JPH1026091A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPH1026091A JPH1026091A JP18026996A JP18026996A JPH1026091A JP H1026091 A JPH1026091 A JP H1026091A JP 18026996 A JP18026996 A JP 18026996A JP 18026996 A JP18026996 A JP 18026996A JP H1026091 A JPH1026091 A JP H1026091A
- Authority
- JP
- Japan
- Prior art keywords
- roller
- oil
- groove
- rotary compressor
- 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.)
- Granted
Links
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は冷凍冷蔵庫や空調機
等に用いられるロータリ圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used for a refrigerator-freezer or an air conditioner.
【０００２】[0002]
【従来の技術】ロータリ圧縮機はそのコンパクト性や構
造が簡単なことから、冷凍冷蔵庫や空調機などに多く使
用されている。圧縮機の主要構成部品であるベーンやロ
ーラなどの圧縮機構部は、例えば、川平著、密閉形冷凍
機（平成５年）第１４頁、図６．１に記載されている。2. Description of the Related Art Rotary compressors are widely used in refrigerators and refrigerators because of their compactness and simple structure. The compression mechanism such as vanes and rollers, which are main components of the compressor, is described in, for example, Kawahira, Hermetic Refrigerator (1993), page 14, FIG. 6.1.
【０００３】以下に、図６を用いて、従来のロータリ圧
縮機の構成及び動作について説明する。密閉容器内にあ
る圧縮機構部は、偏心部９を有するクランク軸１、クラ
ンク軸１を支える軸受、シリンダ２、ベーン３、及び前
記シリンダ２内で偏心回転するローラ４を有し、先端が
円筒状のベーン３はシリンダ２のベーン溝５内を往復動
し、かつその先端部は、スプリング６によるばね力及び
シリンダ２の内外の圧力差による力によって、ローラ４
の外周面に押し付けられて、ローラ４の外周部と接触摺
動し、シリンダ２内を吸入室７と吐出室８に分割してい
る。Ｏはシリンダ２とクランク軸１の中心であり、クラ
ンク軸１は中心Ｏからｅだけ偏心したＰを中心とする偏
心部９を有する。クランク軸１はＯを中心として回転
し、それに伴いクランク軸と一体となっている偏心部９
は偏心回転をする。偏心部９にはローラ４が嵌合されて
おり、電動機によりクランク軸１が回転してローラ４が
シリンダ２内を公転することにより、冷媒ガスを吸込口
１０から吸い込み、吐出口１１に圧縮しながら送る。吐
出口１１の冷媒ガスは吐出弁１２を通り冷凍サイクル側
に送られ、凝縮器、膨張弁、蒸発器を経て、再度圧縮機
の吸込口１０に戻ってくる。[0003] The configuration and operation of a conventional rotary compressor will be described below with reference to FIG. The compression mechanism in the closed container has a crankshaft 1 having an eccentric part 9, a bearing supporting the crankshaft 1, a cylinder 2, a vane 3, and a roller 4 eccentrically rotating in the cylinder 2, and the tip is a cylinder. The vane 3 reciprocates in the vane groove 5 of the cylinder 2, and the tip of the vane 3 is driven by the spring force of the spring 6 and the force caused by the pressure difference between the inside and outside of the cylinder 2.
And slides in contact with the outer peripheral portion of the roller 4 to divide the inside of the cylinder 2 into a suction chamber 7 and a discharge chamber 8. O is the center of the cylinder 2 and the crankshaft 1, and the crankshaft 1 has an eccentric portion 9 centered on P eccentric from the center O by e. The crankshaft 1 rotates about O, and accordingly, an eccentric portion 9 integrated with the crankshaft.
Rotates eccentrically. A roller 4 is fitted in the eccentric portion 9, and the crankshaft 1 is rotated by the electric motor so that the roller 4 revolves in the cylinder 2, thereby sucking the refrigerant gas from the suction port 10 and compressing the refrigerant gas into the discharge port 11. Send while. The refrigerant gas at the discharge port 11 is sent to the refrigeration cycle side through the discharge valve 12, and returns to the suction port 10 of the compressor again through the condenser, the expansion valve, and the evaporator.
【０００４】前記構成においては、ローラ４とベーン３
先端部との当接部では、おもに吸入冷媒中に含まれるオ
イルと、ベーン３とシリンダ２に設けられたベーン溝５
の隙間、あるいはローラ４の端面部の隙間を圧力差によ
り通過するオイルにより油膜が形成されていた。In the above configuration, the roller 4 and the vane 3
In the contact portion with the tip portion, the oil mainly contained in the suction refrigerant and the vane groove 5 provided in the vane 3 and the cylinder 2 are formed.
An oil film is formed by the oil passing through the gap of the roller 4 or the gap at the end face of the roller 4 due to the pressure difference.
【０００５】尚、前記密閉容器、クランク軸１を支える
軸受け、及び電動機は図示していない。[0005] The closed container, the bearing for supporting the crankshaft 1, and the electric motor are not shown.
【０００６】しかしながら、上記の従来の構成では、ベ
ーン３の先端部は円筒状曲面であり、ローラ４の外周面
も円筒面であるので、ベーン３とローラ４の接触状態は
等価的には小円筒と大円筒の接触となる。したがって、
接触状態は線接触状態で、接触面積が小さくなり、単位
面積当たりの荷重すなわち接触応力が大きくなり、ベー
ン３とローラ４の接触摺動条件は過酷なものとなる。However, in the above-mentioned conventional configuration, since the tip of the vane 3 is a cylindrical curved surface and the outer peripheral surface of the roller 4 is also a cylindrical surface, the contact state between the vane 3 and the roller 4 is equivalently small. The cylinder and the large cylinder come into contact. Therefore,
The contact state is a line contact state, in which the contact area decreases, the load per unit area, that is, the contact stress increases, and the contact sliding condition between the vane 3 and the roller 4 becomes severe.
【０００７】又、ローラ４の自転数もローラ４の内周面
と偏心部９との摺動抵抗と、ローラ４の外周面とベーン
３の先端との摺動抵抗の差などで決まるものであり、ロ
ーラ４の自転数は非常に不安定であり、一般にクランク
軸１の回転数を３５００ｒｐｍで運転した時、ローラの
自転数は数十〜数百ｒｐｍ程度である。このため、ベー
ン３の先端とローラ４の摺動面は、すべり速度が条件に
より変わり、不安定なすべり摺動となる。The number of rotations of the roller 4 is also determined by the sliding resistance between the inner peripheral surface of the roller 4 and the eccentric portion 9 and the sliding resistance between the outer peripheral surface of the roller 4 and the tip of the vane 3. The rotation speed of the roller 4 is very unstable, and generally, when the rotation speed of the crankshaft 1 is operated at 3500 rpm, the rotation speed of the roller is about several tens to several hundreds rpm. For this reason, the sliding speed of the leading end of the vane 3 and the sliding surface of the roller 4 changes depending on the conditions, resulting in unstable sliding.
【０００８】さらに、塩素を含まない代替冷媒、例えば
Ｒ１３４ａなどを用いた場合、摺動部の油膜が切れた場
合に著しく潤滑性が低下する問題があり、特にロータリ
圧縮機の場合油膜のできにくいローラ４外周とベーン３
先端との間で摩耗が生じやすいという問題があった。Further, when an alternative refrigerant containing no chlorine, such as R134a, is used, there is a problem that the lubricating property is remarkably reduced when the oil film of the sliding portion is broken, and in particular, it is difficult to form an oil film in a rotary compressor. Roller 4 circumference and vane 3
There is a problem that abrasion easily occurs with the tip.
【０００９】この問題点を解決するため、例えば特開平
７−２５９７６７号公報には、図７に示すようにクラン
ク軸１３及びその偏心部１４の内部を、給油通路１５か
ら偏心部１４の外径まで貫通した横孔１６と、前記偏心
部１４外径に前記横孔１６と連通して設けた油溝１７
と、ローラ１８の外周に設けた外周溝１９と、その外周
溝１９にローラ内径から貫通する孔２０と、前記外周溝
１９最深部に当該外周溝１９と平行に設けた油溝２１と
を設けたものが開示されている。To solve this problem, for example, Japanese Unexamined Patent Publication No. Hei 7-259767 discloses that the inside of the crankshaft 13 and its eccentric part 14 is moved from the oil supply passage 15 to the outside diameter of the eccentric part 14 as shown in FIG. And an oil groove 17 provided in the outer diameter of the eccentric portion 14 so as to communicate with the horizontal hole 16.
And an outer peripheral groove 19 provided on the outer periphery of the roller 18, a hole 20 penetrating from the roller inner diameter in the outer peripheral groove 19, and an oil groove 21 provided in the deepest portion of the outer peripheral groove 19 in parallel with the outer peripheral groove 19. Are disclosed.
【００１０】[0010]
【発明が解決しようとする課題】しかしながら、この構
成ではローラ１８とベーン２２の接触は面接触となると
共に、ローラ１８の自転も規制されるため安定な摺動条
件を実現できるが、ローラ１８とベーン２２の接触部へ
の給油は、ローラ内径から貫通する孔２０が給油通路１
５から偏心部外径に通じるように設けた横孔１６とは１
回転に１度だけ連通するだけのため、間欠給油となり十
分なオイルが供給されず、さらに偏心部１４とローラ１
８の内周との摺動部へ給油されるオイルが減少するなど
の欠点を有していた。However, in this configuration, the contact between the roller 18 and the vane 22 is a surface contact and the rotation of the roller 18 is restricted, so that a stable sliding condition can be realized. The oil is supplied to the contact portion of the vane 22 by a hole 20 penetrating from the roller inner diameter.
The horizontal hole 16 provided so as to communicate with the outer diameter of the eccentric part from 5 is 1
Since the oil is communicated only once with the rotation, the oil is intermittently supplied, and sufficient oil is not supplied.
8 has a disadvantage that the amount of oil supplied to the sliding portion with the inner periphery of the oil-injection No. 8 decreases.
【００１１】本発明は、上記従来の課題を考慮し、ベー
ンとローラの摺動部負荷が低減されると共に、ベーンと
ローラの摺動部へ十分なオイルが供給されることによ
り、信頼性が高く長寿命化したロータリ圧縮機を提供す
ることを目的とする。In view of the above-mentioned conventional problems, the present invention reduces the load on the sliding portion between the vane and the roller and supplies a sufficient amount of oil to the sliding portion between the vane and the roller, thereby improving reliability. An object of the present invention is to provide a rotary compressor having a long service life.
【００１２】[0012]
【課題を解決するための手段】この課題を解決するため
に本発明は、軸受部と偏心部を有するクランク軸、シリ
ンダ、Ｒ形状の先端を有するベーン、及び前記シリンダ
内で公転する管状のローラを有する圧縮機構部と、その
圧縮機構部を駆動する電動機部とを密閉容器内に備え、
前記ローラ外周には前記ベーン先端が当接配置される凹
溝部が設けられ、前記ローラの端面には第１の油溝が設
けられ、前記ローラにはその第１の油溝と前記ローラの
前記凹溝部を連通する油孔が設けられた構成としたもの
である。SUMMARY OF THE INVENTION To solve this problem, the present invention provides a crankshaft having a bearing portion and an eccentric portion, a cylinder, a vane having an R-shaped tip, and a tubular roller revolving in the cylinder. A compression mechanism unit having a motor unit that drives the compression mechanism unit is provided in a closed container,
The outer periphery of the roller is provided with a concave groove portion in which the tip of the vane is disposed in abutment, a first oil groove is provided on an end surface of the roller, and the first oil groove and the roller An oil hole communicating with the concave groove is provided.
【００１３】[0013]
【発明の実施の形態】以下、本発明の実施の形態につい
て、図１から図５を用いて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.
【００１４】（実施の形態１）図１は本発明の一実施例
のロータリ圧縮機の圧縮機構部の断面図であり、図２は
その要部斜視図である。図１及び図２において圧縮機構
部はクランクピン３２を有するクランク軸３１、シリン
ダ３３、先端がＲ形状のベーン３４、及びシリンダ３３
内で公転するローラ３５を有し、前記ローラ３５の外周
には凹溝３６が形成され、ベーン３４の先端が当接配置
されている。さらに、ローラ３５の端面には油溝３７及
び、横溝４０が設けられている。給油孔３９は、クラン
ク軸３１及びクランクピン３２の内部を、給油通路３８
からクランクピン３２の外周まで貫通しており、給油通
路３８からクランクピン３２の外周に導かれたオイル
は、ローラ３５端面とその上下のシリンダ側壁（図示せ
ず）との隙間及び、横溝４０により、油溝３７に導かれ
るように構成されている。また、油溝３７と前記ローラ
３５の凹溝３６とを連通するよう、縦油孔４１及び横油
孔４２が設けられている。(Embodiment 1) FIG. 1 is a sectional view of a compression mechanism section of a rotary compressor according to an embodiment of the present invention, and FIG. 2 is a perspective view of a main part thereof. 1 and 2, the compression mechanism includes a crankshaft 31 having a crankpin 32, a cylinder 33, a vane 34 having an R-shaped tip, and a cylinder 33.
The roller 35 revolves within the roller 35. A concave groove 36 is formed on the outer periphery of the roller 35, and the tip of the vane 34 is disposed in contact with the roller 35. Further, an oil groove 37 and a lateral groove 40 are provided on an end surface of the roller 35. The oil supply hole 39 is provided between the crankshaft 31 and the crankpin 32 so as to form an oil supply passage 38.
From the oil supply passage 38 to the outer periphery of the crankpin 32, the oil flows between the end face of the roller 35 and the upper and lower cylinder side walls (not shown) and the lateral groove 40. , And are guided to the oil groove 37. Further, a vertical oil hole 41 and a horizontal oil hole 42 are provided so as to communicate the oil groove 37 with the concave groove 36 of the roller 35.
【００１５】次に、本実施の形態における給油機構の動
作について説明する。オイルは給油通路３８より給油孔
３９を介してクランクピン３２の摺動部に導かれた後、
ローラ３５端面とその上下のシリンダ側壁（図示せず）
との隙間及び、ローラ３５の端面に設けられた横溝４０
を介して油溝３７に導かれ、さらに縦油孔４１、横油孔
４２を介してローラ３５の凹溝３６にほぼ連続的に導か
れる。Next, the operation of the oil supply mechanism in the present embodiment will be described. After the oil is guided from the oil supply passage 38 to the sliding portion of the crank pin 32 through the oil supply hole 39,
Roller 35 end surface and upper and lower cylinder side walls (not shown)
And a lateral groove 40 provided in the end face of the roller 35.
Through the vertical oil hole 41 and the horizontal oil hole 42 to the concave groove 36 of the roller 35 almost continuously.
【００１６】このように（実施の形態１）では、摺動条
件が厳しく摩耗が生じやすいベーンとローラの摺動部に
十分なオイルをほぼ連続的に供給することができ、油膜
形成も十分で、摺動負荷を低減できると共に、信頼性が
高く長寿命化したロータリ圧縮機を提供できるものであ
る。As described above, in the first embodiment, a sufficient amount of oil can be supplied almost continuously to the sliding portion of the vane and the roller where the sliding conditions are severe and wear is likely to occur, and the formation of the oil film is also sufficient. Further, it is possible to provide a rotary compressor which can reduce a sliding load and has a high reliability and a long life.
【００１７】（実施の形態２）図３は本発明の一実施例
のロータリ圧縮機の要部斜視図である。図３において油
溝４３はローラ３５の凹溝３６内に、凹溝３６とは平行
しない方向に沿って設けられている。また、その他の部
品構成は図１および図２と同一である。(Embodiment 2) FIG. 3 is a perspective view of a main part of a rotary compressor according to an embodiment of the present invention. In FIG. 3, the oil groove 43 is provided in the groove 36 of the roller 35 along a direction not parallel to the groove 36. Other components are the same as those shown in FIGS.
【００１８】次に、本実施の形態における給油機構の動
作について説明する。本実施の形態のように構成された
ロータリ圧縮機では、オイルは給油通路３８より給油孔
３９を介してクランクピン３２の摺動部に導かれた後、
ローラ３５端面とその上下のシリンダ側壁（図示せず）
との隙間及び、ローラ３５の端面に設けられた横溝４０
を介して油溝３７に導かれ、さらに縦油孔４１、横油孔
４２を介してローラ３５の凹溝３６内に設けた油溝４３
にほぼ連続的に導かれる。Next, the operation of the oil supply mechanism in the present embodiment will be described. In the rotary compressor configured as in the present embodiment, after the oil is guided from the oil supply passage 38 to the sliding portion of the crank pin 32 through the oil supply hole 39,
Roller 35 end surface and upper and lower cylinder side walls (not shown)
And a lateral groove 40 provided in the end face of the roller 35.
Through a vertical oil hole 41 and a horizontal oil hole 42, an oil groove 43 provided in the concave groove 36 of the roller 35.
Is almost continuously guided to
【００１９】このように（実施の形態２）では、ベーン
３４とローラ３５の摺動部のほぼ全域に渡って十分なオ
イルを供給することができ、油膜形成も十分で、摺動負
荷を低減できると共に、信頼性が高く長寿命化したロー
タリ圧縮機を提供できるものである。As described above, in the second embodiment, a sufficient amount of oil can be supplied to almost the entire sliding portion between the vane 34 and the roller 35, the oil film can be sufficiently formed, and the sliding load can be reduced. It is possible to provide a rotary compressor having high reliability and a long life.
【００２０】（実施の形態３）図４は本発明の一実施例
のロータリ圧縮機の要部斜視図である。図４においてベ
ーン３４の先端Ｒ形状の頂部には平坦面４４が形成され
ている。また、その他の部品構成は図１および図２と同
一である。(Embodiment 3) FIG. 4 is a perspective view of a main part of a rotary compressor according to an embodiment of the present invention. In FIG. 4, a flat surface 44 is formed on the top of the tip R shape of the vane 34. Other components are the same as those shown in FIGS.
【００２１】次に、本実施の形態における給油機構の動
作について説明する。本実施の形態のように構成された
ロータリ圧縮機では、オイルは給油通路３８より給油孔
３９を介してクランクピン３２の摺動部に導かれた後、
ローラ３５端面とその上下のシリンダ側壁（図示せず）
との隙間及び、ローラ３５の端面に設けられた横溝４０
を介して油溝３７に導かれ、さらに縦油孔４１、横油孔
４２を介してローラ３５の凹溝３６とベーン３４の先端
Ｒ形状の頂部に設けられた平坦面４４の隙間にほぼ連続
的に導かれる。Next, the operation of the oil supply mechanism in the present embodiment will be described. In the rotary compressor configured as in the present embodiment, after the oil is guided from the oil supply passage 38 to the sliding portion of the crank pin 32 through the oil supply hole 39,
Roller 35 end surface and upper and lower cylinder side walls (not shown)
And a lateral groove 40 provided in the end face of the roller 35.
Through the vertical oil hole 41 and the horizontal oil hole 42, and is substantially continuous with the gap between the concave groove 36 of the roller 35 and the flat surface 44 provided at the top of the tip R shape of the vane 34. Is guided by
【００２２】このように（実施の形態３）では、ベーン
３４とローラ３５の摺動部のほぼ全域に渡って十分なオ
イルを供給することができ、油膜形成も十分で、摺動負
荷を低減できると共に、信頼性が高く長寿命化したロー
タリ圧縮機を提供できるものである。As described above, in the third embodiment, a sufficient amount of oil can be supplied over almost the entire sliding portion between the vane 34 and the roller 35, and an oil film can be sufficiently formed to reduce the sliding load. It is possible to provide a rotary compressor having high reliability and a long life.
【００２３】（実施の形態４）図５は本発明の一実施例
のロータリ圧縮機の要部斜視図である。図５においてベ
ーン３４の先端Ｒ形状部には油溝４５が設けられてい
る。また、その他の部品構成は図１および図２と同一で
ある。(Embodiment 4) FIG. 5 is a perspective view of a main part of a rotary compressor according to an embodiment of the present invention. In FIG. 5, an oil groove 45 is provided in the tip R-shaped portion of the vane 34. Other components are the same as those shown in FIGS.
【００２４】次に、本実施の形態における給油機構の動
作について説明する。本実施の形態のように構成された
ロータリ圧縮機では、オイルは給油通路３８より給油孔
３９を介してクランクピン３２の摺動部に導かれた後、
ローラ３５端面とその上下のシリンダ側壁（図示せず）
との隙間及び、ローラ３５の端面に設けられた横溝４０
を介して油溝３７に導かれ、さらに縦油孔４１、横油孔
４２を介してローラ３５の凹溝３６とベーン３４の先端
Ｒ形状部に設けられた油溝４５にほぼ連続的に導かれ
る。Next, the operation of the oil supply mechanism in the present embodiment will be described. In the rotary compressor configured as in the present embodiment, after the oil is guided from the oil supply passage 38 to the sliding portion of the crank pin 32 through the oil supply hole 39,
Roller 35 end surface and upper and lower cylinder side walls (not shown)
And a lateral groove 40 provided in the end face of the roller 35.
Through the vertical oil hole 41 and the horizontal oil hole 42, and almost continuously to the concave groove 36 of the roller 35 and the oil groove 45 provided at the tip R-shaped portion of the vane 34. I will
【００２５】このように（実施の形態４）では、ベーン
３４とローラ３５の摺動部のほぼ全域に渡って十分なオ
イルを供給することができ、油膜形成も十分で、摺動負
荷を低減できると共に、信頼性が高く長寿命化したロー
タリ圧縮機を提供できるものである。As described above, in the fourth embodiment, a sufficient amount of oil can be supplied to almost the entire sliding portion between the vane 34 and the roller 35, the oil film can be sufficiently formed, and the sliding load can be reduced. It is possible to provide a rotary compressor having high reliability and a long life.
【００２６】尚、油溝３７はローラ３５の片側の端面に
限らず、上下両側の端面に設けてもよい。The oil groove 37 is not limited to one end face of the roller 35 but may be provided on both upper and lower end faces.
【００２７】又、横溝４０は一つに限らず、複数個設け
てもよい。The number of the lateral grooves 40 is not limited to one, and a plurality of lateral grooves may be provided.
【００２８】又、縦油孔４１及び横油孔４２は一つに限
らず、複数個設けてもよい。The number of vertical oil holes 41 and horizontal oil holes 42 is not limited to one, and a plurality of oil holes may be provided.
【００２９】又、塩素を含まない冷媒、例えばＨＦＣ１
３４ａを用いて運転してもよい。Further, a refrigerant containing no chlorine, for example, HFC1
34a may be used for operation.
【００３０】又、油溝３７は、本発明の第１の油溝、油
溝４３は本発明の第２の油溝、さらに油溝４５は本発明
の第３の油溝の一例である。The oil groove 37 is an example of the first oil groove of the present invention, the oil groove 43 is an example of the second oil groove of the present invention, and the oil groove 45 is an example of the third oil groove of the present invention.
【００３１】又、クランクピン３２は本発明の偏心部の
一例である。The crank pin 32 is an example of the eccentric part of the present invention.
【００３２】[0032]
【発明の効果】以上のように本発明によれば、信頼性の
高い長寿命化したロータリ圧縮機を提供することができ
る。As described above, according to the present invention, it is possible to provide a highly reliable and long-life rotary compressor.
【図１】本発明の実施の形態１、実施の形態２、実施の
形態３、実施の形態４によるロータリ圧縮機の圧縮機構
部の断面図FIG. 1 is a cross-sectional view of a compression mechanism of a rotary compressor according to a first, second, third, or fourth embodiment of the present invention.
【図２】本発明の実施の形態１、実施の形態２、実施の
形態３、実施の形態４によるロータリ圧縮機の要部斜視
図FIG. 2 is a perspective view of a main part of a rotary compressor according to Embodiments 1, 2, 3, and 4 of the present invention.
【図３】本発明の実施の形態２によるロータリ圧縮機の
要部斜視図FIG. 3 is a perspective view of a main part of a rotary compressor according to a second embodiment of the present invention.
【図４】本発明の実施の形態３によるロータリ圧縮機の
要部斜視図FIG. 4 is a perspective view of a main part of a rotary compressor according to a third embodiment of the present invention.
【図５】本発明の実施の形態４によるロータリ圧縮機の
要部斜視図FIG. 5 is a perspective view of a main part of a rotary compressor according to a fourth embodiment of the present invention.
【図６】従来のロータリ圧縮機の圧縮機構部の断面図FIG. 6 is a sectional view of a compression mechanism of a conventional rotary compressor.
【図７】従来のロータリ圧縮機の圧縮機構部の断面図FIG. 7 is a sectional view of a compression mechanism of a conventional rotary compressor.
３１ クランク軸 ３２ クランクピン ３３ シリンダ ３４ ベーン ３５ ローラ ３６ 凹溝 ３７ 第１の油溝 ４１ 縦油孔 ４２ 横油孔 ４０ 横溝 Reference Signs List 31 crankshaft 32 crankpin 33 cylinder 34 vane 35 roller 36 concave groove 37 first oil groove 41 vertical oil hole 42 horizontal oil hole 40 horizontal groove
───────────────────────────────────────────────────── フロントページの続き (72)発明者 西脇 文俊 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 新宅 秀信 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 長谷川 寛 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 鈴木 悦郎 大阪府東大阪市高井田本通４丁目２番５号 松下冷機株式会社内 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Fumitoshi Nishiwaki 1006 Kazuma Kadoma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. 72) Inventor Hiroshi Hasegawa 1006 Kadoma Kadoma, Kadoma City, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd.
Claims (10)
リンダ、Ｒ形状の先端を有するベーン、及び前記シリン
ダ内で公転する管状のローラを有する圧縮機構部と、そ
の圧縮機構部を駆動する電動機部とを密閉容器内に備
え、前記ローラ外周には前記ベーン先端が当接配置され
る凹溝部が設けられ、前記ローラの端面には第１の油溝
が設けられ、前記ローラにはその第１の油溝と前記ロー
ラの前記凹溝部を連通する油孔が設けられたことを特徴
とするロータリ圧縮機。1. A compression mechanism having a crankshaft having a bearing portion and an eccentric portion, a cylinder, a vane having an R-shaped tip, and a tubular roller revolving in the cylinder, and an electric motor driving the compression mechanism. And a groove in which the tip of the vane abuts is provided on the outer periphery of the roller, a first oil groove is provided on an end face of the roller, and the roller has a first oil groove. A rotary compressor, comprising: an oil hole that communicates the oil groove of (1) with the concave groove of the roller.
し、前記油孔は、前記第１の油溝と前記第２の油溝とを
連通する油孔であることを特徴とする請求項１記載のロ
ータリ圧縮機。2. A roller having a second oil groove in the concave groove portion of the roller, wherein the oil hole is an oil hole communicating the first oil groove and the second oil groove. The rotary compressor according to claim 1, wherein
し、前記油孔は、前記第１の油溝と、前記ベーン先端が
前記ローラの前記凹溝部に当接配置された場合に構成さ
れる、前記ローラの前記凹溝部と前記ベーンの先端のＲ
形状部分の平坦面との隙間とを連通する油孔であること
を特徴とする請求項１記載のロータリ圧縮機。3. A vane tip having a flat surface at an R-shaped portion, wherein the oil hole is provided when the tip of the vane and the vane tip are disposed in contact with the groove of the roller. R of the groove of the roller and the tip of the vane
The rotary compressor according to claim 1, wherein the rotary compressor is an oil hole that communicates with a gap between the flat portion and the flat surface of the shape portion.
を有し、前記油孔は、前記第１の油溝と、前記第３の油
溝とを連通する油孔であることを特徴とする請求項１記
載のロータリ圧縮機。4. An oil hole which has a third oil groove in an R-shaped portion at the tip of the vane, wherein the oil hole communicates with the first oil groove and the third oil groove. The rotary compressor according to claim 1, wherein:
方向に沿って設けられた油溝であることを特徴とする請
求項２記載のロータリ圧縮機。5. The rotary compressor according to claim 2, wherein the second oil groove is an oil groove provided along a direction not parallel to the concave groove portion.
面に設置されていることを特徴とする請求項１ないし４
記載いずれかのロータリ圧縮機。6. The roller according to claim 1, wherein said first oil groove is provided on both upper and lower end surfaces of said roller.
A rotary compressor according to any of the preceding claims.
求項１ないし４記載いずれかのロータリ圧縮機。7. The rotary compressor according to claim 1, wherein a plurality of oil holes are provided.
記ローラ内周までの横溝が設けられたことを特徴とする
請求項１ないし４記載いずれかのロータリ圧縮機。8. The rotary compressor according to claim 1, wherein a lateral groove extending from said first oil groove to an inner periphery of said roller is provided on an end surface of said roller.
求項１ないし４記載いずれかのロータリ圧縮機。9. The rotary compressor according to claim 1, wherein a plurality of lateral grooves are provided.
ことを特徴とする請求項１ないし４記載いずれかのロー
タリ圧縮機。10. The rotary compressor according to claim 1, wherein the rotary compressor is operated using a refrigerant containing no chlorine.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18026996A JP3600694B2 (en) | 1996-07-10 | 1996-07-10 | Rotary compressor |
| SG1997002415A SG53012A1 (en) | 1996-07-10 | 1997-07-09 | Rotary compressor |
| CN97114554A CN1105830C (en) | 1996-07-10 | 1997-07-10 | Rotary compressor |
| US08/891,155 US6132195A (en) | 1996-07-10 | 1997-07-10 | Rotary compressor |
| US09/664,311 US6409488B1 (en) | 1996-07-10 | 2000-09-18 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18026996A JP3600694B2 (en) | 1996-07-10 | 1996-07-10 | Rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1026091A true JPH1026091A (en) | 1998-01-27 |
| JP3600694B2 JP3600694B2 (en) | 2004-12-15 |
Family
ID=16080287
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18026996A Expired - Fee Related JP3600694B2 (en) | 1996-07-10 | 1996-07-10 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3600694B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010168976A (en) * | 2009-01-22 | 2010-08-05 | Panasonic Corp | Rotary compressor |
| JP2012233486A (en) * | 2012-09-06 | 2012-11-29 | Panasonic Corp | Rotary compressor |
| CN110319018A (en) * | 2019-04-28 | 2019-10-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor pump, compressor, air conditioner |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110836184B (en) * | 2018-08-17 | 2022-03-04 | Lg电子株式会社 | Rotary compressor |
-
1996
- 1996-07-10 JP JP18026996A patent/JP3600694B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010168976A (en) * | 2009-01-22 | 2010-08-05 | Panasonic Corp | Rotary compressor |
| JP2012233486A (en) * | 2012-09-06 | 2012-11-29 | Panasonic Corp | Rotary compressor |
| CN110319018A (en) * | 2019-04-28 | 2019-10-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor pump, compressor, air conditioner |
| CN110319018B (en) * | 2019-04-28 | 2023-11-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor pump body, compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3600694B2 (en) | 2004-12-15 |
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