JPH06346880A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPH06346880A JPH06346880A JP14051393A JP14051393A JPH06346880A JP H06346880 A JPH06346880 A JP H06346880A JP 14051393 A JP14051393 A JP 14051393A JP 14051393 A JP14051393 A JP 14051393A JP H06346880 A JPH06346880 A JP H06346880A
- Authority
- JP
- Japan
- Prior art keywords
- chamber side
- lubricating oil
- oil
- cylinder
- vane
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003921 oil Substances 0.000 claims abstract description 100
- 239000010687 lubricating oil Substances 0.000 claims abstract description 95
- 230000006835 compression Effects 0.000 claims abstract description 82
- 238000007906 compression Methods 0.000 claims abstract description 82
- 239000003507 refrigerant Substances 0.000 claims description 8
- 230000006866 deterioration Effects 0.000 description 10
- 238000005461 lubrication Methods 0.000 description 9
- 238000007789 sealing Methods 0.000 description 8
- 238000001816 cooling Methods 0.000 description 4
- 238000005299 abrasion Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Landscapes
- 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 is known.
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６は従来の回転式圧
縮機の縦断面図であり、図７は図６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. FIG. 6 is a vertical sectional view of a conventional rotary compressor, and FIG. 7 is a sectional view taken along line BB in FIG.
【０００４】図６，図７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. 6 and 7, 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にはそれぞれ油通路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
通路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, 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１
４，吸入通路１５より導かれシリンダ４内の吸入室１１
ａ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 drawn into the suction pipe 1.
4, the suction chamber 11 in the cylinder 4 guided from the suction passage 15
to a. The refrigerant gas reaching the suction chamber 11a is compressed in the compression chamber 11b partitioned by the roller 5 and the vane 6 which are rotatably housed in the crank 3c of the shaft 3 and is gradually rotated by the rotational movement of the shaft 3 accompanying the rotation of the electric motor unit 2. Compressed. 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、油通路３ｅ，
３ｆ，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. To the oil passage 3e,
The sliding parts are lubricated through 3f and 3d, and a part of them flows out from the oil discharge port 13 of the main bearing 7 on the electric motor 2 side and directly returns to the lower part of the closed casing 1. A part of the gas enters the compression chamber 11b and is discharged into the closed casing 1 together with the refrigerant gas.
Return to the bottom of.
【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、密閉ケーシング内から冷却システムへの潤
滑油の流出量が多い圧力条件の場合、あるいは冷却シス
テムからの潤滑油の戻りが悪い際には、密閉ケーシング
下部に溜まった潤滑油の油面が低下する。その時にはベ
ーンが往復運動をしても潤滑油に浸らなくなり、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 configuration, under a pressure condition in which the amount of lubricating oil flowing from the closed casing into the cooling system is large, or when the lubricating oil returns from the cooling system poorly. , The oil level of the lubricating oil accumulated in the lower part of the closed casing lowers. At that time, even if the vane reciprocates, it will not be submerged in the lubricating oil, and there is a problem of deterioration in reliability that causes 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、シリンダの溝の吸入室側摺動
部に設けられた吸入室側潤滑油室と、シリンダの溝の圧
縮室側摺動部に設けられた圧縮室側潤滑油室と、一端が
副軸受給油部に開口し他端が吸入室側潤滑油室及び圧縮
室側潤滑油室に連通した給油路を備えた構成となってい
る。In order to solve the above problems, a rotary compressor according to the present invention has a suction chamber side lubricating oil chamber provided at a suction groove side sliding portion of a cylinder groove and a cylinder groove. It has a compression chamber side lubricating oil chamber provided in the compression chamber side sliding part, and an oil supply passage that opens at one end to the auxiliary bearing oil supply part and connects the other end to the suction chamber side lubrication oil chamber and the compression chamber side lubrication oil chamber. It has been configured.
【００１２】また、吸入室側潤滑油室と圧縮室側潤滑油
室とを連通する潤滑油の連通路を備えた構成となってい
る。Further, there is provided a lubricating oil communication passage for connecting the suction chamber side lubricating oil chamber and the compression chamber side lubricating oil chamber.
【００１３】また、吸入室側摺動部及び圧縮室側摺動部
に油溜め部を有するベーンを備えた構成となっている。Further, the suction chamber side sliding portion and the compression chamber side sliding portion are provided with vanes having oil sumps.
【００１４】また、シリンダとベーンの吸入室側摺動部
に設けられ、ベーン往復運動方向における吸入室側摺動
部の中央よりもローラ側に設けられた吸入室側油溜め部
と、シリンダとベーンの圧縮室側摺動部に設けられ、ベ
ーン往復運動方向における圧縮室側摺動部の中央よりも
反ローラ側に設けられた圧縮室側油溜め部と、吸入室側
油溜め部と圧縮室側油溜め部とを連通する連通孔とを備
えた構成となっている。Further, a suction chamber side oil sump portion is provided on a suction chamber side sliding portion of the cylinder and the vane, and is disposed closer to the roller than the center of the suction chamber side sliding portion in the reciprocating direction of the vane, and the cylinder. The compression chamber side oil sump portion, which is provided on the compression chamber side slide portion of the vane, is provided on the roller side rather than the center of the compression chamber side slide portion in the reciprocating direction of the vane, and the suction chamber side oil sump portion and the compression. A communication hole that communicates with the chamber-side oil sump portion is provided.
【００１５】[0015]
【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給油機構か
らベーン摺動部へ潤滑油を供給することができる。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 if the reciprocating vane is no longer immersed in the lubricating oil, the lubricating oil in the hermetic casing is lowered from the oil supply mechanism to the vane sliding portion. The lubricating oil can be supplied to. Therefore, it is possible to prevent wear, seizure, deterioration of sealing performance, and increase of sliding loss due to poor lubrication between the vane and the cylinder, which improves reliability and prevents deterioration of efficiency.
【００１６】また、さらに、シリンダの溝に設けたベー
ンの吸入室側潤滑油室と圧縮室側潤滑油室の圧力をほぼ
同等とすることができるため、圧縮室側潤滑油室に供給
される潤滑油量を吸入室側潤滑油室とほぼ同等量にまで
増大させることができる。したがって、ベーンの吸入室
側摺動部と同等に圧縮室側摺動部の潤滑性を向上でき、
摩耗や焼付き及びシール性の低下、摺動損失の増大を防
止し、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。Further, since the pressure in the suction chamber side lubricating oil chamber of the vane provided in the groove of the cylinder and the pressure in the compression chamber side lubricating oil chamber can be made substantially equal, they are supplied to the compression chamber side lubricating oil chamber. The amount of lubricating oil can be increased to almost the same amount as the lubricating oil chamber on the suction chamber side. Therefore, it is possible to improve the lubricity of the compression chamber side sliding portion as well as the suction chamber side sliding portion of the vane,
It is possible to prevent wear, seizure, decrease in sealing property, increase in sliding loss, improve reliability, and prevent decrease in efficiency.
【００１７】また、さらに、ベーンがシリンダの溝内を
往復運動する際、吸入室側潤滑油室及び圧縮室側潤滑油
室に溜められた潤滑油をベーンの側面に設けられた油溜
め部によりベーンとシリンダの摺動面全体に潤滑油を供
給し、かつ給油量を増大することができる。したがっ
て、油面が低下した場合でもベーンとシリンダ間の摺動
面全体の潤滑性を確保でき、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し、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。Further, when the vane reciprocates in the groove of the cylinder, the lubricating oil accumulated in the suction chamber side lubricating oil chamber and the compression chamber side lubricating oil chamber is caused by the oil sump portion provided on the side surface of the vane. Lubricating oil can be supplied to the entire sliding surface of the vane and the cylinder, and the amount of oil supply can be increased. Therefore, even if the oil level drops, the lubricity of the entire sliding surface between the vane and the cylinder can be secured, wear and seizure, a decrease in sealing performance, and an increase in sliding loss can be prevented, and reliability is improved. It is possible to prevent a decrease in efficiency.
【００１８】また、さらに、ベーンの側面に加わる荷重
が最大となるクランク角にて、給油機構からベーンとシ
リンダ間の摺動面の最大荷重作用部へ潤滑油を供給する
ことができる。したがって、油面が低下した場合でも確
実にベーンとシリンダ間の最大荷重作用部の潤滑を行う
ことができ、摩耗や焼付き及び摺動損失の増大を防止
し、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。Further, the lubricating oil can be supplied from the oil supply mechanism to the maximum load acting portion of the sliding surface between the vane and the cylinder at the crank angle at which the load applied to the side surface of the vane becomes maximum. Therefore, even when the oil level drops, the maximum load acting part between the vane and the cylinder can be reliably lubricated, wear and seizure, and increase in sliding loss are prevented, reliability is improved and efficiency is improved. It is possible to prevent the decrease.
【００１９】[0019]
【実施例】以下本発明による回転式圧縮機の第一の実施
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.
【００２０】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における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 in FIG.
【００２１】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に設けられた吸入室側潤
滑油室であり、２１は圧縮室側摺動部２２に設けられた
圧縮室側潤滑油室である。２３ａ、２３ｂはそれぞれ一
端が副軸受給油部２４に開口し他端が吸入室側潤滑油室
１９及び圧縮室側潤滑油室２１と連通した給油路であ
る。In FIGS. 1 and 2, 19 is a suction chamber side lubricating oil chamber provided in the suction chamber side sliding portion 20 of the cylinder 4 and the vane 6, and 21 is provided in the compression chamber side sliding portion 22. It is the compression chamber side lubricating oil chamber. 23a and 23b are oil supply passages, one end of which opens to the auxiliary bearing oil supply portion 24 and the other end of which communicates with the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21.
【００２２】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２４
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２３ａ、２３ｂを
介してそれぞれ吸入室側潤滑油室１９及び圧縮室側潤滑
油室２１へ導かれ、ベーン６とシリンダ４の摺動部２
０、２２へ給油される。The operation of the rotary compressor having the above structure 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 auxiliary pipe oil supply section 24 via 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. Further, some of them are guided to the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 via the oil supply passages 23a and 23b, respectively, and the sliding portion 2 between the vane 6 and the cylinder 4 is introduced.
It is refueled to 0 and 22.
【００２３】したがって潤滑油１８の油面がベーン６の
最下点より下がった場合でも、ベーン６とシリンダ４間
の摺動部２０、２２を常に潤滑，シールすることができ
る。Therefore, even if the oil level of the lubricating oil 18 falls below the lowest point of the vane 6, the sliding portions 20, 22 between the vane 6 and the cylinder 4 can be lubricated and sealed at all times.
【００２４】以上のように本実施例の回転式圧縮機は、
シリンダ４とベーン６の吸入室側摺動部２０に設けられ
た吸入室側潤滑油室１９と、圧縮室側摺動部２２に設け
られた圧縮室側潤滑油室２１と、一端が副軸受給油部２
４に開口し他端が吸入室側潤滑油室１９及び圧縮室側潤
滑油室２１と連通した給油路２３ａ、２３ｂとから構成
されているので、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、２
２へ常に潤滑油１８を供給できる。したがって、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
A suction chamber side lubricating oil chamber 19 provided in the suction chamber side sliding part 20 of the cylinder 4 and the vane 6, a compression chamber side lubricating oil chamber 21 provided in the compression chamber side sliding part 22, and an auxiliary bearing at one end Refueling section 2
4 and has the other end connected to the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 and the oil supply passages 23a and 23b, so that the oil level of the lubricating oil 18 in the closed casing 1 is Even if it falls, the sliding parts 20, 2 of the vane 6
The lubricating oil 18 can be constantly supplied to 2. Therefore, it is possible to prevent abrasion of the vane 6 and the cylinder 4, seizure, deterioration of sealing performance, and increase of sliding loss, so that it is possible to prevent deterioration of efficiency and improve reliability.
【００２５】次に、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。なお、第１の実施例と同一構
成については、同一符号を付して詳細な説明を省略す
る。Next, a second embodiment of the present invention will be described with reference to the drawings. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.
【００２６】図３は本発明の第２の実施例による回転式
圧縮機の要部断面図である。図３において、２５ａは吸
入室側潤滑油室１９と圧縮室側潤滑油室２１とを連通す
る連通路である。FIG. 3 is a sectional view of the essential parts of a rotary compressor according to the second embodiment of the present invention. In FIG. 3, reference numeral 25a is a communication passage that connects the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21.
【００２７】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。潤滑油１８は給油機構
１２から給油路２３ａを介して、吸入室側潤滑油室１９
へ供給され、吸入室側摺動部２０を潤滑する。その際、
吸入室側潤滑油室１９内は高圧Ｐdと低圧Ｐsの中間圧力
Ｐmとなる。また、吸入室側潤滑油室１９と圧縮室側潤
滑油室２１とが連通路２５ａにて連通しているため、圧
縮室側潤滑油室２１内も中間圧力Ｐmとなる。したがっ
て、圧縮室１１ｂが高圧Ｐdである場合においても、高
圧Ｐdと中間圧力Ｐmとの差圧により給油路２３ｂを介し
て圧縮室側潤滑油室２１内に、吸入室側潤滑油室１９内
と同等の潤滑油を供給することができる。The operation of the rotary compressor constructed as above will be described below. The lubricating oil 18 is supplied from the oil supply mechanism 12 via the oil supply passage 23a to the suction chamber side lubricating oil chamber 19
Is supplied to lubricate the sliding portion 20 on the suction chamber side. that time,
The suction chamber side lubricating oil chamber 19 has an intermediate pressure P m between the high pressure P d and the low pressure P s . Further, since the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 are communicated with each other through the communication passage 25a, the inside of the compression chamber side lubricating oil chamber 21 also has an intermediate pressure P m . Therefore, even when the compression chamber 11b has a high pressure P d , the pressure difference between the high pressure P d and the intermediate pressure P m causes the suction chamber side lubrication oil chamber to enter the compression chamber side lubrication oil chamber 21 through the oil supply passage 23b. The same lubricating oil as that in 19 can be supplied.
【００２８】以上のように本実施例の回転式圧縮機は、
一端が副軸受給油部２４に開口し他端が吸入室側潤滑油
室１９及び圧縮室側潤滑油室２１に連通した給油路２３
ａ、２３ｂと、吸入室側潤滑油室１９と圧縮室側潤滑油
室２１とを連通する連通路２５ａとから構成されている
ので、圧縮室１１ｂが高圧圧力Ｐdである場合において
もシリンダ４とベーン６の圧縮室側摺動部２２へ吸入室
側潤滑油室２０と同等の給油をすることができる。した
がって、圧縮室側摺動部２２の潤滑性を向上でき、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
し、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。As described above, the rotary compressor of this embodiment is
An oil supply passage 23, one end of which opens to the auxiliary bearing oil supply portion 24 and the other end of which communicates with the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21.
a, 23b, and the communication passage 25a that connects the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 to each other, so that the cylinder 4 can operate even when the compression chamber 11b has a high pressure P d. Thus, it is possible to supply the same amount of oil as the suction chamber side lubricating oil chamber 20 to the compression chamber side sliding portion 22 of the vane 6. Therefore, it is possible to improve the lubricity of the sliding portion 22 on the compression chamber side, prevent wear and seizure, decrease in sealing performance, and increase in sliding loss, improve reliability, and prevent a decrease in efficiency. .
【００２９】次に、本発明の第３の実施例について図面
を参照しながら説明する。なお、第１の実施例と同一構
成については、同一符号を付して詳細な説明を省略す
る。Next, a third embodiment of the present invention will be described with reference to the drawings. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.
【００３０】図４は本発明の第３の実施例による回転式
圧縮機の要部断面図である。図４において、２６ａはベ
ーン６の吸入室側摺動部２０及び圧縮室側摺動部２２に
設けられた油溜め部である。FIG. 4 is a sectional view of the essential parts of a rotary compressor according to the third embodiment of the present invention. In FIG. 4, reference numeral 26 a denotes an oil sump portion provided on the suction chamber side sliding portion 20 and the compression chamber side sliding portion 22 of the vane 6.
【００３１】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。潤滑油１８は給油機構
１２から給油路２３ａ、２３ｂを介して吸入室側潤滑油
室１９及び圧縮室側潤滑油室２１に供給され、ベーン６
が往復運動する間に吸入室側潤滑油室１９及び圧縮室側
潤滑油室２１の潤滑油を油溜め部２６ａを介してベーン
６とシリンダ４の摺動部２０、２２全域にわたって潤滑
油を供給できる。The operation of the rotary compressor configured as described above will be described below. The lubricating oil 18 is supplied from the oil supply mechanism 12 to the intake chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 via the oil supply passages 23a and 23b, and the vane 6
While reciprocating, the lubricating oil in the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 is supplied to the entire sliding portions 20, 22 of the vane 6 and the cylinder 4 via the oil sump portion 26a. it can.
【００３２】以上のように本実施例の回転式圧縮機は、
ベーン６の吸入室側摺動部２０及び圧縮室側摺動部２２
に油溜め部２６ａ備えているので、ベーン６とシリンダ
４の摺動部２０、２２全域にわたって潤滑油を供給でき
る。したがって、油面が低下した場合でもベーン６とシ
リンダ４間の摺動部２０、２２全域の潤滑性を確保で
き、摩耗や焼付き及びシール性の低下、摺動損失の増大
を防止し、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。As described above, the rotary compressor of this embodiment is
The suction chamber side sliding portion 20 and the compression chamber side sliding portion 22 of the vane 6
Since the oil sump portion 26a is provided in the above, the lubricating oil can be supplied over the entire sliding portions 20, 22 of the vane 6 and the cylinder 4. Therefore, even if the oil level is lowered, the lubricity of the entire sliding portions 20, 22 between the vane 6 and the cylinder 4 can be ensured, and wear, seizure, deterioration of sealability, and increase of sliding loss can be prevented. It is possible to improve the property and prevent a decrease in efficiency.
【００３３】次に、本発明の第４の実施例について図面
を参照しながら説明する。なお、第１の実施例と同一構
成については、同一符号を付して詳細な説明を省略す
る。Next, a fourth embodiment of the present invention will be described with reference to the drawings. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.
【００３４】図５は本発明の第４の実施例による回転式
圧縮機の要部断面図である。図５において、２６ｂ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、
ベーン６の往復運動方向における吸入室側摺動部２０の
中央よりもローラ５側に設けられた吸入室側油溜め部で
ある。２６ｃは圧縮室側摺動部２２に設けられ、ベーン
６の往復運動方向における圧縮室側摺動部２２の中央よ
りもローラ５と反対側に設けられた圧縮室側油溜め部で
ある。２７は吸入室側油溜め部２６ｂと圧縮室側油溜め
部２６ｃとを連通する連通孔である。FIG. 5 is a sectional view of the essential parts of a rotary compressor according to the fourth embodiment of the present invention. In FIG. 5, 26b is provided on the suction chamber side sliding portion 20 of the cylinder 4 and the vane 6,
The suction chamber side oil sump portion is provided on the roller 5 side with respect to the center of the suction chamber side sliding portion 20 in the reciprocating direction of the vane 6. Reference numeral 26c is a compression chamber side oil sump portion provided on the compression chamber side sliding portion 22 and on the opposite side of the roller 5 from the center of the compression chamber side sliding portion 22 in the reciprocating direction of the vane 6. Reference numeral 27 is a communication hole that connects the suction chamber side oil sump portion 26b and the compression chamber side oil sump portion 26c.
【００３５】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。潤滑油１８は給油機構
１２から給油路２３ａ、２３ｂを介して、それぞれ吸入
室側潤滑油室１９及び圧縮室側潤滑油室２１に供給され
る。また、ベーン６とシリンダ４の摺動部２０、２２に
おいて、クランク角で２７０゜〜３６０゜近傍にて圧縮
室１１ｂのガス圧により最大荷重が作用する。しかも、
摺動部２０、２２においてその最大荷重が作用する領域
は吸入室側摺動部２０においては、ベーン６の往復運動
方向における中央よりもローラ５側であり、圧縮室側摺
動部２２においては、ベーン６の往復運動方向における
中央よりもローラ５と反対側である。そのため、最大荷
重が作用するクランク角において、吸入室側潤滑油室１
９を介して吸入室側油溜め部２６ｂに給油され、最大荷
重が作用する吸入室側の摺動部に確実に給油を行うこと
ができる。また、圧縮室側潤滑油室２１を介して圧縮室
側油溜め部２６ｂに給油され、最大荷重が作用する圧縮
室側の摺動部に確実に給油を行うことができる。さら
に、両油溜め部２６ｂ、２６ｃは、連通孔２７により連
通しているため、圧縮室１１ｂがほぼ高圧Ｐdである最
大荷重作用時においても給油機構１２から両油溜め部２
６ｂ、２６ｃにほぼ同等量の給油を行うことができる。The operation of the rotary compressor constructed as above will be described below. The lubricating oil 18 is supplied from the oil supply mechanism 12 to the suction chamber side lubricating oil chamber 19 and the compression chamber side lubricating oil chamber 21 via the oil supply passages 23a and 23b, respectively. Further, in the sliding portions 20 and 22 of the vane 6 and the cylinder 4, the maximum load acts due to the gas pressure of the compression chamber 11b in the vicinity of the crank angle of 270 ° to 360 °. Moreover,
In the sliding portions 20 and 22, the maximum load acts on the suction chamber side sliding portion 20 on the roller 5 side with respect to the center of the vane 6 in the reciprocating direction, and on the compression chamber side sliding portion 22. , On the opposite side of the roller 5 from the center of the vane 6 in the reciprocating direction. Therefore, at the crank angle at which the maximum load acts, the suction chamber side lubricating oil chamber 1
It is possible to reliably supply oil to the suction chamber side oil sump portion 26b through 9 and to the sliding portion on the suction chamber side where the maximum load acts. Further, oil is supplied to the compression chamber side oil sump portion 26b via the compression chamber side lubricating oil chamber 21 so that the sliding portion on the compression chamber side where the maximum load acts can be surely supplied with oil. Further, since the oil sumps 26b and 26c are communicated with each other through the communication hole 27, even when the compression chamber 11b is under the maximum load at which the compression chamber 11b is at a high pressure Pd , the oil sump 2 is not separated from the oil supply mechanism 12.
It is possible to supply approximately the same amount of oil to 6b and 26c.
【００３６】以上のように本実施例の回転式圧縮機は、
シリンダ４とベーン６の吸入室側摺動部２０に設けら
れ、ベーン６の往復運動方向における吸入室側摺動部２
０の中央よりもローラ５側に設けられた吸入室側油溜め
部２６ｂとシリンダ４とベーン６の圧縮室側摺動部２２
に設けられ、ベーン６の往復運動方向における圧縮室側
摺動部２２の中央よりも反ローラ側に設けられた圧縮室
側油溜め部２６ｃと、吸入室側油溜め部２６ｂと圧縮室
側油溜め部２６ｃとを連通する連通孔２７とから構成さ
れているので、油面が低下した場合でも確実にベーン６
とシリンダ４間の摺動部２０、２２のうち、最大荷重が
作用する吸入室側摺動部２０と圧縮室側摺動部２２に同
等量の給油を行うことができる。したがって、ベーン６
とシリンダ４間の摩耗や焼付き及び摺動損失の増大を防
止し、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。As described above, the rotary compressor of this embodiment is
The suction chamber side sliding part 2 provided in the suction chamber side sliding part 20 of the cylinder 4 and the vane 6 in the reciprocating direction of the vane 6
Suction chamber side oil sump portion 26b provided on the roller 5 side with respect to the center of 0 and the compression chamber side sliding portion 22 of the cylinder 4 and the vane 6
, A compression chamber side oil sump portion 26c, a suction chamber side oil sump portion 26b, and a compression chamber side oil side, which are provided on the opposite roller side from the center of the compression chamber side sliding portion 22 in the reciprocating direction of the vane 6. Since it is composed of the communication hole 27 that communicates with the reservoir portion 26c, the vane 6 can be reliably operated even when the oil level is lowered.
Of the sliding parts 20, 22 between the cylinder 4 and the cylinder 4, the same amount of oil can be supplied to the suction chamber side sliding part 20 and the compression chamber side sliding part 22 on which the maximum load acts. Therefore, vane 6
It is possible to prevent abrasion between the cylinder 4 and the cylinder 4, seizure, and increase in sliding loss, thereby improving reliability and preventing a decrease in efficiency.
【００３７】[0037]
【発明の効果】以上説明したように本発明は、冷媒ガス
空間を有する密閉ケーシングと、密閉ケーシングの下部
に溜められた潤滑油と、密閉ケーシング内に収納される
シリンダと、シリンダの両端に固定された主軸受および
副軸受と、シリンダ内を偏心回転するローラと、シリン
ダの溝内を往復運動しローラと当接することによりシリ
ンダ内を吸入室と圧縮室に分割するベーンと、副軸受給
油部に密閉ケーシングの下部に溜められた潤滑油を供給
する給油機構と、シリンダの溝の吸入室側摺動部に設け
られた吸入室側潤滑油室と、シリンダの溝の圧縮室側摺
動部に設けられた圧縮室側潤滑油室と、一端が前記副軸
受給油部に開口し他端が吸入室側潤滑油室及び圧縮室側
潤滑油室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潤滑油を供給することができるた
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 hermetic casing having the refrigerant gas space, the lubricating oil accumulated in the lower portion of the hermetic casing, the cylinder housed in the hermetic casing, and the both ends of the cylinder are fixed. Main bearing and auxiliary bearing, a roller that eccentrically rotates in the cylinder, a vane that reciprocates in the groove of the cylinder and abuts against the roller to divide the cylinder into an intake chamber and a compression chamber, and an auxiliary bearing oil supply section Oil supply mechanism that supplies the lubricating oil stored in the lower part of the closed casing to the suction chamber side lubrication oil chamber provided in the suction chamber side sliding part of the cylinder groove, and the compression chamber side sliding part of the cylinder groove A lubricating oil chamber on the side of the compression chamber, and an oil supply path having one end opened to the oil supply portion for the auxiliary bearing and the other end communicating with the lubricating oil chamber on the suction chamber side and the lubricating oil chamber on the compression chamber side. From
Even when the reciprocating vane is no longer immersed in the lubricating oil due to the lowering of the lubricating oil level in the closed casing, the lubricating oil can be supplied to the sliding part of the vane from the oil supply mechanism. It is possible to prevent wear, seizure, deterioration of sealability, and increase of sliding loss due to poor lubrication, which improves reliability and prevents deterioration of efficiency.
【００３８】また、吸入室側潤滑油室と圧縮室側潤滑油
室とを連通する潤滑油の連通路を備えることにより、圧
縮室が高圧圧力Ｐdである場合においても吸入室側摺動
部と同等量の潤滑油を圧縮室側摺動部へ供給することが
できる。したがって、圧縮室側摺動部の潤滑性を向上で
き、摩耗や焼付き及びシール性の低下、摺動損失の増大
を防止し、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。Further, by providing a lubricating oil communication passage that connects the suction chamber side lubricating oil chamber and the compression chamber side lubricating oil chamber, even if the compression chamber is at a high pressure P d , the suction chamber side sliding portion is provided. It is possible to supply the same amount of lubricating oil to the sliding portion on the compression chamber side. Therefore, it is possible to improve the lubricity of the sliding portion on the compression chamber side, prevent wear, seizure, deterioration of sealing performance and increase of sliding loss, improve reliability and prevent deterioration of efficiency.
【００３９】また、シリンダとベーンの吸入室側摺動部
及び圧縮室側摺動部に油溜め部を有するベーンを備える
ことにより、ベーンとシリンダの摺動部全域にわたって
潤滑油を供給できる。したがって、油面が低下した場合
でもベーンとシリンダ間の摺動部全域の潤滑性を確保で
き、摩耗や焼付き及びシール性の低下、摺動損失の増大
を防止し、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。Further, by providing the vane having the oil reservoir on the suction chamber side sliding portion and the compression chamber side sliding portion of the cylinder and the vane, the lubricating oil can be supplied over the entire sliding portion of the vane and the cylinder. Therefore, even if the oil level drops, the lubricity of the entire sliding part between the vane and the cylinder can be secured, wear and seizure, a decrease in sealing performance, and an increase in sliding loss are prevented, and reliability is improved and It is possible to prevent a decrease in efficiency.
【００４０】また、シリンダとベーンの吸入室側摺動部
に設けられ、ベーン往復運動方向における吸入室側摺動
部の中央よりもローラ側に設けられた吸入室側油溜め部
と、シリンダとベーンの圧縮室側摺動部に設けられ、ベ
ーン往復運動方向における圧縮室側摺動部の中央よりも
反ローラ側に設けられた圧縮室側油溜め部と、吸入室側
油溜め部と圧縮室側油溜め部とを連通する連通孔とを備
えることにより、油面が低下した場合でも確実にベーン
とシリンダ間の摺動部のうち、最大荷重が作用する摺動
部に給油を行うことができる。したがって、ベーンとシ
リンダ間の摩耗や焼付き及び摺動損失の増大を防止し、
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。Further, a suction chamber side oil sump portion which is provided on the suction chamber side sliding portion of the cylinder and the vane, and which is provided on the roller side with respect to the center of the suction chamber side sliding portion in the vane reciprocating direction, and the cylinder. The compression chamber side oil sump portion, which is provided on the compression chamber side slide portion of the vane, is provided on the roller side rather than the center of the compression chamber side slide portion in the reciprocating direction of the vane, and the suction chamber side oil sump portion and the compression. By providing a communication hole that communicates with the chamber side oil sump, even if the oil level drops, it is possible to reliably supply oil to the sliding part of the sliding part between the vane and cylinder where the maximum load acts. You can Therefore, it is possible to prevent wear between the vane and the cylinder, seizure, and increase in sliding loss.
It is possible to improve reliability and prevent 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】本発明による回転式圧縮機の第２の実施例の要
部断面図FIG. 3 is a sectional view of an essential part of a second embodiment of the rotary compressor according to the present invention.
【図４】本発明による回転式圧縮機の第３の実施例の要
部断面図FIG. 4 is a sectional view of an essential part of a third embodiment of the rotary compressor according to the present invention.
【図５】本発明による回転式圧縮機の第４の実施例の要
部断面図FIG. 5 is a sectional view of the essential parts of a fourth embodiment of the rotary compressor according to the present invention.
【図６】従来の回転式圧縮機の縦断面図FIG. 6 is a vertical sectional view of a conventional rotary compressor.
【図７】図６のＢ−Ｂ線における断面図FIG. 7 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 吸入室側潤滑油室 ２０ 吸入室側摺動部 ２１ 圧縮室側潤滑油室 ２２ 圧縮室側摺動部 ２３ａ、２３ｂ 給油路 ２４ 副軸受給油部 ２５ａ 連通路 ２６ａ 油溜め部 ２６ｂ 吸入室側油溜め部 ２６ｃ 圧縮室側油溜め部 ２７ 連通孔 1 Airtight casing 1a Refrigerant gas space 4 Cylinder 4a Cylinder groove 5 Roller 6 Vanes 7 Main bearing 8 Secondary bearing 11a Suction chamber 11b Compression chamber 12 Oil supply mechanism 18 Lubricating oil 19 Suction chamber side lubricating oil chamber 20 Suction chamber side sliding part 21 Lubrication chamber side of compression chamber 22 Sliding parts on compression chamber side 23a, 23b Oil supply passage 24 Secondary bearing oil supply portion 25a Communication passage 26a Oil sump portion 26b Suction chamber side oil sump portion 26c Compression chamber side oil sump portion 27 Communication hole
Claims (4)
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、副軸受
給油部に前記密閉ケーシングの下部に溜められた潤滑油
を供給する給油機構と、前記シリンダの溝の吸入室側摺
動部に設けられた吸入室側潤滑油室と、前記シリンダの
溝の圧縮室側摺動部に設けられた圧縮室側潤滑油室と、
一端が前記副軸受給油部に開口し他端が前記吸入室側潤
滑油室及び前記圧縮室側潤滑油室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 groove of the cylinder to contact the roller. By doing so, a vane that divides the inside of the cylinder into an intake chamber and a compression chamber, an oil supply mechanism that supplies the auxiliary bearing oil supply unit with the lubricating oil that is stored in the lower portion of the closed casing, and the groove of the cylinder that slides on the intake chamber side A suction-chamber-side lubricating oil chamber provided in the section, a compression-chamber-side lubricating oil chamber provided in the compression-chamber-side sliding portion of the groove of the cylinder,
A rotary compressor having one end opened to the auxiliary bearing oil supply portion and the other end having an oil supply passage communicating with the suction chamber side lubricating oil chamber and the compression chamber side lubricating oil chamber.
を連通する連通路を備えた請求項１記載の回転式圧縮
機。2. The rotary compressor according to claim 1, further comprising a communication passage that connects the suction chamber side lubricating oil chamber and the compression chamber side lubricating oil chamber.
溜め部を有するベーンを備えた請求項１記載の回転式圧
縮機。3. The rotary compressor according to claim 1, wherein the suction chamber side sliding portion and the compression chamber side sliding portion each include a vane having an oil sump portion.
けられ、ベーン往復運動方向における前記吸入室側摺動
部の中央よりもローラ側に設けられた吸入室側油溜め部
と、前記シリンダと前記ベーンの圧縮室側摺動部に設け
られ、前記ベーン往復運動方向における圧縮室側摺動部
の中央よりも反ローラ側に設けられた圧縮室側油溜め部
と、前記吸入室側油溜め部と前記圧縮室側油溜め部とを
連通する連通孔とを備えた請求項１記載の回転式圧縮
機。4. A suction chamber side oil sump portion which is provided at a suction chamber side sliding portion of a cylinder and a vane, and which is provided closer to the roller than the center of the suction chamber side sliding portion in the vane reciprocating direction, A compression chamber side oil reservoir provided on the compression chamber side sliding part of the cylinder and the vane, and on the roller side rather than the center of the compression chamber side sliding part in the vane reciprocating direction, and the suction chamber side. The rotary compressor according to claim 1, further comprising a communication hole that connects the oil sump and the compression chamber side oil sump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14051393A JPH06346880A (en) | 1993-06-11 | 1993-06-11 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14051393A JPH06346880A (en) | 1993-06-11 | 1993-06-11 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06346880A true JPH06346880A (en) | 1994-12-20 |
Family
ID=15270401
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14051393A Pending JPH06346880A (en) | 1993-06-11 | 1993-06-11 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06346880A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009103067A (en) * | 2007-10-24 | 2009-05-14 | Panasonic Corp | Hermetic compressor |
| JP2021001607A (en) * | 2015-03-30 | 2021-01-07 | ハイコア テクノロジーズ インク．Ｈｉｃｏｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ，Ｉｎｃ． | Compressor having liquid injection cooling function |
| KR20210009695A (en) * | 2019-07-17 | 2021-01-27 | 엘지전자 주식회사 | Rotary compressor |
-
1993
- 1993-06-11 JP JP14051393A patent/JPH06346880A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009103067A (en) * | 2007-10-24 | 2009-05-14 | Panasonic Corp | Hermetic compressor |
| JP2021001607A (en) * | 2015-03-30 | 2021-01-07 | ハイコア テクノロジーズ インク．Ｈｉｃｏｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ，Ｉｎｃ． | Compressor having liquid injection cooling function |
| US11306722B2 (en) | 2015-03-30 | 2022-04-19 | Forums Us, Inc. | Compressor with mechanical seal |
| KR20210009695A (en) * | 2019-07-17 | 2021-01-27 | 엘지전자 주식회사 | Rotary compressor |
| US11486398B2 (en) | 2019-07-17 | 2022-11-01 | Lg Electronics Inc. | Rotary compressor with selective oil communication |
| US12146493B2 (en) | 2019-07-17 | 2024-11-19 | Lg Electronics Inc. | Rotary compressor with selective oil communication |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0622546B1 (en) | Rotary compressor with oil injection | |
| JP2006258002A (en) | Hermetic compressor | |
| JPH06346880A (en) | Rotary compressor | |
| JPH07293476A (en) | Rotary compressor | |
| JP7130133B2 (en) | Scroll compressor and refrigeration cycle equipment | |
| JPH08159071A (en) | Rotary compressor | |
| JP2769177B2 (en) | Rotary compressor | |
| JPH05141376A (en) | Rotary compressor | |
| JPH07247981A (en) | Rotary compressor | |
| JPH07293474A (en) | Rotary compressor | |
| KR100299589B1 (en) | Fluid appatus | |
| JP2604835B2 (en) | Rotary compressor | |
| JPH07119670A (en) | Vertical rotary compressor | |
| JPH0674171A (en) | Rotary compressor | |
| JPH04219486A (en) | Rotary compressor | |
| JPH07259766A (en) | Hermetic type compressor | |
| JPH07145792A (en) | Rotary type compressor | |
| JPH07293470A (en) | Rotary compressor | |
| JPH06147163A (en) | Rotary compressor | |
| JPH02191895A (en) | Rotary compressor | |
| JP2003293953A (en) | Reciprocating hermetic electric compressor | |
| JP3236366B2 (en) | Rotary compressor | |
| JPH04153594A (en) | rolling piston compressor | |
| JP2604818B2 (en) | Rotary compressor | |
| JPH07293469A (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20040701 |
|
| A131 | Notification of reasons for refusal |
Effective date: 20040720 Free format text: JAPANESE INTERMEDIATE CODE: A131 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20041116 |