JP2574827B2 - Movable airfoil rotary compressor - Google Patents
Movable airfoil rotary compressorInfo
- Publication number
- JP2574827B2 JP2574827B2 JP62321290A JP32129087A JP2574827B2 JP 2574827 B2 JP2574827 B2 JP 2574827B2 JP 62321290 A JP62321290 A JP 62321290A JP 32129087 A JP32129087 A JP 32129087A JP 2574827 B2 JP2574827 B2 JP 2574827B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- slider
- vane
- vanes
- rotor
- 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
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
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/001—Radial sealings for working fluid
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は可動翼形回転式圧縮機に係り、特に自動車用
圧縮機に好適な可動翼形回転式圧縮機に関する。Description: TECHNICAL FIELD The present invention relates to a movable airfoil rotary compressor, and more particularly to a movable airfoil rotary compressor suitable for a compressor for an automobile.
従来のロータリベーン形圧縮機は、特開昭53−106914
号公報に記載のように、シリンダ内でロータを回転さ
せ、ロータの外周面とシリンダ内周面との間に形成され
る空間の容積を、ロータと共に回転するベーンと、その
ベーン先端に摺動自在に係合したチツプシールによって
増大，減少させてこの空間の容積変化に伴つて流体を圧
送する構成となつていた。A conventional rotary vane type compressor is disclosed in Japanese Patent Application Laid-Open No. 53-106914.
As described in the publication, the rotor is rotated in the cylinder, and the volume of the space formed between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder is slid by the vane rotating with the rotor and the vane tip. Fluid is pumped in accordance with a change in the volume of the space by increasing or decreasing the size by means of a chip seal freely engaged.
また、特開昭55−43211号公報にはベーンを収容する
各溝の底部に流体の過圧縮防止用通孔を開口したものが
記載されている。Further, Japanese Patent Application Laid-Open No. 55-43211 discloses a structure in which a through hole for preventing excessive compression of fluid is opened at the bottom of each groove for accommodating a vane.
上記従来技術の特開昭53−106914号は、ベーン先端と
シリンダ内壁面との間から流体が逆流しないようにする
ため、ベーンの背後及び副ベーンの背後に油圧や圧縮ガ
スを作用させ、特に副ベーンの背後には圧縮行程では高
圧、吸気行程では低圧によつて、副ベーン先端をシリン
ダ内壁面に押圧している。このため、高圧押圧による機
械的損失が大きく、ベーン・シリンダの摺動摩耗片が吐
出流体中に排出されて流体配管及びその配管に付設され
るバルブの目詰り等が生じ、エアコン機能を低下等の二
次的な不具合を引き起す。また吸気行程では副ベーンと
シリンダ内壁面との押圧が減少し、特にロータ低回転域
では副ベーンとシリンダ内壁面とのシール性が低下して
逆流が生じ、漏れ損失が大きくなる等の問題があつた。Japanese Patent Application Laid-Open No. 53-106914 discloses a technique of applying hydraulic pressure or compressed gas behind a vane and behind a sub-vane in order to prevent a fluid from flowing back from between the tip of the vane and the inner wall surface of the cylinder. The tip of the sub-vane is pressed against the inner wall of the cylinder behind the sub-vane by a high pressure in the compression stroke and a low pressure in the intake stroke. For this reason, the mechanical loss due to the high pressure is large, and the sliding wear pieces of the vane and cylinder are discharged into the discharged fluid, causing clogging of the fluid piping and valves attached to the piping, thereby deteriorating the air conditioner function. Causes secondary malfunctions. Also, in the intake stroke, the pressure between the sub-vane and the inner wall surface of the cylinder is reduced, and especially in the low rotation speed region of the rotor, the sealing performance between the sub-vane and the inner wall surface of the cylinder is reduced, and a backflow occurs, resulting in a large leakage loss. Atsuta.
他方特開昭55−43211号によれば、ベーンそのものを
シリンダ内壁面に押圧する構造になつているため、大き
な圧力が必要となり不利な構造である。On the other hand, according to Japanese Patent Application Laid-Open No. 55-43211, since the vane itself is pressed against the inner wall surface of the cylinder, a large pressure is required, which is disadvantageous.
本発明の目的は、ベーン先端のシール性を向上させつ
つ摩擦損失を低減させて機械効率の高い可動翼形回転式
圧縮機を提供するにある。An object of the present invention is to provide a movable airfoil rotary compressor having high mechanical efficiency by reducing frictional loss while improving the sealing performance of the vane tip.
上記目的は、シリンダ内で回転するロータと共に回転
し、かつ半径方向に進退運動しながらシリンダ内壁面に
沿つて移動する一対のベーンと、該一対のベーンを連結
し中央部にスライド溝を設け、このスライダ溝内にはス
ライダを有し、スライダが前記ロータに対して偏心した
中心で回転する回転式圧縮機にして、かつ前記ベーン先
端に形成した摺動溝にチツプシールを摺動可能に嵌入
し、該チツプシールの押圧力を高圧を導入して増圧する
ことによつて達成される。The object is to rotate with the rotor rotating in the cylinder, and a pair of vanes moving along the cylinder inner wall while moving forward and backward in the radial direction, and provide a slide groove in the center by connecting the pair of vanes, A slider is provided in the slider groove, the slider is a rotary compressor which rotates at a center eccentric with respect to the rotor, and a chip seal is slidably fitted in a slide groove formed at the tip of the vane. This is achieved by increasing the pressing force of the tip seal by introducing a high pressure.
チツプシール12の押圧力は、一対のベーン6a,6bの先
端部圧力を連通する連絡孔14によつて、吸気行程及び圧
縮行程でのシールバランスされることによつて、摩擦損
失が小さく、機械効率の高い回転式圧縮機となる。The pressing force of the tip seal 12 is reduced by friction loss due to seal balance in the intake stroke and the compression stroke by the communication hole 14 that communicates the pressure at the tip of the pair of vanes 6a, 6b. High-speed rotary compressor.
以下本発明の実施例を図面に基づき説明する。第１図
乃至第６図に示すように本発明における回転式圧縮機
は、内壁面が円筒状に形成されたシリンダ１およびこの
シリンダ１の両端閉塞するサイドプレート2,3とからな
るケーシング４と、前記シリンダ内で回転する中空状の
ロータ５と、このロータと共に回転し、かつ胴体部６を
前記中空部に配置すると共に半径方向に進退自在な少な
くとも一対のアルミニユーム材からなるベーン6a,6bを
備えている。Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 1 to 6, the rotary compressor according to the present invention includes a casing 4 comprising a cylinder 1 having an inner wall formed in a cylindrical shape and side plates 2 and 3 closing both ends of the cylinder 1. A hollow rotor 5 rotating in the cylinder, and vanes 6a and 6b made of at least one pair of aluminum materials rotating together with the rotor and having the body portion 6 disposed in the hollow portion and capable of moving back and forth in the radial direction. Have.
尚、5aはロータの入力軸となるシヤフト部分、5bはロ
ータ５部に設けられたベーン溝、７はフロントカバー、
8a,8b,8cはロータ５の外周面とシリンダ１の内周面との
間に形成される圧縮室、９は吐出弁である。5a is a shaft portion serving as an input shaft of the rotor, 5b is a vane groove provided on the rotor 5, 7 is a front cover,
8a, 8b and 8c are compression chambers formed between the outer peripheral surface of the rotor 5 and the inner peripheral surface of the cylinder 1, and 9 is a discharge valve.
前記一対のベーン6a,6bは胴体部６を介して連結され
ていると共に、該胴体部６の中央部にベーンの方向と直
角方向にスライド溝10を設け、このスライド溝10内には
焼結金属からなるスライダ11が配置されている。そし
て、スライダ11はロータ５に対して偏心した位置に配置
され、かつその位置で回転するように形成されると共
に、ベーン6a,6bの進退運動と共にスライド溝10内を摺
動する。そしてロータ５を片側に配置した軸受11a,11b
で後記するように支持され、スライダ11の回転を支持す
るスライダ軸12を前記サイドプレート３に固定配置して
いる。このようにして一対のベーン6a,6bは連結され、
その連結されたベーンの中央部である胴体部６にはスラ
イド溝10が設けられ、このスライド溝10内にスライダ11
が配置されている。そしてこのスライダ11はロータ５に
対して偏心した位置に配置され、かつその位置で回転す
るように形成されると共に、ベーン６はそのスライド溝
10を介してスライダ11と摺動し径方向に進退運動する。The pair of vanes 6a and 6b are connected to each other through the body 6, and a slide groove 10 is provided in the center of the body 6 in a direction perpendicular to the direction of the vane. A slider 11 made of metal is arranged. The slider 11 is disposed at a position eccentric with respect to the rotor 5 and is formed so as to rotate at that position, and slides in the slide groove 10 along with the movement of the vanes 6a and 6b. And bearings 11a and 11b in which the rotor 5 is arranged on one side
The slider shaft 12 which is supported as described later and supports the rotation of the slider 11 is fixed to the side plate 3. In this way, the pair of vanes 6a and 6b are connected,
A slide groove 10 is provided in the body 6 which is the center of the connected vane, and a slider 11 is provided in the slide groove 10.
Is arranged. The slider 11 is arranged at a position eccentric with respect to the rotor 5 and is formed so as to rotate at that position.
The slider slides with the slider 11 via 10 and moves forward and backward in the radial direction.
すなわちロータ５の外周の18が対向した位置に一対の
ベーン溝5bが設けられており、シヤフト部分5aはロータ
５の一方側のみに形成される。ロータ５の他の端面から
ロータ５内部にかけて大きな前記中空部が設けられてお
り、ロータ５のシヤフト部分5aはサイドプレート２を挾
んでフロントカバー７に設けられた２ケ所の軸受11a,11
bで支持される。サイドプレート２にシリンダ１および
サイドプレート３が軸方向に重ねられて前記ロータ５の
外周との間に圧縮室が形成されるが、この圧縮室はロー
タ５のベーン溝5bを貫通して組込まれた一対のベーン6
a,6bにより、３つの圧縮室8a,8b,8cに細分される。前記
ベーン6a,6bはその先端部に摺動部材である鋳鉄製のチ
ツプシール12が組込んでありシリンダ１の内壁面との間
の微小隙間をシールしている。That is, a pair of vane grooves 5b is provided at a position where the outer periphery 18 of the rotor 5 faces, and the shaft portion 5a is formed only on one side of the rotor 5. The large hollow portion is provided from the other end face of the rotor 5 to the inside of the rotor 5, and a shaft portion 5 a of the rotor 5 is provided at two bearings 11 a, 11 provided on the front cover 7 with the side plate 2 interposed therebetween.
Supported by b. The cylinder 1 and the side plate 3 are axially overlapped on the side plate 2 to form a compression chamber between the side plate 2 and the outer periphery of the rotor 5. The compression chamber is inserted through the vane groove 5 b of the rotor 5. A pair of vanes 6
By a and 6b, it is subdivided into three compression chambers 8a, 8b and 8c. The vanes 6a and 6b incorporate a tip seal 12 made of cast iron, which is a sliding member, at the tip thereof to seal a minute gap between the vanes 6a and 6b and the inner wall surface of the cylinder 1.
上記連結された一対のベーン6a,6bの中央部には、ロ
ータ５のベーン溝5bとは直角方向の円筒状のスライド溝
10が形成される。スライダ11はその摺動部10aがスライ
ド溝10内に組み込まれ、円筒軸方向に相対的に往復運動
できるように構成されている。At the center of the pair of connected vanes 6a and 6b, a cylindrical slide groove perpendicular to the vane groove 5b of the rotor 5 is provided.
10 is formed. The slider 11 has a sliding portion 10a incorporated in the slide groove 10 and is configured to be able to reciprocate relatively in the cylindrical axis direction.
スライダ11に係合するスライダ軸13はロータ５のシヤ
フト部分5aと平行で、かつ偏心した位置に支持されてい
る。A slider shaft 13 that engages with the slider 11 is supported at an eccentric position parallel to the shaft portion 5a of the rotor 5.
このようにすることにより回転式圧縮機は第３図にも
示されているように動作するようになる。例えばロータ
５のシヤフト部がＰ点回りを回転するとそのベーン溝56
中に組込まれたベーン6a,6bも一緒に回転するが、ベー
ン6a,6bはまたＱ点回りに回転するスライダ11によつて
拘束されているので、ベーン6a,6bの垂直２等分線は必
らずＱ点を通る。その結果、図中矢印表示の（ａ）から
（ａ）のように、ベーン6a,6bはロータ５の半回転の間
にベーン溝5b内の往復運動の中の片道（径路）を移動す
る。残る半回転の間に図中矢印表示の（ａ）が（ａ）と
全く同様に残りの復路運動を行ない、ロータ５の１回転
でベーン溝5b内を１回往復運動する。この場合にベーン
6a,6bの先端部で描く軌跡Ｒは第７図から解るように真
円ではなく特殊なカーブとなるが、シリンダ１の円面形
状をこの軌跡Ｒの形状に合わせて加工してやれば、ロー
タ5,シリンダ1,ベーン6a,6bおよびサイドプレート2,3に
よりロータ５の回転に伴い容積の増減を繰り返すための
圧縮室8a,8b,8cを形成し、容積形圧縮機として働らかせ
ることができる。In this way, the rotary compressor operates as shown in FIG. For example, when the shaft portion of the rotor 5 rotates around point P, the vane groove 56
The vanes 6a, 6b incorporated therein rotate together, but since the vanes 6a, 6b are also constrained by the slider 11 rotating about point Q, the vertical bisector of the vanes 6a, 6b is You must pass point Q. As a result, as shown by arrows (a) to (a) in the figure, the vanes 6a, 6b move one way (path) in the reciprocating motion in the vane groove 5b during the half rotation of the rotor 5. During the remaining half-turn, (a) indicated by an arrow in the figure performs the rest of the backward movement just like (a), and the rotor 5 makes one reciprocation in the vane groove 5b by one rotation. Vane in this case
The trajectory R drawn at the tips of 6a and 6b is not a perfect circle but a special curve, as can be seen from FIG. , Cylinders 1, vanes 6a, 6b and side plates 2, 3 form compression chambers 8a, 8b, 8c for repeatedly increasing and decreasing the volume as the rotor 5 rotates, and can function as a positive displacement compressor. .
さらに本発明では、組立性，信頼性向上の面でベーン
6a,6bの先端部が上記軌跡Ｒより内側にあるように、そ
の全長を短かくし、シリンダ１の内壁面に干渉しないよ
うにすると共に、チツプシール12によつて圧縮ガスの逆
流による漏れ損失を防ぐようにしてある。このチツプシ
ール12にはシリンダ1,ロータ５及びベーン6a,6bに囲ま
れた圧縮ガスが摺動溝14bの底部からの押圧がかかる。Further, in the present invention, the vane is improved in terms of assemblability and reliability.
The total length of the cylinders 6a and 6b is shortened so that the distal ends of the cylinders 6a and 6b are located inside the locus R so as not to interfere with the inner wall surface of the cylinder 1, and the tip seal 12 prevents leakage loss due to backflow of the compressed gas. It is like that. Compressed gas surrounded by the cylinder 1, the rotor 5, and the vanes 6a, 6b is applied to the tip seal 12 from the bottom of the sliding groove 14b.
すなわち、第４図〜第７図に示す如く、ベーン6a,6b
には、先端部のチツプシール12が嵌入できるようにした
摺動溝14bの底部からスライダ溝10の内面まで貫通した
連絡孔14aを形成してある。このスライダ溝10に対し
て、スライダ軸13と穴10bとを嵌合して摺動するスライ
ダ11は、その摺動面部10aに貫通した孔16aと長溝16bと
で形成する開口孔16を有し、任意の吸気点から吐出口近
傍までの区間においてチツプシール12の押圧を連通断続
によつて制御できる。その連通断続は第６図に示す開口
孔16の長溝16bの寸法、l1,l2に支配されており、第７
図，第８図に示すとおり、ロータ５の回転中心Ｐとオフ
セツトしたスライダ軸12の中心間Ｋと連通開始角θ１及
び終了角θ２によつて一義的に決められる。That is, as shown in FIGS. 4 to 7, vanes 6a, 6b
A communication hole 14a penetrating from the bottom of the slide groove 14b, into which the tip seal 12 at the tip can be fitted, to the inner surface of the slider groove 10 is formed. The slider 11 that slides by fitting the slider shaft 13 and the hole 10b into the slider groove 10 has an opening 16 formed by a hole 16a penetrating the sliding surface portion 10a and a long groove 16b. In the section from an arbitrary intake point to the vicinity of the discharge port, the pressing of the tip seal 12 can be controlled by intermittent communication. The intermittent communication is governed by the dimensions l 1 and l 2 of the long groove 16b of the opening 16 shown in FIG.
FIG, as shown in FIG. 8, uniformly decided Te rotation center P and offset the center between K and the communication start angle theta 1 and end angle theta 2 Niyotsu slider shaft 12 of the rotor 5.
ここでｈはベーンを貫通する連通孔14の穴径である。 Here, h is the hole diameter of the communication hole 14 penetrating the vane.
第７図のようにベーン6a,6bの回転移動に伴つて圧縮
室の圧力が上昇するものであり、吸気行程では低圧にな
り、シール不足を招き、更に吐出弁９付近では最大圧に
なり過剰な押圧になることがあり、そのために摩擦力の
増大になることがわかる。そこで、180゜の位相差にあ
る一対のベーン6a,6bの先端部圧力を連通する連絡孔14
によつてチツプシール12の押圧を制御し、摩擦損失が小
さく、機械効率及び耐久性の向上を可能とした回転式圧
縮機を得ることができる。As shown in FIG. 7, the pressure in the compression chamber increases as the vanes 6a and 6b rotate, and the pressure in the compression chamber becomes low during the intake stroke, causing insufficient sealing. It can be seen that there is a case where the pressing force is increased, which results in an increase in the frictional force. Therefore, the communication hole 14 for communicating the pressure at the tip of the pair of vanes 6a and 6b having a phase difference of 180 ° is provided.
Accordingly, it is possible to obtain a rotary compressor that controls the pressing of the chip seal 12, has a small friction loss, and can improve mechanical efficiency and durability.
従つて、本実施例によれば、ベーン6a,6bをシリンダ
１内壁面と非接触にすると共にチツプシール12の押圧を
連絡孔14と開口孔16の連通によつて制御できるので、摩
擦損失が小さく機械効率の高い、耐久性にすぐれ、かつ
吸気行程にあるチツプシール12へ高圧を導くことができ
るので圧縮ガスの漏れ損失を小なくできる回転式圧縮機
を得ることができる。Therefore, according to the present embodiment, the vanes 6a and 6b are kept out of contact with the inner wall surface of the cylinder 1, and the pressing of the tip seal 12 can be controlled by the communication between the communication hole 14 and the opening hole 16, so that the friction loss is small. Since high pressure can be introduced to the tip seal 12 in the intake stroke with high mechanical efficiency and excellent durability, it is possible to obtain a rotary compressor capable of reducing the leakage loss of the compressed gas.
尚、前記実施例で連絡孔14aをチツプシール12の下面
に当る際の形状は円形で図示しているが、チツプシール
下面に広く均等に当るのがより好ましく安定したシール
効果が期待できる。In the above-described embodiment, the shape when the communication hole 14a hits the lower surface of the chip seal 12 is shown as a circle. However, it is more preferable that the contact hole 14a hits the lower surface of the chip seal widely and evenly, and a stable sealing effect can be expected.
上述のように本発明は、摺動摩擦損失と、吸気行程に
おける逆流による漏れ損失が小さく機械効率の向上及び
耐久性を高めることを可能とした回転式圧縮機を得るこ
とができる。INDUSTRIAL APPLICABILITY As described above, the present invention can provide a rotary compressor that has small sliding friction loss and leakage loss due to backflow in the intake stroke and can improve mechanical efficiency and increase durability.
第１図は本発明回転式圧縮機の実施例を示すもので、第
２図のＩ−Ｉ断面図、第２図は同縦断正面図、第３図は
同圧縮機の動作サイクル説明図、第４図は第１図におけ
る圧縮機のベーンとスライダの組斜視図、第５図はスラ
イダの斜視図、第６図は第５図のＡ矢視平面図、第７図
は第１図の作動状態を示す断面図、第８図（Ａ）（Ｂ）
はロータの回転角に対するスライダの変位および圧縮圧
力の相関図である。 １……シリンダ、2,3……サイドプレート、４……ケー
シング、５……ロータ、6a,6b……ベーン、10……スラ
イド溝、11……スライダ、12……チツプシール、14……
連絡手段である連絡孔、16……連絡手段である開口孔。FIG. 1 shows an embodiment of the rotary compressor of the present invention. FIG. 2 is a sectional view taken along the line II of FIG. 2, FIG. 2 is a vertical sectional front view, FIG. FIG. 4 is a perspective view of a combination of a vane and a slider of the compressor in FIG. 1, FIG. 5 is a perspective view of the slider, FIG. 6 is a plan view of FIG. Sectional view showing operating state, FIGS. 8 (A) and (B)
FIG. 4 is a correlation diagram of the displacement of the slider and the compression pressure with respect to the rotation angle of the rotor. 1 ... Cylinder, 2,3 ... Side plate, 4 ... Casing, 5 ... Rotor, 6a, 6b ... Vane, 10 ... Slide groove, 11 ... Slider, 12 ... Chip seal, 14 ...
Communication hole as communication means, 16 ... Opening hole as communication means.
Claims (1)
と、 このシリンダの両端を閉口するサイドプレートとからな
るケーシング、 B.前記シリンダ内で回転する中空の回転ロータであっ
て、このシリンダの中心に対して偏心した位置に回転中
心を有する回転ロータと、 C.この回転ロータと共に回転し、かつこの回転ロータに
対して半径方向に、かつ相対的に進退運動する機械的に
連結された少なくとも一対のベーン、 D.前記一対のベーンの中央に形成した長溝に滑合し、こ
のベーンの進退方向に対して直角方向にスライド可能な
スライダー、 E.このスライダーを前記シリンダーの中心で回転支持す
る軸受機構、 とを有する可動翼形回転式圧縮機において、 F.前記ベーンの先端に取り付けたチップシール、 G.前記ベーンの長溝に一端が開口し、他端が前記チップ
シールの背面に開口する圧力導入孔、 H.前記スライダーを貫通し、前記スライダが所定の位置
にスライドしたとき前記ベーンに設けた前記圧力導入孔
に所定の圧力を導く一対の貫通孔、 を設けたことを特徴とする可動翼形回転式圧縮機。1. A casing comprising a cylinder whose inner peripheral surface is formed in a cylindrical shape, and a side plate closing both ends of the cylinder; B. a hollow rotating rotor rotating in the cylinder, A rotating rotor having a center of rotation at a position eccentric to the center of the cylinder; C. mechanically rotating with the rotating rotor and moving forward and backward relative to the rotating rotor in a radial direction and relatively. At least one pair of vanes, D. a slider that slides in a long groove formed in the center of the pair of vanes and is slidable in a direction perpendicular to the direction in which the vanes advance and retreat, and E. the slider at the center of the cylinder. A movable airfoil rotary compressor having a bearing mechanism that supports rotation; and F. a tip seal attached to the tip of the vane; G. one end of which is open in a long groove of the vane; A pressure introducing hole having the other end opened to the back of the tip seal; H. a pair of holes that penetrate the slider and guide a predetermined pressure to the pressure introducing hole provided in the vane when the slider slides to a predetermined position; A movable airfoil rotary compressor having a through hole.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62321290A JP2574827B2 (en) | 1987-12-21 | 1987-12-21 | Movable airfoil rotary compressor |
| KR1019880014466A KR890008458A (en) | 1987-11-16 | 1988-11-04 | Rotary vane compressor |
| US07/271,891 US4925378A (en) | 1987-11-16 | 1988-11-16 | Rotary vane compressor with valve controlled pressure biased sealing means |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62321290A JP2574827B2 (en) | 1987-12-21 | 1987-12-21 | Movable airfoil rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01163487A JPH01163487A (en) | 1989-06-27 |
| JP2574827B2 true JP2574827B2 (en) | 1997-01-22 |
Family
ID=18130916
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62321290A Expired - Lifetime JP2574827B2 (en) | 1987-11-16 | 1987-12-21 | Movable airfoil rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2574827B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6537001B1 (en) * | 2018-02-16 | 2019-07-03 | 好包 生武 | Lubrication system for reciprocating part of vane for vane engine. |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5838394A (en) * | 1981-08-31 | 1983-03-05 | Toyoda Autom Loom Works Ltd | Vane compressor |
-
1987
- 1987-12-21 JP JP62321290A patent/JP2574827B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01163487A (en) | 1989-06-27 |
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