JPS5847195A - Oil feeding structure for movable-vane type rotary compressor - Google Patents
Oil feeding structure for movable-vane type rotary compressorInfo
- Publication number
- JPS5847195A JPS5847195A JP14390381A JP14390381A JPS5847195A JP S5847195 A JPS5847195 A JP S5847195A JP 14390381 A JP14390381 A JP 14390381A JP 14390381 A JP14390381 A JP 14390381A JP S5847195 A JPS5847195 A JP S5847195A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- oil
- oil supply
- tangential
- cam ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、カーニアコンディショナに使用される可動翼
形回転式圧縮機に係り、高速回転領域における吐出温度
の異常上昇を抑制するために好適な潤滑給油通路を摺動
部材に配設したことを特徴とする可動翼形回転式圧縮機
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a movable vane type rotary compressor used in a carnier conditioner. The present invention relates to a movable vane type rotary compressor characterized in that it is disposed on a moving member.
一般的に、可動翼形回転式圧縮機の軸受構造は、ロータ
とフロント側及びリア側プレートの面接触を避けるため
に、ロータの両端面とフロント側及びリア側プレート間
にスラストニードル軸受を介在させて、ロータのスラス
ト方向の位置決めを行う一方、冷媒圧縮作用に帰因する
ラジアル力を支持するため、フロント側及びリア側プレ
ートにう。In general, the bearing structure of a movable vane rotary compressor uses thrust needle bearings between both end faces of the rotor and the front and rear plates to avoid surface contact between the rotor and the front and rear plates. In order to position the rotor in the thrust direction, and to support the radial force resulting from the refrigerant compression action, the front and rear plates are mounted.
シアルニードル軸受を配設している。Equipped with a shear needle bearing.
このような可動翼形回転式圧縮機の、従来問題となって
いる点の一つは、高速回転領域(圧縮機回転数で600
Orpm以上)において、過圧縮熱及びベーンの摺動
摩擦熱や内部漏洩による再圧縮熱等によって条件によっ
ては、吐出温度が異常に上昇(150’CC以上上て、
各摺動部材に熱変形を生じさせ、ロータ外周及びロータ
の両側端面において、焼付焼損を発生させる現象があり
、耐久性を著しく減少させる欠点があった。One of the conventional problems with such movable vane rotary compressors is that they operate in the high-speed rotation region (compressor rotation speed of 600 rpm).
Orpm), the discharge temperature may rise abnormally (over 150'CC) due to overcompression heat, vane sliding friction heat, recompression heat due to internal leakage, etc.
This method causes thermal deformation in each sliding member and causes seizure and burnout on the outer periphery of the rotor and both end surfaces of the rotor, which has the disadvantage of significantly reducing durability.
本発明の目的は、前記従来の欠点を除去するためになさ
れたもので、高速回転領域における吐出温度の異常上昇
を防止し、各摺動部材の熱変形を抑制して、ロータの両
端面及びロータ外周の焼付焼損から回避さnるようにし
たことを特徴とする耐久性のある可動翼形回転式圧縮機
を提供することにある。SUMMARY OF THE INVENTION An object of the present invention has been made to eliminate the above-mentioned drawbacks of the conventional technology. It is an object of the present invention to provide a durable movable vane type rotary compressor, which is characterized in that seizing and burning out of the outer periphery of the rotor is avoided.
上述の目的は、ベーン背圧給油の一部を、差圧によシ、
フロント側及びリア側プレートに配設された給油通路に
分流させ、さらに前記給油通路はフロン) 1!+1及
びリア側プレートに配設された軸受箱外周に連絡される
一方、前記軸受箱外周と連゛通ずる給油孔あるいは給油
溝を、圧縮室数(接線シール部数)だけフロント側及び
リア側プレート摺動面に配設することで達成される。The above purpose is to replace part of the vane back pressure oil supply with differential pressure.
The oil flow is divided into the oil supply passages provided on the front and rear plates, and the oil supply passages are further filled with Freon) 1! +1 and the outer periphery of the bearing box arranged on the rear plate, and the oil supply hole or oil groove that communicates with the outer periphery of the bearing box is connected to the front and rear plate slides by the number of compression chambers (the number of tangential seals). This is achieved by placing it on the moving surface.
以下、本発明の一実施例を、添付図面に従ってさらに具
体的に説明する。Hereinafter, one embodiment of the present invention will be described in more detail with reference to the accompanying drawings.
第1図及び第2図は、本発明の一実施例を備えた当該圧
縮機の本体を示すものであって、この圧縮機は、圧縮機
カバーを包囲する一端開口形の圧縮機カバー1並びにフ
ロントカバ2とにより構成され、前記本体Aは、カムリ
ング3とその両側部に締結されたフロント側プレート4
及びリア側プレート5とによシ構成され、これら三者に
ょシカムリング室Bが形成されて、草のカムリング室B
内に、ロータ6は、フロント側4及びリア側プレート5
に配設されたラジアルニードル軸受7によって回転自在
に収納されている。FIGS. 1 and 2 show the main body of a compressor equipped with an embodiment of the present invention, and the compressor includes a compressor cover 1 with an open end that surrounds the compressor cover, and a compressor cover 1 that surrounds the compressor cover. The main body A includes a cam ring 3 and a front side plate 4 fastened to both sides of the cam ring 3.
and the rear side plate 5, and these three members form a new cam ring chamber B.
Inside, the rotor 6 has a front side plate 4 and a rear side plate 5.
It is rotatably housed by a radial needle bearing 7 disposed in the radial needle bearing 7.
前記ロータ6には、ベーン8が摺動可能に設置され、前
記ベーン8により、カムリングxf3内は、複数個の作
業室に分割され(第2図例では3圧縮室5ベ一ン方式)
、ロータ6が矢印方向に回転することにより、吸入圧縮
を行う。A vane 8 is slidably installed on the rotor 6, and the vane 8 divides the inside of the cam ring xf3 into a plurality of working chambers (in the example in FIG. 2, a 3 compression chamber 5 vane system).
, suction compression is performed by rotating the rotor 6 in the direction of the arrow.
当該圧縮機の冷媒の流れと動作を述べると、フロントカ
バ2に形成された吸入口9より、前記フロントカバ2内
の低圧室Cに矢印方向に流入後、同冷媒は、フロント側
プレートに配設された吸入孔10(第2図では3箇所)
から吸入ポートDを経てカムリング室Bへ矢印方向へ流
入する。同冷媒は、ロータ6に配設された吐出ポートE
及び吐出弁11を経て前記圧縮機カバl内に設けた油分
離装置(第1図では図示してない)を通流する際に、′
油は、同冷媒よシ分離され、圧縮機カバ1内底部に貯溜
し、リア側プレート5に配設された背圧給油孔12より
ベーン背後部及び軸受箱を含む ・各摺動面に、差圧に
よシ給油され、潤滑油として再度圧縮機カバ1内底部に
帰環される。さらに、本発明の一実施例を喝えた背圧給
油孔12から軸受箱内及び軸受箱内のスラストニードル
軸受外周に給油される迄の通路構成を、第1図及び、第
3図を用いて説明する。リア側プレート5に配設された
背圧給油孔12に、吐出圧力相当の圧力油が流入し、背
圧給油孔12からリア側プレート5に配設された軸受箱
に連絡される導通路13を通シ、圧力油は矢印の如く前
記軸受箱内のリア側スラストニードル軸受14外周に流
入後、ベーン背後部15へ到達しベーン8をロータ6外
周に向って飛び出させる作用を行う一方、軸受箱内に到
達した圧力油の一部は、軸受箱内のリア側ラジアルニー
ドル軸受7で形成される隙間を通過して、U−タロのリ
ア廁摺動面における圧縮行程直後へ連絡される導通路1
6に矢印の如く流入し、差圧により、ロータ6のリア1
則摺動面へ面射される。また、前圧給油孔12へ流入し
た圧力油の一部は、フロント側に配設された軸受箱内の
フロント側スラストニードル軸受14外周に連絡さ汎る
フロント側4及びリア側プレー+−5とカムリング外−
It貫通して設けられた、導通路17に矢印の如く給油
分流される。またベーン背圧油は、ベーンスリット間を
、M過して、ロータ6のフロント側摺動面へ流出し、フ
ロント側プレート4に配設された軸受箱内の隙間を矢印
の如< 、tt過して、ンヤフトンール室■“へ到達す
る。シャフトシール室Fへ到達した圧力油の一部は、ロ
ータ6のフロント側慴動面へ連絡されるフロント側プレ
ート4に配設された導通路18により、ロータ6のフロ
ント測摺動面へ差圧で、噴射される。最後に、ロータ端
面とフロント側4及びリア側プレート5間に漏洩流出し
た潤滑油は、カムリング室Bへ逃がしている。To describe the flow and operation of the refrigerant in the compressor, after flowing into the low pressure chamber C inside the front cover 2 in the direction of the arrow from the suction port 9 formed in the front cover 2, the refrigerant flows through the front plate. Suction holes 10 provided (3 locations in Figure 2)
From there, it flows into the cam ring chamber B through the suction port D in the direction of the arrow. The refrigerant is supplied to a discharge port E provided in the rotor 6.
and when flowing through the oil separation device (not shown in FIG. 1) provided in the compressor cover l through the discharge valve 11,'
The oil is separated from the refrigerant, stored in the inner bottom of the compressor cover 1, and is supplied to the back of the vane and the bearing box, including the back pressure oil supply hole 12 arranged in the rear side plate 5. The lubricating oil is supplied by the differential pressure and returned to the inner bottom of the compressor cover 1 as lubricating oil. Furthermore, the passage configuration from the back pressure oil supply hole 12 to the inside of the bearing box and the outer periphery of the thrust needle bearing in the bearing box, according to an embodiment of the present invention, will be explained using FIGS. 1 and 3. explain. Pressure oil equivalent to the discharge pressure flows into the back pressure oil supply hole 12 arranged on the rear side plate 5, and a conduction path 13 is connected from the back pressure oil supply hole 12 to the bearing box arranged on the rear side plate 5. After the pressure oil flows into the outer periphery of the rear thrust needle bearing 14 in the bearing box as shown by the arrow, it reaches the rear part 15 of the vane and has the effect of causing the vane 8 to protrude toward the outer periphery of the rotor 6. A part of the pressure oil that has reached the box passes through the gap formed by the rear radial needle bearing 7 in the bearing box, and is led to the rear sliding surface of the U-Taro immediately after the compression stroke. Passage 1
6 as shown by the arrow, and due to the differential pressure, the rear 1 of the rotor 6
It is reflected onto the sliding surface. Also, a part of the pressure oil that has flowed into the front pressure oil supply hole 12 is communicated with the outer periphery of the front thrust needle bearing 14 in the bearing box disposed on the front side. and outside the cam ring
The oil is supplied to a conduction path 17 provided through it as shown by the arrow. Further, the vane backpressure oil passes through M between the vane slits, flows out to the front side sliding surface of the rotor 6, and flows through the gap in the bearing box provided on the front side plate 4 as shown by the arrow. A part of the pressure oil that has reached the shaft seal chamber F flows through a conduction path 18 provided in the front plate 4 that communicates with the front sliding surface of the rotor 6. As a result, the lubricating oil is injected with a differential pressure onto the front sliding surface of the rotor 6.Finally, the lubricating oil leaked between the rotor end face and the front side 4 and rear side plates 5 is released to the cam ring chamber B.
次に本発明の特徴であるフロント側プレート4及びリア
側プレート5における摺動面上に形成された給油孔ある
いは給油溝構成を第3図、及び第4図と第5図、第6図
を用いて1.さらに具体的に説明する。Next, FIG. 3, FIG. 4, FIG. 5, and FIG. Using 1. This will be explained more specifically.
本発明の特徴とする所は、第3図に示される背圧給油孔
12へ流入した圧力油が、前記した給油 。The feature of the present invention is that the pressure oil flowing into the back pressure oil supply hole 12 shown in FIG.
通路構成によりフロント側4及びリア側プレート5に配
設された軸受箱内のスラストニードル軸受14外同近傍
に到達し、第4図及び第5図に示されるプレート摺動面
上に配設された円周上油溝19あるいは半月状給油孔2
1へ連絡される導通路20(第6図)に流入させること
にある。Due to the passage structure, it reaches the outside and vicinity of the thrust needle bearings 14 in the bearing boxes disposed on the front side 4 and rear side plates 5, and is disposed on the plate sliding surface shown in FIGS. 4 and 5. Circumferential oil groove 19 or semicircular oil supply hole 2
1 through a conductive path 20 (FIG. 6).
すなわち、第4図において、リア側スラストニードル軸
受14外周のリア側プレート5上に円周上油溝19を配
設し、前記円周状油溝19から分岐される油溝を、円周
状油溝における噴射方向が【コータ6の回転方向(矢印
方向)に従う。接線方向にに設け、接線方向ト油溝22
の終端を、破線(iで示すロータ外用ラインと破線11
で示すカムリンダ曲線との支点である■(接線シール部
)に交差させ、接線方向上油溝22の終端位置を、圧縮
室数(接線シール部a)に対応した角度間隔で(第4図
の3圧縮室形なら120°間隔で)配列1−Bだ給油溝
構成とする。That is, in FIG. 4, a circumferential oil groove 19 is provided on the rear plate 5 on the outer periphery of the rear thrust needle bearing 14, and the oil groove branching from the circumferential oil groove 19 is arranged in a circumferential manner. The injection direction in the oil groove follows the rotational direction (arrow direction) of the coater 6. A tangential oil groove 22 is provided in the tangential direction.
The end of the rotor external line indicated by i and the broken line
The terminal position of the upper oil groove 22 in the tangential direction is intersected with the fulcrum of the cam cylinder curve (tangential seal part a) at angular intervals corresponding to the number of compression chambers (tangential seal part a) (see Fig. 4). If it is a 3-compression chamber type, the oil supply grooves will be arranged at 120° intervals (Arrangement 1-B).
従って、上記の給油溝構成にすれば、リア側スジストニ
ードル軸受14外周に位置する円周上池:l’+ 19
へ流入した圧力油は、遠氾・力によってo−夕外周ライ
し・Gに向って流出する一方、円周上池、4内をロータ
6の回転方向に旋回しながら接線方向−に/lll 4
22へ流出し、接線/−ル部近傍へ常時束中的に飛散す
るので、ロータのフロント側及びリア1jll摺動而上
に常時良好な潤滑被膜を形成させると共に、特に接線シ
ール部近傍の油膜強度を増IJnさせ吐出11]1]か
ら吸気側への内部漏洩を威少させ乙。Therefore, with the above oil supply groove configuration, the circumferential upper reservoir located on the outer periphery of the rear side streak needle bearing 14: l'+19
The pressure oil that has flowed into the cylinder flows out toward the outer periphery of the cylinder 4 due to the force of the hydraulic fluid, while rotating in the rotational direction of the rotor 6 within the upper cylinder 4 in the tangential direction.
22, and is constantly scattered in the vicinity of the tangential/ru portion, so that a good lubricating film is always formed on the front side and rear sliding body of the rotor, and the oil film especially near the tangential seal portion is Increase the strength and reduce internal leakage from the discharge 11]1] to the intake side.
また+g明の曲友施例である第5図においてはリア側ス
ラストニードル軸受14外局部から、リア側プレート摺
動面上の接線シール部方向に位置する半月状給油孔21
に連絡される第6図に示される導通路20をリア側プレ
ートに配設し、半月状給油孔21位置を、圧縮室数(接
線シール部数)に対応した角度間隔で(第5図の3圧縮
室形なら120°間隔で)配列された給油孔構成とする
。In addition, in FIG. 5, which is an example of a +g light, a semicircular oil supply hole 21 is located from the outer part of the rear thrust needle bearing 14 to the tangential seal portion on the sliding surface of the rear plate.
The conduction passage 20 shown in Fig. 6 is arranged on the rear plate, and the positions of the semicircular oil supply holes 21 are arranged at angular intervals corresponding to the number of compression chambers (the number of tangential seals) (3 in Fig. 5). If it is a compression chamber type, the oil supply holes are arranged at 120° intervals.
従って上記給油孔構成にすればリア側スラストニードル
軸受14外局部へ到達した圧力油は、導通路20に流入
し、給油孔21から、遠心力によって接線シール部近傍
へ常時噴射されるので前記実施例(第4図)と同様に、
特に接線シール部近傍の油膜強度を増加させ吐出側から
吸気側への内部漏洩を減少させる。Therefore, with the oil supply hole configuration described above, the pressure oil that has reached the external part of the rear thrust needle bearing 14 flows into the conduction path 20 and is constantly injected from the oil supply hole 21 to the vicinity of the tangential seal portion by centrifugal force. Similar to the example (Figure 4),
In particular, the strength of the oil film near the tangential seal portion is increased to reduce internal leakage from the discharge side to the intake side.
以上述べたように、本発明によれば、フロント側及びリ
ア側プレート摺動面の接線シール部方向へ給油溝あるい
は、給油孔を配設し、常時圧力油を、ロータの両端面と
接線シール部方向へ噴射させる給油構成にしたことから
、ロータの両端面と接線シール部近傍に常時良好な潤滑
被膜が形成されるので、ロータ表面の異常過熱を防止す
る効果があり、高速回転領域においても、吐出温度上昇
は抑制され、摺動部材面に発生する焼付焼損を回避して
、耐久性のある可動翼形回転式圧縮機を提供することが
できる。As described above, according to the present invention, oil supply grooves or oil supply holes are provided in the direction of the tangential seals on the sliding surfaces of the front and rear plates, and pressure oil is constantly supplied to both end surfaces of the rotor and the tangential seals. Since the oil is sprayed in the direction of the rotor, a good lubricating film is always formed on both end faces of the rotor and near the tangential seal, which has the effect of preventing abnormal overheating of the rotor surface, even in high-speed rotation areas. The increase in discharge temperature is suppressed, and it is possible to avoid seizure and burnout occurring on the sliding member surface, thereby providing a durable movable vane rotary compressor.
第1図は可動翼形回転式圧縮機本体断面図、第2図は第
1図のI−4断面図、第3図は給油通路部の拡大説明図
、第4図、第5図は本発明の詳細な説明するための説明
図、第6図は第5図のX −X断面図である。
3・・・カムリング、6・・・ロータ、7・・・ラジア
ルニードル軸受・、12・・・ベーン背圧給油孔、14
・・・スラストニードル軸受、19・・・円周上油溝、
21・・・半第 S 図Figure 1 is a sectional view of the movable vane rotary compressor main body, Figure 2 is a sectional view taken along I-4 in Figure 1, Figure 3 is an enlarged explanatory view of the oil supply passage, and Figures 4 and 5 are the main body of the rotary compressor. An explanatory diagram for explaining the invention in detail, FIG. 6 is a sectional view taken along line X-X in FIG. 5. 3... Cam ring, 6... Rotor, 7... Radial needle bearing, 12... Vane back pressure oil supply hole, 14
...Thrust needle bearing, 19...Circumferential oil groove,
21... Half figure S
Claims (1)
れたフロント側及びリア側プレートによシカムリング室
を形成し、前記カムリング室に回転自在に横架されたロ
ータと、前記ロータのベーンスリット3間に、ベーンを
半径方向に摺動自在に配設した可動翼形回転式圧縮機に
おいて、フロント側及びリア側プレートに形成された凸
状空間に軸受箱を設け、前記軸受箱内にう゛シアルニー
ドル軸受とスラストニードル軸受を配設して、リア側プ
レートに配設した背圧給油孔を、リア側軸受箱内のスラ
ストニードル軸受外周近傍に連通させる一方、前記背圧
給油孔から、フロント側軸受箱内のスラストニードル軸
受外周近傍に連通ずる給油通路を、カムリング及び、フ
ロント側プレートに配設したことを特徴とする可動翼形
回転式圧縮機の給油構造。 2、特許請求の範囲第1項において1、リア側スラスト
ニードル軸受外周近傍のリア側プレート摺動面上に円周
上油溝を配設し、前記円周上油溝から分岐される油溝を
円周上油溝のロータの回転方向に従う接゛線方向上に設
け、前記接線方向上油溝終端が、カムリングの接線シー
ル部方向に位置する一方、前記給油終端位置が圧縮室数
(接線シール部数)に対応した角度間隔でリア側摺動面
上に配設されたことを特徴とする可動翼形回転式圧縮機
の給油構造。 3、特許請求の範囲第1項において、リア側スラ・スト
ニードル軸受外周部から、リア側プレート摺動面上のカ
ムリング接線シール部方向へ位置する半月状給油孔に連
絡さ牲る導通路を、リア側プレートに配設し、前記半月
状給油孔を、圧縮室数(接線シール部数〕に対応した角
度間隔で、リア側プレート摺動面上に配設したことを特
徴ζする可動翼形回転式圧縮機の給油構造。 4、特許請求の範囲第2項および第3項において、給油
構造をフロント側プレート摺動面にも同時に、あるいは
組合せて配設したことを特徴とする特許翼形回転式圧縮
機の給油構造。[Scope of Claims] (1) A cam ring chamber is formed by a cam ring and front and rear plates fastened to both sides of the cam ring, and a rotor is rotatably suspended horizontally in the cam ring chamber; In a movable vane type rotary compressor in which vanes are arranged between vane slits 3 so as to be slidable in the radial direction, a bearing box is provided in a convex space formed in the front side and rear side plates, and a bearing box is provided in the convex space formed in the front side and rear side plates. A radial needle bearing and a thrust needle bearing are arranged, and the back pressure oil supply hole arranged in the rear side plate is communicated with the vicinity of the outer periphery of the thrust needle bearing in the rear side bearing box. A refueling structure for a movable vane rotary compressor, characterized in that a refueling passage communicating with the vicinity of the outer periphery of a thrust needle bearing in a front bearing box is provided in a cam ring and a front plate. 2. Claim 1: 1. A circumferential oil groove is provided on the sliding surface of the rear plate near the outer periphery of the rear thrust needle bearing, and the oil groove is branched from the circumferential oil groove. is provided in the tangential direction of the oil groove on the circumference according to the rotational direction of the rotor, and the end of the upper oil groove in the tangential direction is located toward the tangential seal portion of the cam ring, while the oil supply end position is located in the direction of the number of compression chambers (the tangential direction). A refueling structure for a movable vane rotary compressor, characterized in that the oil supply structure is arranged on the rear sliding surface at angular intervals corresponding to the number of seals (number of seals). 3. In claim 1, there is provided a conduction path that connects from the outer circumference of the rear thrust needle bearing to the semicircular oil supply hole located in the direction of the cam ring tangential seal on the sliding surface of the rear plate. A movable airfoil shape characterized in that the semicircular oil supply holes are arranged on the sliding surface of the rear plate at angular intervals corresponding to the number of compression chambers (the number of tangential seals). Oil supply structure for a rotary compressor. 4. A patented airfoil according to claims 2 and 3, characterized in that the oil supply structure is also provided on the sliding surface of the front plate at the same time or in combination. Rotary compressor oil supply structure.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14390381A JPS5847195A (en) | 1981-09-14 | 1981-09-14 | Oil feeding structure for movable-vane type rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14390381A JPS5847195A (en) | 1981-09-14 | 1981-09-14 | Oil feeding structure for movable-vane type rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5847195A true JPS5847195A (en) | 1983-03-18 |
Family
ID=15349745
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP14390381A Pending JPS5847195A (en) | 1981-09-14 | 1981-09-14 | Oil feeding structure for movable-vane type rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5847195A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5411385A (en) * | 1992-11-20 | 1995-05-02 | Calsonic Corporation | Rotary compressor having oil passage to the bearings |
-
1981
- 1981-09-14 JP JP14390381A patent/JPS5847195A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5411385A (en) * | 1992-11-20 | 1995-05-02 | Calsonic Corporation | Rotary compressor having oil passage to the bearings |
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