さい場合には通
路断面積の大なる第１通路からベーン抑圧に必要な潤滑
油を供給し、高低圧力差が大となって差圧により部分な
潤滑油を供給できる場合には通路断面積の小なる第２通
路から潤滑油量を制限してベーン底部空間に供給できる
ので、圧縮機の耐久性や効率を損なうことなくベーンの
不調現象や圧縮不良現象を防止できる。As described above, according to the present embodiment, in the vane rotary compressor, the sliding chamber is slidably disposed in the sliding chamber across the oil supply passage that communicates the vane bottom space and the high pressure chamber. A first passage with a small cross-sectional area and a second passage with a small cross-sectional area are provided independently in the valve body, and a second passage with a small cross-sectional area is provided at both ends of the valve body by closing both ends of the sliding chamber. A stopper that forms a first sliding chamber and a second sliding chamber, a first pressure introduction path that communicates the first sliding chamber and the suction port, and a second pressure introduction path that communicates the second sliding chamber and the high pressure chamber. By providing a pressure introduction passage and a spring that urges the valve body toward the second sliding chamber, the cross-sectional area of the passage can be reduced when there is no or small pressure difference between high and low pressures when starting or operating the compressor. The lubricating oil necessary for vane suppression is supplied from the large first passage, and when the difference in high and low pressure is large and a partial supply of lubricating oil is possible due to the differential pressure, the lubricating oil is supplied from the second passage whose cross-sectional area is small. Since the amount can be limited and supplied to the space at the bottom of the vane, it is possible to prevent vane malfunctions and poor compression phenomena without impairing the durability or efficiency of the compressor.
以下本発明の第２の実施例について、図面を参照しなが
ら説明する。A second embodiment of the present invention will be described below with reference to the drawings.
第７図〜第１０図は本発明の第２の実施例におけるベー
ン回転式圧縮機の給油装置を示すもので、同図において
前記第１の実施例を示す第３図〜第６図と同一の符号は
同一の部品を示すもので第１の実施例と異なるのは第２
導入通路２８が高圧側の作動室と第２摺動室２０ｂ と
を連通して設けられている点である。Figures 7 to 10 show an oil supply system for a vane rotary compressor according to a second embodiment of the present invention, and are the same as Figures 3 to 6 showing the first embodiment. The numerals indicate the same parts, and the second embodiment differs from the first embodiment.
The introduction passage 28 is provided to communicate the high pressure side working chamber and the second sliding chamber 20b.
１３、？ プ
この場合、圧縮機が停止すると、圧縮機の高圧室１４と
吸入口９とに圧力差が存在しても、第１圧力導入路２５
が開口する吸入口９と第２圧力導入路２８が開口する高
圧側の作動室８との圧力は等しくなるため弁体２１の両
端に作用する圧力は等しくなり弁体２１はバネ２７の付
勢力によって第１０図の状態すなわち第２摺動室２ｏｂ
側に押し付けられた状態となるが、この状態から始動し
た場合には、高圧通路１３の圧力に抗して吐出弁１１を
押し上げようとして第２圧力導入路２８が開口する高圧
側の作動室８内の圧力が瞬時に上昇するため、第２摺動
室２０ｂ 内の圧力も増大しバネ２７の付勢力に打ち勝
って弁体２１を第９図の状態すなわち第１摺動室２Ｏａ
側に押し付けた状態にするので、瞬時に潤滑油供給は
第２通路２３によって行なわれるため、この場合でも前
記第１の実施例とほぼ同様の作用効果を有することは明
らかである。13.? In this case, when the compressor stops, even if there is a pressure difference between the high pressure chamber 14 and the suction port 9 of the compressor, the first pressure introduction path 25
Since the pressures of the inlet 9, which is opened, and the high-pressure working chamber 8, which is opened by the second pressure introduction path 28, are equal, the pressures acting on both ends of the valve body 21 are equal, and the valve body 21 is moved by the biasing force of the spring 27. Accordingly, the state shown in FIG. 10, that is, the second sliding chamber 2ob
However, when starting from this state, the working chamber 8 on the high pressure side where the second pressure introduction passage 28 opens in an attempt to push up the discharge valve 11 against the pressure of the high pressure passage 13. As the pressure inside the second sliding chamber 20b increases instantaneously, the pressure inside the second sliding chamber 20b also increases, overcoming the biasing force of the spring 27 and moving the valve body 21 into the state shown in FIG. 9, that is, the first sliding chamber 2Oa.
Since the lubricant is pressed to the side, lubricating oil is instantaneously supplied through the second passage 23, so it is clear that this case also has substantially the same effect as the first embodiment.
なお、第１の実施例において第１圧力導入路２５は吸入
口９に開口させたが、低圧側の作動室８に１４ ・ ブ
開口させてもよいし、第２圧力導入路２６は高圧室１４
に開口させたが、高圧通路１３もしくは給油通路１６に
開口させてもよい。また圧力導入路２５．２６を上記の
部分と同等の圧力を有する圧縮機の各空間に開口させて
もよいことは勿論である。In the first embodiment, the first pressure introduction passage 25 was opened to the suction port 9, but it may be opened to the working chamber 8 on the low pressure side, and the second pressure introduction passage 26 may be opened to the high pressure chamber 8. 14
However, the high pressure passage 13 or the oil supply passage 16 may be opened. It goes without saying that the pressure introduction passages 25 and 26 may be opened to each space of the compressor having the same pressure as the above-mentioned portions.
まだ、第２の実施例において第１圧力導入路２５は吸入
口９に開口させたが、吸入側の作動室８に開口させても
よいし、第２圧力導入路２８は高圧側の作動室８に開口
させたが吐出口１０に開口させてもよい。まだ圧力導入
路２５．２８を上記の部分と同等の圧力を有する圧縮機
の各空間に開口させてもよいことは勿論である。In the second embodiment, the first pressure introduction path 25 is opened to the suction port 9, but it may be opened to the working chamber 8 on the suction side, and the second pressure introduction path 28 is opened to the working chamber 8 on the high pressure side. Although the discharge port 8 is opened, the discharge port 10 may be opened. Of course, the pressure introduction passages 25, 28 may be opened into the respective spaces of the compressor having the same pressure as the above-mentioned portions.
さらに、第２の実施例において第１圧力導入路２５を高
圧通路１３もしくは高圧室１４もしくは給油通路１６に
開口させ、第２圧力導入路２８は吐出口１０もしくは吐
出口１ｏ近傍の高圧側作動室８に開口させてもよい。ま
た圧力導入路２５゜２８を上記の部分と同等の圧力を有
する圧縮機の各空間に開口させてもよいことは勿論であ
る。Furthermore, in the second embodiment, the first pressure introduction passage 25 is opened to the high pressure passage 13, the high pressure chamber 14, or the oil supply passage 16, and the second pressure introduction passage 28 is opened to the discharge port 10 or the high pressure side working chamber near the discharge port 1o. 8 may be opened. It goes without saying that the pressure introduction passages 25 and 28 may be opened into each space of the compressor having the same pressure as the above-mentioned portions.
１５、 ゾ
また、第１および第２の実施例における第６図および第
１０図において第２通路２３は給油通路１６と遮断され
ているが連通させてもよい。またこの場合には第１通路
２２と第２通路２３との通路断面積の関係は逆でもよい
。15. Also, although the second passage 23 is cut off from the oil supply passage 16 in FIGS. 6 and 10 in the first and second embodiments, it may be communicated with the oil supply passage 16. Further, in this case, the relationship between the cross-sectional areas of the first passage 22 and the second passage 23 may be reversed.
発明の効果
以」二のように本発明は、ベーン回転式圧縮機における
ベーン抑圧のだめの潤滑油を高圧室の油溜り部からベー
ン底部空間へ供給する給油装置として、通路断面積の大
なる第１通路と通路断面積の小なる第２通路とを各々独
立に有し、さらに給油通路と第１通路とを連通遮断しか
つ少なくとも第１通路と給油通路とを遮断している場合
には第２通路と給油通路とを連通する弁体を設けて圧縮
機の高低圧力差が無いか小さい場合は第１及び第２通路
または第１通路から、高低圧力差が大きい場合は第２通
路のみから潤滑油を供給することによって、圧縮機の高
低圧力差が無いか小さい場合に低速回転で圧縮機を始動
あるいは運転した場合でも圧縮機の耐久性や効率を損な
うことなくベーン特開昭ＧＯ−１４５４７８（５）
の不調現象や圧縮不良現象を防止でき、その実用的効果
は犬なるものがある。Effects of the Invention As described in 2., the present invention provides a lubricating device for supplying lubricating oil from a vane suppression reservoir to a vane bottom space in a vane rotary compressor from an oil reservoir in a high pressure chamber to a vane bottom space. In the case where the first passage and the second passage having a small passage cross-sectional area are independently provided, and the communication between the oil supply passage and the first passage is cut off, and at least the first passage and the oil supply passage are cut off, A valve body is provided to communicate between the two passages and the oil supply passage, so that if there is no or small pressure difference between the high and low pressures of the compressor, the first and second passages or the first passage are used, and when the difference between high and low pressures is large, the second passage is used only. By supplying lubricating oil, even if the compressor is started or operated at low speed when there is no or small pressure difference between the high and low pressures of the compressor, the vane can be maintained without compromising the durability or efficiency of the compressor. (5) It is possible to prevent the phenomenon of malfunction and poor compression, and its practical effects are significant.
第１図は従来の給油装置を具備したベーン回転式圧縮機
の縦断面図、第２図は第１図のＡ−Ａ線による断面図、
第３図は本発明の第１の実施例における給油装置を具備
したベーン回転式圧縮機の縦断面図、第４図は第３図の
ｘ−Ｘ線による断面図、第６図、第６図は第３図のＹ−
Ｙ線による要部拡大断面図、第７図は本発明の第２の実
施例における給油装置を具備したベーン回転式圧縮機の
縦断面図、第８図は第７図のｘ’−ｘ’線による断面図
、第９図、第１０図は第７図のＹ’−Ｙ’線による要部
拡大断面図である。
１・・・・・・シリンダ、２・・・−・・ロータ、３・
・・・・ベーン、４・・・・・ベーンスロット、６・・
甲ＩＥ動軸、６・・・・前部側板、７・・−・・後部側
板、８・・・・作動室、９・・・・・吸入口、１０・・
・・・・吐出口、１１・・・・・・吐出弁、１２・・・
・・高圧ケース、１４・・・・・・高圧室、１６・・・
・・・給油通路、２ｏ・・・摺動室、２１・・川・弁体
、２２・・・・・１７ 、
第１通路、２３・・・・・第２通路、２５・・・・・・
第１圧力導入路、２６．２８・・・・・・第２圧力導入
路、２７・・・・・・バネ。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名第
１ 図
第 ２８ｉ！
＠ ３ 図
第 ５ 図
第 ４ 図
ｆＡｃ図
ｔＪＳｑ図
＠ ８ ｍ
寸
派 〜Fig. 1 is a longitudinal cross-sectional view of a vane rotary compressor equipped with a conventional oil supply device, Fig. 2 is a cross-sectional view taken along line A-A in Fig. 1,
FIG. 3 is a longitudinal cross-sectional view of a vane rotary compressor equipped with an oil supply device according to the first embodiment of the present invention, FIG. The figure is Y- in Figure 3.
FIG. 7 is a longitudinal sectional view of a vane rotary compressor equipped with an oil supply device according to a second embodiment of the present invention, and FIG. 8 is an enlarged cross-sectional view of main parts taken along the Y line. 9 and 10 are enlarged sectional views of main parts taken along the Y'-Y' line in FIG. 7. 1...Cylinder, 2...--Rotor, 3...
... Vane, 4 ... Vane slot, 6...
AIE moving shaft, 6... Front side plate, 7... Rear side plate, 8... Working chamber, 9... Suction port, 10...
...Discharge port, 11...Discharge valve, 12...
...High pressure case, 14... High pressure chamber, 16...
...Oil supply passage, 2o...Sliding chamber, 21...River/valve body, 22...17, 1st passage, 23...2nd passage, 25...・
First pressure introduction path, 26.28...Second pressure introduction path, 27...Spring. Name of agent: Patent attorney Toshio Nakao and 1 other person
1 Figure 28i! @ 3 Figure 5 Figure 4 Figure f Ac Figure t JSq Figure @ 8 m Dimension ~
Claims (4)
部に配設されその外周の一部がシリンダ内壁′ と微小
隙間を形成するロータと、このロータに設けられたベー
ンスロツト内に摺動自在に挿入された複数のベーンと、
前記ロータと一体的に形成され回転自在に軸支される駆
動軸と、前記シリンダの両端を閉塞して内部妃作動室を
形成する前部側板および後部側板と、前記ロータ外周と
シリンダ内壁が近接している部分をはさんで作動室に連
通ずる吸入通路および吐出通路と、この吐出通路に設け
られた吐出弁と、吐出通路に連通し圧縮された高圧流体
中の潤滑油を分離しかつその下方部分に油溜り部を含む
高圧室を有する高圧ケースと、この高圧室の油溜り部と
前記ベーンスロ、ントとを連通する給油通路とから成り
、通路断面積の大なる第１通路と通路断面積の小なる第
２通路とを各々独立に有しさらに前記給油通路と第１通
路とを連通遮断しかつ少なくとも第１通路と前記給油通
路とを遮断している場合には第２通路と前記給油通路と
を連通する弁体を設けだベーン回転式圧縮機の給油装置
。(1) A cylinder having a cylindrical inner wall, a rotor disposed inside the cylinder and having a part of its outer periphery forming a minute gap with the inner wall of the cylinder, and a rotor that can freely slide into a vane slot provided in the rotor. multiple vanes inserted;
A drive shaft formed integrally with the rotor and rotatably supported; a front side plate and a rear side plate that close both ends of the cylinder to form an internal working chamber; and an outer periphery of the rotor and an inner wall of the cylinder are close to each other. The suction passage and the discharge passage that communicate with the working chamber across the parts that are connected to each other, the discharge valve provided in this discharge passage, and the lubricating oil in the compressed high-pressure fluid that communicates with the discharge passage are separated. It consists of a high-pressure case having a high-pressure chamber including an oil reservoir in its lower part, and an oil supply passage that communicates the oil reservoir of the high-pressure chamber with the vane slot. and second passages each having a small area independently, and furthermore, when the communication between the oil supply passage and the first passage is cut off, and at least the first passage and the oil supply passage are cut off, the second passage and the A vane rotary compressor oil supply system equipped with a valve body that communicates with the oil supply passage.
その内部に前記弁体が摺動自在に配設される摺動室と、
前記弁体の一端の第１摺動室に開口する第１圧力導入路
と、少なくとも圧縮機運転中は第１圧力導入路より高い
圧力を有しかつ前記弁体の他端の第２摺動室に開口する
第２圧力導入路と、弁体を第２圧力導入路の連通する第
２摺動室側へ付勢しようとするバネとを設け、弁体両端
の圧力差が無いか小さい場合には前記バネ力により給油
通路と少なくとも第１通路とを連通させるように弁体を
第２摺動室側へ移動させ、弁体両端の圧力差が前記バネ
力に打ち勝った場合には弁体を第１摺動室側へ移動させ
給油通路と前記第１通路とを遮断して前記第２通路との
み連通するようにしだ前記特許請求の範囲第１項に記載
のベーン回転式３７、 圧縮機の給油装置。(2) a sliding chamber formed in the middle of the oil supply passage across the oil supply passage and in which the valve body is slidably disposed;
a first pressure introduction path that opens into a first sliding chamber at one end of the valve body; and a second pressure introduction path that has a higher pressure than the first pressure introduction path at least during compressor operation and that opens into a first sliding chamber at the other end of the valve body. When a second pressure introduction path that opens into the chamber and a spring that biases the valve body toward the second sliding chamber with which the second pressure introduction path communicates are provided, and there is no or small pressure difference between the two ends of the valve body. The spring force moves the valve body toward the second sliding chamber so that the oil supply passage and at least the first passage communicate with each other, and when the pressure difference between both ends of the valve body overcomes the spring force, the valve body The vane rotary type 37 according to claim 1 is moved to the first sliding chamber side to block the oil supply passage and the first passage so as to communicate only with the second passage. Aircraft refueling system.
通路と弁体の一端の摺動室とを連通し、第２圧力導入路
は、吐出弁以後の吐出通路もしくは高圧室もしくは給油
通路と弁体の他端の摺動室とを連通する前記特許請求の
範囲第２項に記載のベーン回転式圧縮機の給油装置。(3) The first pressure introduction path communicates the low-pressure side working chamber or suction passage with the sliding chamber at one end of the valve body, and the second pressure introduction path communicates with the discharge passage after the discharge valve, the high-pressure chamber, or the oil supply. The oil supply device for a vane rotary compressor according to claim 2, which communicates the passage with the sliding chamber at the other end of the valve body.
通路と弁体の一端の摺動室とを連通し、第２圧力導入路
は、吐出弁以前の吐出通路もしくは高圧側の作動室と弁
体の他端の摺動室とを連通ずる前記特許請求の範囲第２
項に記載のベーン回転式圧縮機の給油装置。 （＠ 第１圧力導入路は、吐出弁以後の吐出通路もしく
は高圧室もしくは給油通路と弁体の一端の摺動室とを連
通し、第２圧力導入路は、吐出弁以前の吐出通路もしく
は吐出通路近傍の高圧側作動室と弁体の他端の摺動室と
を連通する前記特許請求の範囲第２項に記載のベーン回
転式圧縮機の給油装置。 Ｔ！ｆ開昭ＧＯ−１４５４７８（２）(4) The first pressure introduction passage communicates the working chamber or suction passage on the low pressure side with the sliding chamber at one end of the valve body, and the second pressure introduction passage communicates the working chamber or suction passage on the low pressure side with the sliding chamber at one end of the valve body, and the second pressure introduction passage communicates with the working chamber or suction passage on the low pressure side, and the second pressure introduction passage communicates with the working chamber or the suction passage on the low pressure side. Claim 2, which communicates the chamber with the sliding chamber at the other end of the valve body.
Lubricating device for the vane rotary compressor described in . (@ The first pressure introduction path communicates the discharge passage after the discharge valve or the high pressure chamber or the oil supply passage with the sliding chamber at one end of the valve body, and the second pressure introduction passage communicates with the discharge passage or the high pressure chamber or the oil supply passage after the discharge valve and the sliding chamber at one end of the valve body. The oil supply device for a vane rotary compressor according to claim 2, which communicates the high-pressure side working chamber near the passage with the sliding chamber at the other end of the valve body. 2)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25136483A JPS60145478A (en) | 1983-12-29 | 1983-12-29 | Oil feeding apparatus for rotary vane type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25136483A JPS60145478A (en) | 1983-12-29 | 1983-12-29 | Oil feeding apparatus for rotary vane type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60145478A true JPS60145478A (en) | 1985-07-31 |
Family
ID=17221725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25136483A Pending JPS60145478A (en) | 1983-12-29 | 1983-12-29 | Oil feeding apparatus for rotary vane type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60145478A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0643286U (en) * | 1992-11-20 | 1994-06-07 | カルソニック株式会社 | Rotary compressor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4421172Y1 (en) * | 1965-01-02 | 1969-09-08 |
-
1983
- 1983-12-29 JP JP25136483A patent/JPS60145478A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4421172Y1 (en) * | 1965-01-02 | 1969-09-08 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0643286U (en) * | 1992-11-20 | 1994-06-07 | カルソニック株式会社 | Rotary compressor |
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