JPH08159071A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPH08159071A JPH08159071A JP29948494A JP29948494A JPH08159071A JP H08159071 A JPH08159071 A JP H08159071A JP 29948494 A JP29948494 A JP 29948494A JP 29948494 A JP29948494 A JP 29948494A JP H08159071 A JPH08159071 A JP H08159071A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- vane
- cylinder
- sliding
- passage
- 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
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷凍サイクル等に使用
する回転式圧縮機に関し、特に信頼性の向上に係わる。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and more particularly to improving reliability.
【０００２】[0002]
【従来の技術】従来の回転式圧縮機としては特開昭６２
−１９９９９０号公報に示されているものがある。2. Description of the Related Art As a conventional rotary compressor, Japanese Patent Laid-Open No. Sho 62-62
There is one disclosed in Japanese Patent Publication No. 199990.
【０００３】以下図面を参照しながら上記従来の回転式
圧縮機の一例について説明する。図３は従来の回転式圧
縮機の縦断面図であり、図４は図３におけるＢ−Ｂ線に
おける断面図である。An example of the conventional rotary compressor will be described below with reference to the drawings. 3 is a vertical sectional view of a conventional rotary compressor, and FIG. 4 is a sectional view taken along line BB in FIG.
【０００４】図３，図４において、１は密閉ケーシン
グ、１ａは冷媒ガス空間、２は電動機部であり、シャフ
ト３を介してシリンダ４，ローラ５，ベーン６，主軸受
７，副軸受８により構成される機械部本体９と連結して
いる。シャフト３は主軸３ａ，副軸３ｂ，クランク３ｃ
によりなる。In FIGS. 3 and 4, 1 is a closed casing, 1a is a refrigerant gas space, 2 is an electric motor portion, and a shaft 4, a cylinder 4, a roller 5, a vane 6, a main bearing 7, and a sub bearing 8 are provided. It is connected to the machine part body 9 that is configured. The shaft 3 includes a main shaft 3a, a sub shaft 3b, and a crank 3c.
It depends on.
【０００５】また、シャフト３の主軸３ａ，副軸３ｂ，
クランク３ｃにはそれぞれ油路３ｄ，３ｅ，３ｆが設け
られている。１０はベーン６の背面とシリンダ４間に設
けられたスプリングである。１１ａ，１１ｂはそれぞれ
シリンダ４内でローラ５，ベーン６，主軸受７，副軸受
８により構成される吸入室と圧縮室である。１２は副軸
３ｂに固定されるコイルバネ１２ａと副軸受８に固定さ
れるガイド管１２ｂで形成される給油機構であり、油路
３ｅ，３ｆ，３ｄと連通している。１４は吸入管であ
り、副軸受８，シリンダ４の吸入通路１５を介して吸入
室１１ａと連通している。１６は吐出部であり吐出弁
（図示せず）を介して密閉ケーシング１内と連通してい
る。１７は吐出口であり密閉ケーシング１内に開放して
いる。１８は密閉ケーシング１内の潤滑油である。Further, the main shaft 3a of the shaft 3, the sub shaft 3b,
The crank 3c is provided with oil passages 3d, 3e and 3f, respectively. Reference numeral 10 is a spring provided between the rear surface of the vane 6 and the cylinder 4. Reference numerals 11a and 11b denote a suction chamber and a compression chamber, which are constituted by the roller 5, the vane 6, the main bearing 7, and the auxiliary bearing 8 in the cylinder 4, respectively. Reference numeral 12 denotes an oil supply mechanism formed by a coil spring 12a fixed to the sub shaft 3b and a guide tube 12b fixed to the sub bearing 8 and communicating with the oil passages 3e, 3f, 3d. Reference numeral 14 denotes a suction pipe, which communicates with the suction chamber 11a via the auxiliary bearing 8 and the suction passage 15 of the cylinder 4. Reference numeral 16 denotes a discharge part, which communicates with the inside of the closed casing 1 via a discharge valve (not shown). A discharge port 17 is open to the inside of the closed casing 1. Reference numeral 18 is a lubricating oil in the closed casing 1.
【０００６】次に回転式圧縮機の機構について説明す
る。冷却システム（図示せず）から冷媒ガスは、吸入管
１４，吸入通路１５より導かれシリンダ４内の吸入室１
１ａに至る。吸入室１１ａに至った冷媒ガスは、シャフ
ト３のクランク３ｃに回転自在に収納されたローラ５と
ベーン６により仕切られた圧縮室１１ｂで、電動機部２
の回転に伴うシャフト３の回転運動により漸次圧縮され
る。圧縮された冷媒ガスは、吐出部１６、吐出弁（図示
せず）を介して密閉ケーシング１内に一旦吐出された
後、吐出口１７を介し冷却システムに吐出される。Next, the mechanism of the rotary compressor will be described. Refrigerant gas from a cooling system (not shown) is introduced from a suction pipe 14 and a suction passage 15 into the suction chamber 1 in the cylinder 4.
1a. The refrigerant gas that has reached the suction chamber 11a is compressed by the roller 5 and the vane 6 that are rotatably accommodated in the crank 3c of the shaft 3 into the compression chamber 11b.
Is gradually compressed by the rotational movement of the shaft 3 accompanying the rotation of the. The compressed refrigerant gas is once discharged into the closed casing 1 through the discharge unit 16 and a discharge valve (not shown), and then discharged through the discharge port 17 into the cooling system.
【０００７】また、密閉ケーシング１内の下部に溜まっ
た潤滑油１８は、給油機構１２の副軸３ｂに固定された
コイルバネ１２ａの回転に伴い、ガイド管１２ｂ内のコ
イルバネ１２ａを介して副軸３ｂに至り、油路３ｅ，３
ｆ，３ｄを通り摺動部を潤滑し、一部は主軸受７の電動
機２側の排油口１３より流出し、直接密閉ケーシング１
下部に戻る。また一部は圧縮室１１ｂに入り冷媒ガスと
共に密閉ケーシング１内に吐出され密閉ケーシング１の
下部に戻る。The lubricating oil 18 accumulated in the lower portion of the closed casing 1 is rotated by the coil spring 12a fixed to the sub shaft 3b of the oil supply mechanism 12, and is passed through the coil spring 12a in the guide tube 12b to the sub shaft 3b. Reaching the oil passages 3e, 3
The sliding parts are lubricated through f and 3d, and a part of them flows out from the oil drain port 13 on the electric motor 2 side of the main bearing 7 to directly seal the casing 1.
Go back to the bottom. A part of the gas enters the compression chamber 11b and is discharged into the closed casing 1 together with the refrigerant gas, and returns to the lower part of the closed casing 1.
【０００８】また、ベーン６とシリンダ４間について
は、ベーン６が往復運動する際に密閉ケーシング１内に
溜められた潤滑油１８に浸ることによりベーン６への給
油がなされ、ベーン６とシリンダ４間の摺動部が潤滑，
シールされている。Further, between the vane 6 and the cylinder 4, when the vane 6 reciprocates, it is immersed in the lubricating oil 18 stored in the closed casing 1 to supply oil to the vane 6 and the vane 6 and the cylinder 4. Lubrication between sliding parts,
It is sealed.
【０００９】[0009]
【発明が解決しようとする課題】しかしながら上記従来
の構成では、密閉ケーシング１内から冷却システムへの
潤滑油１８の流出量が多い圧力条件の場合、あるいは冷
却システムからの潤滑油１８の戻りが悪い際には、密閉
ケーシング１下部に溜まった潤滑油１８の油面が低下
し、ベーン６が往復運動をしても潤滑油１８に浸らなく
なるため、ベーン摺動部が給油不能となる。また、高温
・高圧の厳しい条件での運転では、潤滑油１８の粘度が
低下し、さらにベーン６に作用するガス圧荷重が大きく
なることからベーン摺動部の潤滑状態が悪化するため、
摩耗や焼付きの原因になるとの信頼性低下の課題があっ
た。さらに、シール性が悪くなり体積効率の低下や摺動
損失の増大により効率が低下するとの課題があった。However, in the above-mentioned conventional structure, the lubricating oil 18 returns from the cooling system poorly under a pressure condition in which the amount of the lubricating oil 18 flowing from the closed casing 1 into the cooling system is large. At this time, the oil level of the lubricating oil 18 accumulated in the lower portion of the closed casing 1 is lowered, and even if the vane 6 reciprocates, it is not immersed in the lubricating oil 18, so that the vane sliding portion cannot be refueled. In addition, when operating under severe conditions of high temperature and high pressure, the viscosity of the lubricating oil 18 decreases, and the gas pressure load acting on the vane 6 increases, which deteriorates the lubrication state of the vane sliding portion.
There is a problem that reliability is deteriorated due to wear and seizure. Further, there is a problem that the sealing performance is deteriorated, the volume efficiency is lowered, and the sliding loss is increased to lower the efficiency.
【００１０】本発明は、上記従来の課題を解決するもの
であり、信頼性の向上及び体積効率の低下や摺動損失の
増大を防止することを目的としている。The present invention solves the above-mentioned conventional problems, and an object of the present invention is to improve reliability, prevent volume efficiency from decreasing, and prevent sliding loss from increasing.
【００１１】[0011]
【課題を解決するための手段】上記課題を解決するため
本発明の回転式圧縮機は、ベーンの吸入室側及び圧縮室
側摺動部に開口部を有し開口部からローラとベーンの当
接部に対して離れる方向に深くなる傾斜油溝と、一端が
ベーンの摺動部に開口し他端が傾斜油溝に連通する油通
路と、シリンダのベーン摺動部に設けられ油通路と連通
する油溜部と、一端が副軸受給油部に開口し他端が油溜
部に連通した給油路とを備えた構成となっている。In order to solve the above-mentioned problems, a rotary compressor of the present invention has an opening at a suction part side of a vane and a sliding part on the compression chamber side, and the contact between the roller and the vane is made from the opening part. An inclined oil groove that deepens in the direction away from the contact portion, an oil passage that opens at the sliding portion of the vane at one end and communicates with the inclined oil groove at the other end, and an oil passage that is provided at the vane sliding portion of the cylinder. It is configured to include an oil reservoir communicating with each other, and an oil supply passage having one end opened to the auxiliary bearing oil supply and the other end communicating with the oil reservoir.
【００１２】[0012]
【作用】本発明の回転式圧縮機は上記の構成により、密
閉ケーシング内の潤滑油の油面が低下し、往復運動をす
るベーンが潤滑油に浸らなくなった場合でも常に給油機
構からベーン摺動部の油溜部及び油通路を介して傾斜油
溝へ潤滑油を供給すると共に、ベーン摺動部への差圧に
よる給油に加えて、ベーンの往復運動で生じる潤滑油の
慣性力を利用して特にベーン溝の荷重の大きい摺動部を
潤滑することができる。したがって、ベーンとシリンダ
間の給油不良による摩耗や焼付き及びシール性の低下、
摺動損失の増大を防止することができ、信頼性が向上す
ると共に効率の低下を防止できるものである。The rotary compressor according to the present invention has the above-described structure, and even when the oil level of the lubricating oil in the closed casing is lowered and the reciprocating vanes are no longer immersed in the lubricating oil, the vanes slide from the oil supply mechanism at all times. Lubrication oil is supplied to the inclined oil groove through the oil reservoir and oil passage of the section, and in addition to the oil supply by the differential pressure to the vane sliding part, the inertia force of the lubricating oil generated by the reciprocating motion of the vane is used. In particular, it is possible to lubricate the sliding portion of the vane groove having a large load. Therefore, wear and seizure due to poor lubrication between the vane and the cylinder, and deterioration of sealing performance,
It is possible to prevent an increase in sliding loss, improve reliability, and prevent a decrease in efficiency.
【００１３】[0013]
【実施例】以下本発明による回転式圧縮機の第１の実施
例について図面を参照しながら説明する。なお、従来と
同一構成については、同一符号を付して詳細な説明を省
略する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the rotary compressor according to the present invention will be described below with reference to the drawings. It should be noted that the same configurations as those of the conventional one are denoted by the same reference numerals and detailed description thereof will be omitted.
【００１４】図１は本発明の第１の実施例による回転式
圧縮機の縦断面図であり、図２は図１のＡ−Ａ線におけ
る断面図である。FIG. 1 is a vertical sectional view of a rotary compressor according to a first embodiment of the present invention, and FIG. 2 is a sectional view taken along line AA of FIG.
【００１５】図１、図２において、１９はシリンダ４と
ベーン６の吸入室側摺動部２０に設けられた油溜部であ
り、２１は一端が副軸受給油部２２に開口し他端が油溜
部１９と連通した給油路である。２３ａ，２３ｂはそれ
ぞれベーン６の吸入室側摺動部２０及び圧縮室側摺動部
２４に開口部２６を有し開口部２６からローラ５とベー
ン６の当接部２７に対して離れる方向に深くなる傾斜油
溝である。２５は一端がベーン６の吸入室側摺動部２０
に開口し他端が吸入室側及び圧縮室側の傾斜油溝２３
ａ，２３ｂと連通する油通路である。In FIGS. 1 and 2, 19 is an oil sump portion provided on the suction chamber side sliding portion 20 of the cylinder 4 and the vane 6, and 21 is one end open to the auxiliary bearing oil supply portion 22 and the other end is It is an oil supply passage communicating with the oil reservoir 19. Reference numerals 23a and 23b respectively have openings 26 in the suction chamber side sliding portion 20 and the compression chamber side sliding portion 24 of the vane 6 and in a direction away from the opening portion 26 with respect to the contact portion 27 of the roller 5 and the vane 6. It is a deep oil groove. 25 is a sliding portion 20 on the suction chamber side of the vane 6 at one end.
To the suction chamber side and the compression chamber side at the other end
It is an oil passage communicating with a and 23b.
【００１６】以上のように構成された回転式圧縮機につ
いて、以下その動作を説明する。密閉ケーシング１内の
下部に溜まった潤滑油１８は、給油機構１２の副軸３ｂ
に固定されたコイルバネ１２ａの回転に伴い、ガイド管
１２ｂ内のコイルバネ１２ａを介して副軸受給油部２２
へ至り、一部は副軸受８の摺動部より機械部９の各摺動
部へ供給される。また、一部は給油路２１を介して油溜
部１９へ供給されている。The operation of the rotary compressor configured as described above will be described below. The lubricating oil 18 accumulated in the lower portion of the closed casing 1 is the auxiliary shaft 3 b of the oil supply mechanism 12.
Along with the rotation of the coil spring 12a fixed to the sub-bearing, the auxiliary bearing oil supply section 22 is inserted through the coil spring 12a in the guide tube 12b.
Then, a part is supplied from the sliding portion of the auxiliary bearing 8 to each sliding portion of the mechanical portion 9. A part of the oil is supplied to the oil reservoir 19 via the oil supply passage 21.
【００１７】また、シリンダ４の溝内を往復運動するベ
ーン６に設けられた油通路２５と、シリンダ４に設けら
れている油溜部１９は連通しており、潤滑油１８は油溜
部１９から油通路２５を介して傾斜油溝２３ａ，２３ｂ
へ供給され、常にベーン６の摺動部２０，２４へ給油さ
れる。よって、密閉ケーシング１の下部に溜まった潤滑
油１８の油面が低下して、ベーン６の往復運動で潤滑油
に浸らない場合においても潤滑不良を回避できる。The oil passage 25 provided in the vane 6 which reciprocates in the groove of the cylinder 4 communicates with the oil reservoir 19 provided in the cylinder 4, and the lubricating oil 18 contains the oil reservoir 19. Through the oil passage 25 from the inclined oil grooves 23a, 23b
Is constantly supplied to the sliding portions 20 and 24 of the vane 6. Therefore, even if the oil level of the lubricating oil 18 accumulated in the lower portion of the closed casing 1 is lowered and the vane 6 is not immersed in the lubricating oil by the reciprocating motion of the vane 6, the poor lubrication can be avoided.
【００１８】また、傾斜油溝２３ａ，２３ｂは、ベーン
６の吸入室側摺動部２０及び圧縮室側摺動部２４の開口
部２６からローラ５とベーン６の当接部２７に対して離
れる方向に深くなる様に設けられているため、傾斜油溝
２３ａ，２３ｂ内の潤滑油１８は、ベーン６に大きなガ
ス圧荷重が加わるベーン６の下死点方向の運動でローラ
ー５とベーン６の当接部２７の方向に慣性力を受ける。
さらに、ローラー５とベーン６の当接部２７の方向に慣
性力を受けた潤滑油１８は、傾斜油溝２３ａ，２３ｂに
沿ってシリンダ４とベーン６の荷重の大きい摺動部へ給
油される。Further, the inclined oil grooves 23a and 23b are separated from the suction chamber side sliding portion 20 of the vane 6 and the opening portion 26 of the compression chamber side sliding portion 24 with respect to the contact portion 27 of the roller 5 and the vane 6. Since the lubricating oil 18 in the inclined oil grooves 23a and 23b is provided so as to become deep in the direction, the movement of the roller 5 and the vane 6 in the bottom dead center direction of the vane 6 in which a large gas pressure load is applied to the vane 6. An inertial force is applied in the direction of the contact portion 27.
Further, the lubricating oil 18 which has received the inertial force in the direction of the contact portion 27 of the roller 5 and the vane 6 is supplied to the sliding portion of the cylinder 4 and the vane 6 having a large load along the inclined oil grooves 23a and 23b. .
【００１９】従って、シリンダ４とベーン６の摺動部
は、従来通りにベーン６の背圧と圧縮室１１ａ，１１ｂ
の差圧によりベーン６の摺動部２０，２４へ給油される
と共に、加えて、潤滑油１８の慣性力によりベーン６の
摺動部２０，２４の特に荷重の大きい部位へ給油できる
ため、高温・高圧の厳しい条件での運転におけるベーン
６の摺動部２０，２４の耐荷重性及び耐摩耗性が向上す
る。Therefore, the sliding portion between the cylinder 4 and the vane 6 has the conventional back pressure of the vane 6 and the compression chambers 11a and 11b.
Is applied to the sliding portions 20 and 24 of the vane 6 and, in addition, the inertial force of the lubricating oil 18 can be applied to the sliding portions 20 and 24 of the vane 6 where the load is particularly large. -The load resistance and wear resistance of the sliding portions 20 and 24 of the vane 6 are improved during operation under high pressure and severe conditions.
【００２０】以上のように本実施例の回転式圧縮機は、
ベーン６の吸入室側及び圧縮室側摺動部２４に開口部２
６を有し開口部２６からローラ５とベーン６の当接部２
７に対して離れる方向に深くなる傾斜油溝２３ａ，２３
ｂと、一端がベーン６の摺動部に開口し他端が傾斜油溝
２３ａ，２３ｂに連通する油通路２５と、シリンダ４の
ベーン摺動部に設けられ油通路２５と連通する油溜部１
９と、一端が副軸受給油部２２に開口し他端が油溜部１
９に連通した給油路２１とから構成されているので、シ
リンダ４とベーン６の摺動部は、密閉ケーシング１内の
潤滑油１８の油面が低下した場合においてもベーン６の
摺動部２０、２４へ常に潤滑油１８を供給できると共
に、差圧給油に加えて、潤滑油１８の慣性力によりシリ
ンダ４とベーン６の摺動部の荷重大部へ給油できる。従
って、ベーン６とシリンダ４の摩耗や焼付き及びシール
性の低下、摺動損失の増大を防止することができるた
め、効率の低下を防止できるとともに信頼性も向上す
る。As described above, the rotary compressor of this embodiment is
The opening 2 is formed in the suction chamber side and compression chamber side sliding portion 24 of the vane 6.
6, the contact portion 2 between the roller 5 and the vane 6 through the opening 26
Inclined oil grooves 23a, 23 that become deeper in the direction away from 7
b, an oil passage 25 having one end opened to the sliding portion of the vane 6 and the other end communicating with the inclined oil grooves 23a and 23b, and an oil reservoir portion provided in the vane sliding portion of the cylinder 4 and communicating with the oil passage 25. 1
9 and one end opens to the auxiliary bearing oil supply portion 22 and the other end to the oil reservoir portion 1
9 is connected to the oil supply passage 21. Therefore, the sliding portion of the cylinder 4 and the vane 6 has a sliding portion 20 of the vane 6 even when the oil level of the lubricating oil 18 in the closed casing 1 is lowered. , 24 can be always supplied, and in addition to differential pressure oil supply, the inertia force of the lubricating oil 18 can be used to supply a large load to the sliding portion between the cylinder 4 and the vane 6. Therefore, it is possible to prevent wear and seizure of the vane 6 and the cylinder 4, deterioration of sealing performance, and increase of sliding loss, so that it is possible to prevent deterioration of efficiency and improve reliability.
【００２１】[0021]
【発明の効果】以上説明したように本発明は、ベーンの
吸入室側及び圧縮室側摺動部に開口部を有し開口部から
ローラとベーンの当接部に対して離れる方向に深くなる
傾斜油溝と、一端がベーンの摺動部に開口し他端が傾斜
油溝に連通する油通路と、シリンダのベーン溝摺動部に
設けられ油通路と連通する油溜部と、一端が副軸受給油
部に開口し他端が油溜部に連通した給油路とを備えたも
のであるから、密閉ケーシング内の潤滑油の油面が低下
し、往復運動をするベーンが潤滑油に浸らなくなった場
合でも給油機構からベーン摺動部へ常に潤滑油を供給す
ることができる。さらに、シリンダとベーンの摺動部を
差圧給油に加えて、潤滑油の慣性力によりシリンダとベ
ーンの荷重が大きい摺動部へ給油できるため、ベーンと
シリンダ間の給油不良による摩耗や焼付き及びシール性
の低下、摺動損失の増大を防止することができ、信頼性
が向上すると共に効率の低下を防止できる。As described above, according to the present invention, the sliding portions of the vane on the suction chamber side and the compression chamber side have openings, and the depth becomes deeper in the direction away from the contact portion between the roller and the vane. The inclined oil groove, an oil passage having one end open to the sliding portion of the vane and the other end communicating with the inclined oil groove, an oil reservoir portion provided in the sliding portion of the vane groove of the cylinder and communicating with the oil passage, and one end Since it is provided with an oil supply passage that opens to the auxiliary bearing oil supply part and the other end communicates with the oil sump part, the oil level of the lubricating oil in the closed casing decreases and the reciprocating vanes are immersed in the lubricating oil. Even when the oil disappears, the lubricating oil can be constantly supplied from the oil supply mechanism to the vane sliding portion. Furthermore, in addition to differential pressure lubrication at the sliding part between the cylinder and the vane, the inertial force of the lubricating oil can lubricate the sliding part where the load between the cylinder and the vane is large, so wear and seizure due to poor lubrication between the vane and cylinder In addition, it is possible to prevent a decrease in sealing property and an increase in sliding loss, which improves reliability and prevents a decrease in efficiency.
【図１】本発明による回転式圧縮機の第１の実施例の縦
断面図FIG. 1 is a vertical sectional view of a first embodiment of a rotary compressor according to the present invention.
【図２】図１のＡ−Ａ線における断面図FIG. 2 is a sectional view taken along line AA of FIG.
【図３】従来の回転式圧縮機の縦断面図FIG. 3 is a vertical sectional view of a conventional rotary compressor.
【図４】図３のＢ−Ｂ線における断面図FIG. 4 is a sectional view taken along line BB of FIG.
１ 密閉ケーシング １ａ 冷媒ガス空間 ４ シリンダ ４ａ シリンダの溝 ５ ローラ ６ ベーン ７ 主軸受 ８ 副軸受 １１ａ 吸入室 １１ｂ 圧縮室 １２ 給油機構 １８ 潤滑油 １９ 油溜部 ２０ 吸入室側摺動部 ２１ 給油路 ２２ 副軸受給油部 ２３ａ、２３ｂ 傾斜油溝 ２４ 圧縮室側摺動部 ２５ 油通路 ２６ 開口部 ２７ 当接部 1 Airtight Casing 1a Refrigerant Gas Space 4 Cylinder 4a Cylinder Groove 5 Roller 6 Vane 7 Main Bearing 8 Secondary Bearing 11a Suction Chamber 11b Compression Chamber 12 Lubrication Mechanism 18 Lubricating Oil 19 Oil Reservoir 20 Suction Chamber Side Sliding Part 21 Oil Supply Channel 22 Auxiliary bearing oil supply section 23a, 23b Inclined oil groove 24 Compression chamber side sliding section 25 Oil passage 26 Opening section 27 Abutting section
Claims (1)
と、前記密閉ケーシングの下部に溜められた潤滑油と、
前記密閉ケーシング内に収納されるシリンダと、前記シ
リンダの両端に固定された主軸受および副軸受と、前記
シリンダ内を偏心回転するローラと、前記シリンダのベ
ーン溝内を往復運動し前記ローラと当接することにより
前記シリンダ内を吸入室と圧縮室に分割するベーンと、
前記密閉ケーシングの下部に溜められた前記潤滑油を副
軸受給油部に供給する給油機構と、前記ベーンの吸入室
側及び圧縮室側摺動部に開口部を有し前記開口部から前
記ローラと前記ベーンの当接部に対して離れる方向に深
くなる傾斜油溝と、一端が前記ベーンの摺動部に開口し
他端が前記傾斜油溝に連通する油通路と、前記ベーン溝
摺動部に設けられ前記油通路と連通する油溜部と、一端
が前記副軸受給油部に開口し他端が前記油溜部に連通し
た給油路とを備えた回転式圧縮機。1. A hermetic casing having a refrigerant gas space, and lubricating oil stored in a lower portion of the hermetic casing,
A cylinder housed in the closed casing, a main bearing and a sub-bearing fixed to both ends of the cylinder, a roller that eccentrically rotates in the cylinder, and a reciprocating motion in a vane groove of the cylinder to contact the roller. A vane that divides the inside of the cylinder into a suction chamber and a compression chamber by contacting each other;
An oil supply mechanism that supplies the lubricating oil stored in the lower portion of the closed casing to the auxiliary bearing oil supply part, and an opening at the suction chamber side and compression chamber side sliding part of the vane, and from the opening to the roller. An inclined oil groove that deepens in a direction away from the contact portion of the vane, an oil passage having one end opened to the sliding portion of the vane and the other end communicating with the inclined oil groove, and the vane groove sliding portion. A rotary compressor provided with an oil reservoir connected to the oil passage, and an oil supply passage having one end opened to the auxiliary bearing oil supply portion and the other end communicated with the oil reservoir.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29948494A JPH08159071A (en) | 1994-12-02 | 1994-12-02 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29948494A JPH08159071A (en) | 1994-12-02 | 1994-12-02 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08159071A true JPH08159071A (en) | 1996-06-18 |
Family
ID=17873174
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP29948494A Pending JPH08159071A (en) | 1994-12-02 | 1994-12-02 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08159071A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003060326A1 (en) * | 2001-12-28 | 2003-07-24 | Lg Electronics Inc. | Compressor and vane therefor |
| WO2016143177A1 (en) * | 2015-03-06 | 2016-09-15 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| WO2017018005A1 (en) * | 2015-07-24 | 2017-02-02 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| JP2017031810A (en) * | 2015-07-28 | 2017-02-09 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| WO2017056644A1 (en) * | 2015-09-28 | 2017-04-06 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
-
1994
- 1994-12-02 JP JP29948494A patent/JPH08159071A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003060326A1 (en) * | 2001-12-28 | 2003-07-24 | Lg Electronics Inc. | Compressor and vane therefor |
| WO2016143177A1 (en) * | 2015-03-06 | 2016-09-15 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| JPWO2016143177A1 (en) * | 2015-03-06 | 2017-08-03 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| CN107076148A (en) * | 2015-03-06 | 2017-08-18 | 东芝开利株式会社 | Rotary compressor and freezing cycle device |
| WO2017018005A1 (en) * | 2015-07-24 | 2017-02-02 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| JPWO2017018005A1 (en) * | 2015-07-24 | 2018-02-08 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| CN107850073A (en) * | 2015-07-24 | 2018-03-27 | 东芝开利株式会社 | Rotary compressor and refrigerating circulatory device |
| JP2017031810A (en) * | 2015-07-28 | 2017-02-09 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| WO2017056644A1 (en) * | 2015-09-28 | 2017-04-06 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
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