JPH04143481A - Rotary compressor - Google Patents

Abstract

PURPOSE:To enhance the volume efficiency by providing a plurality of communicating parts leading from a concave step on the internal circumferential side of the roller end faces to another step on the internal circumferential side, furnishing a plurality of sealing parts which decrease the section area as going apart from these communicating parts, and forming grooves from these communicating part and sealing parts. CONSTITUTION:A roller 19 make revolution and a rotating round its own axis associate with rotation of a shaft 3, and thereby a spiral motion is generated. In grooves 20-27 on the end face 19a of this roller 19, those 20c, 21c, 23b-26b, 26c, 27c of the sealing parts 20b-27b, 20c-27c decrease the section area as going in the lubricant flowing direction as shown by the broken arrow, and an oil-hydraulic force is generated by the lubricant flowing in from a plurality of communicating parts 20a-27a. With the rotation component constituting the spiral motion of the roller 19, sealing parts 20b-27b, 20c decreasing the section are approx. in the circumferential direction are formed, so that an oil-hydraulic force due to wedge effect is generated in either direction of rotating round own axis. and the same magnitude of oil-hydraulic force is always generated in dispersed positions on the end faces 19a, 19b of the roller 19 so as to give well balanced condition.

Description

【発明の詳細な説明】 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１．特に体積効率が良好な機械部の構成に係わる。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a rotary compressor used in a refrigeration cycle, etc.1. In particular, it relates to the configuration of mechanical parts with good volumetric efficiency.

従来の技術 従来の構成を第３図、第４図、第６図、第６図を用いて
説明する。Prior Art A conventional configuration will be explained with reference to FIGS. 3, 4, 6, and 6.

１は密閉ケーシング、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６、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。1 is a sealed casing, 2 is an electric motor section, and shaft 3
Through the cylinder 4, roller 6, vane 6, main bearing 7,
It is connected to a mechanical part main body 9 constituted by a sub-bearing 8. The shaft 3 is a main shaft 3a.

副軸ｓｂ、及び主軸３ａ、副軸３ｂの軸芯からＥだけ偏
心したクランク３Ｃよりなる。また、シャフト３の中心
には穴３ｅが形成されると共にクランク３Ｃには給油孔
ｓｆ、給油溝３ｑが設けられている。１ｏはベーン背面
に設けられたスプリングである。１１ａ、１１ｂはシリ
ンダ４内で、ローラ６、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。ローラ６の主
軸受７、副軸受８と対向するそれぞれの端面５Ｍ。It consists of a subshaft sb, and a crank 3C eccentric by E from the axes of the main shaft 3a and subshaft 3b. Further, a hole 3e is formed in the center of the shaft 3, and an oil supply hole sf and an oil supply groove 3q are provided in the crank 3C. 1o is a spring provided on the back side of the vane. 11a and 11b are in the cylinder 4, a roller 6, a vane 6, a main bearing 7, and an auxiliary bearing 8.
It consists of a suction chamber and a compression chamber. Each end face 5M of the roller 6 faces the main bearing 7 and the sub-bearing 8.

／ ６ｂの内周側には内周側から外周側に向うに伴い断面積
が減少するテーパ５ｃ、６ｄが設けられている。１２は
、シャフト３と連結する給油機構でおる。１３は吸入管
であり、副軸受８、シリンダ４の吸入通路１４全介して
吸入室１１ａと連通している。１５は吐出孔であり吐出
弁１６を介して密閉ケーシング１内と連通している。１
７は吐出管であり密閉ケーシング１内に開放している。Tapers 5c and 6d whose cross-sectional area decreases from the inner circumferential side to the outer circumferential side are provided on the inner circumferential side of / 6b. 12 is an oil supply mechanism connected to the shaft 3. Reference numeral 13 denotes a suction pipe, which communicates with the suction chamber 11a through the sub-bearing 8 and the suction passage 14 of the cylinder 4. Reference numeral 15 denotes a discharge hole, which communicates with the inside of the sealed casing 1 via a discharge valve 16. 1
Reference numeral 7 denotes a discharge pipe that opens into the sealed casing 1.

１８は潤滑油である。18 is lubricating oil.

第６図の実線の矢印方向は、圧縮機運転中のある時点に
おけるローラ５の運動方向をまた破線の矢印方向は、ロ
ーラ６の運動によりローラの端面ｓａ、ｓｂを潤滑油１
８が流れる方向を示している。また、ｓｅ、ｓｆはロー
ラ６のテーパ５ｃ。The direction of the solid arrow in FIG. 6 indicates the direction of movement of the roller 5 at a certain point in time during compressor operation, and the direction of the dashed arrow indicates the direction in which the end surfaces sa and sb of the roller are coated with lubricating oil 1 due to the movement of the roller 6.
8 indicates the direction of flow. Further, se and sf are the taper 5c of the roller 6.

５ｄのうち、この破線の矢印方向に断面積を徐々に減少
する部位（ｓｆは図示せず）であり、６ｇ。Of 5d, this is the part whose cross-sectional area gradually decreases in the direction of the broken arrow (sf is not shown), and is 6g.

６ｈは、断面積を徐々に増加する部位（ｓｈは図示せず
）である。6h is a portion (sh is not shown) whose cross-sectional area is gradually increased.

次に回転式圧縮機の圧縮機構について説明する。Next, the compression mechanism of the rotary compressor will be explained.

冷却システム（図示せず）からの冷媒ガスは、吸入管１
３、吸入孔１４より導かれシリンダ４内の吸入室１１Ｍ
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。Refrigerant gas from the cooling system (not shown) is supplied to the suction pipe 1
3. Suction chamber 11M inside cylinder 4 led from suction hole 14
leading to. The refrigerant gas that has reached the suction chamber 11a is transferred to the shaft 3
The compression chamber 11b is partitioned by a roller 5 and a vane 6, which are rotatably housed in the crank 3C, and is gradually compressed by the rotational movement of the shaft 3 as the electric motor section 2 rotates.

圧縮された冷媒ガスは、吐出孔１６、吐出弁１６を介し
て密閉ケーシング１内に一旦吐出された後、吐出管１７
を介して冷却システムに吐出される。The compressed refrigerant gas is once discharged into the sealed casing 1 through the discharge hole 16 and the discharge valve 16, and then through the discharge pipe 17.
to the cooling system.

又、冷媒の溶は込んだ密閉ケーシング１内の高圧の潤滑
油１８Ｆｉ、、給油機構１２によｐシャフト３の穴３ｅ
に供給され、主軸受７と副軸受８との摺動部に供給され
ると共に、給油孔３（、給油溝３ｑよりクランク３Ｃと
ローラ５の内周側に供給され、ローラ端面６ａ、６ｂを
潤滑した後、吸入室１１ａ、圧縮室１１ｂに至り、その
後吐出孔１６より密閉ケーシング１内に吐出され、密閉
ケーシング１の下部に戻る。In addition, high-pressure lubricating oil 18Fi in the sealed casing 1 filled with refrigerant solution is supplied to the hole 3e of the p shaft 3 by the oil supply mechanism 12.
It is supplied to the sliding parts of the main bearing 7 and auxiliary bearing 8, and is also supplied to the inner circumferential side of the crank 3C and roller 5 from the oil supply hole 3 (and oil supply groove 3q), and the roller end faces 6a, 6b. After being lubricated, it reaches the suction chamber 11a and the compression chamber 11b, and is then discharged into the sealed casing 1 from the discharge hole 16, and returns to the lower part of the sealed casing 1.

このとき、ローラ６は、シャフト３の回転に伴い、クラ
ンク３Ｃのまわりを方向を考えながら自転し且つ、公転
運動を行い、この結果ローラ６上の一点の軌跡は、ら旋
状となる。従って、ローラ５の移動方向は、シャフト３
が回転する間に３６００近く変化することになるが例え
ばローラ６のら旋運動の運動方向が、第６図の矢印で示
す方向とすると、ローラ６の端面５ａ、５ｂにはテーパ
５ｃ。At this time, as the shaft 3 rotates, the roller 6 rotates and revolves around the crank 3C while considering the direction, and as a result, the locus of one point on the roller 6 becomes a spiral. Therefore, the moving direction of the roller 5 is the shaft 3
For example, if the direction of the spiral movement of the roller 6 is the direction shown by the arrow in FIG. 6, the end surfaces 5a and 5b of the roller 6 will have a taper 5c.

６ｄが設けられているためテーパ５ｃ、５ｄの中で５０
と６量の近傍部に流入する潤滑油１８のみが、内径側か
ら外径側に向うに従い断面が先細となりクサビ効果によ
り油圧力を発生することになる。（但し、ｔｓ　ｆ’　
はテーパ５ｄの５ｃ’とは反対の部位であシ、図示して
いない。）従って、チー／＜　６　ｃと６ｄの６ｅと５
ｆの近傍部の油圧力がバランスし、その結果ローラ６と
主軸受７、副軸受８間のクリアランスδ８とδｂがδ２
＝δｂとなる様にローラ５が保持される。ところで、ロ
ーラ端面５ａ、５ｂを介して、クランク３ｃ側から吸入
室１１ａ、圧縮室１１ｂに流入する冷媒の溶は込んだ潤
滑油の量は、クリアランスの３乗に比例する。従って、
δ８＋δｂ＝二定の場合、流入する量はδ６＝δｂのと
きに最小となり、その結果、テーパａｃ、ａｄを設ける
ことにより、体積効率が良好で効率の高い圧縮機が提供
される。6d is provided, so 50 in the tapers 5c and 5d.
Only the lubricating oil 18 flowing into the vicinity of the 6th volume has a tapered cross section from the inner diameter side toward the outer diameter side, and generates hydraulic pressure due to the wedge effect. (However, ts f'
is a portion of the taper 5d opposite to 5c' and is not shown. ) Therefore, Chi/< 6 c and 6d 6e and 5
The hydraulic pressure in the vicinity of f is balanced, and as a result, the clearances δ8 and δb between the roller 6, main bearing 7, and sub-bearing 8 become δ2.
The roller 5 is held so that = δb. Incidentally, the amount of lubricating oil dissolved in the refrigerant flowing into the suction chamber 11a and the compression chamber 11b from the crank 3c side via the roller end surfaces 5a and 5b is proportional to the cube of the clearance. Therefore,
When δ8+δb=2 constant, the inflow amount is minimum when δ6=δb, and as a result, by providing the tapers ac and ad, a highly efficient compressor with good volumetric efficiency is provided.

例えば、実公昭６１−２０３１７号公報にて示される。For example, it is shown in Japanese Utility Model Publication No. 61-20317.

発明が解決しようとする課題 この様な従来の溝造では、テーパに侵入する潤滑油のく
さび効果を利用しており、このくさび効果は、シャフト
の回転運動に伴うローラのら旋状の運動のうち公転運動
成分では発生するが、テーパが円周方向には断面積が変
化しないためにローラのクランクのまわ＃）ヲ回る自転
運動の成分に対しては、発生せずくさび効果が小さい。Problems to be Solved by the Invention Conventional groove construction uses the wedge effect of lubricating oil that enters the taper, and this wedge effect is caused by the spiral movement of the roller accompanying the rotational movement of the shaft. This occurs in the orbital motion component, but since the cross-sectional area of the taper does not change in the circumferential direction, it does not occur in the rotational motion component in which the roller rotates around the crank, and the wedge effect is small.

また、クサビ効果による油圧力の発生部位が、ローラの
端面上の一箇所のみであり、大部分の部位には、発生せ
ず、更に、テーパ部そのものが、円周方向に連通した形
状となっているために、くさび効果により発生した圧力
は円周方向に逃げることとなり、くさび効果による発生
圧力は低い。この結果、くさび効果によるローラの安定
性は十分とは言えず、従って体積効率の向上効果が少な
いとの課題があった。In addition, the hydraulic pressure generated by the wedge effect is only at one location on the end face of the roller, and does not occur at most locations, and furthermore, the tapered section itself has a shape that communicates in the circumferential direction. Therefore, the pressure generated by the wedge effect escapes in the circumferential direction, and the pressure generated by the wedge effect is low. As a result, the stability of the roller due to the wedge effect cannot be said to be sufficient, resulting in a problem that the effect of improving volumetric efficiency is small.

又、他の従来例として、ローラの端面に内周側から外周
側に至るに伴い輻が狭くなる数条の溝を設けたものがあ
るが、溝が内周側から外周側へまっすぐ伸びているか、
又は円周方向のどちらが一方へ同じ方向に傾いた曲線で
あるために、１回転中の自転方向が変化するローラの運
動に対して十分なくさび効果を発生することは難しく、
又、油圧力の発生部位が、ローラ上の一箇所となり、や
けりローラの安定性は十分とは言えない課題があった。In addition, as another conventional example, there is one in which several grooves are provided on the end surface of the roller, the convergence of which narrows from the inner circumference to the outer circumference, but the grooves extend straight from the inner circumference to the outer circumference. Is it there?
Or, because the curves are tilted in the same direction in the circumferential direction, it is difficult to generate a sufficient wedge effect for the movement of the roller whose rotation direction changes during one rotation.
In addition, the hydraulic pressure is generated at only one location on the roller, and there is a problem that the stability of the burn roller is not sufficient.

さらにローラの肉厚が厚い場合においては、ローラと軸
受端面との密着力が大きく、ローラと軸受端面が接触す
ると引き離すに十分な油圧力がくさび効果から得られず
体積効率が向上しない課題があった。Furthermore, when the rollers are thick, the adhesion between the rollers and the bearing end surfaces is large, and when the rollers and bearing end surfaces come into contact, sufficient hydraulic pressure cannot be obtained from the wedge effect to separate them, resulting in a problem in which volumetric efficiency is not improved. Ta.

本発明は上記従来例の欠点を解決するものであり、従来
以上に体積効率の向上を図ると共にロラ肉厚の厚い圧縮
機においても十分なくさび効果を発生し、吸入映や圧縮
室への冷媒の溶は込んだ潤滑油の流入量を最小に抑える
こと番目的としている。The present invention solves the above-mentioned drawbacks of the conventional example, and aims to improve the volumetric efficiency more than the conventional example, and also generates a sufficient wedge effect even in compressors with thick rollers, thereby reducing the flow of refrigerant into the suction and compression chambers. The objective is to minimize the amount of lubricating oil that enters the melt.

課題を解決するための手段 本発明は、ローラの端面の内周側にそれぞれ設けられた
内周側凹状の段差とローラの内周側の段差との連通部と
、略円周方向に伸び連通部より離れるに伴い断面積を減
少する複数の封止部とより形成される溝を備えたもので
ある。Means for Solving the Problems The present invention provides communication portions between the inner circumferential concave steps provided on the inner circumferential side of the end faces of the rollers and the inner circumferential steps of the rollers, which extend substantially in the circumferential direction and communicate with each other. It is provided with a groove formed by a plurality of sealing parts whose cross-sectional area decreases as the distance from the part increases.

作　　　用 本発明は上記した構成により、ローラのら粧運動のうち
自転運動の成分に対しては、どちらの方向に自転しても
溝に流入した潤滑油は断面積の小さい方向に流れ、必ず
溝の封止部のどちらかに油圧力を発生することとなり、
大きな雄圧力を発生することができる。また、油圧力の
発生部位は、それぞれのローラ端面で２箇所以上に分散
して発生することになる。更に、溝の封止部に流入した
潤滑油は逃げ場が無いので油圧力は高く維持できる。Effect: With the above-described configuration, the lubricating oil flowing into the groove flows in the direction of the smaller cross-sectional area regardless of which direction the roller rotates, so that the lubricating oil always flows in the direction of the smaller cross-sectional area. Hydraulic pressure will be generated in either of the sealing parts of the groove,
Can generate large male pressure. Furthermore, the hydraulic pressure is generated at two or more distributed locations on each roller end face. Furthermore, since the lubricating oil that has flowed into the sealing portion of the groove has no place to escape, the hydraulic pressure can be maintained at a high level.

さらにローラ肉厚の厚い場合においても、ローラ内周部
に内周側凹状となる段差を設けているため、ローラ端面
面積が小さくなり１．くさび効果により軸受面に対する
密着力よりも大きな油圧力が得られる。Furthermore, even when the roller is thick, the roller end surface area is reduced because the inner circumferential portion of the roller is provided with a step that is concave on the inner circumferential side. Due to the wedge effect, a hydraulic pressure greater than the adhesion force to the bearing surface can be obtained.

従って、両端面に発生する油圧力が大きく且っローラ端
面上に分散して発生し、発生した油圧力が高く維持でき
ることになり、ローラと主軸受及び副軸受間のクリアラ
ンスδ６とδｂが漏れの最も少ないδ６＝δｂにＩＭ実
に保持される。その結果圧縮室や吸入室へ流入するオイ
ルの量が減少し体積効率が向上すると共に漏れ損失が少
なくなる。Therefore, the hydraulic pressure generated on both end faces is large and distributed on the roller end face, and the generated hydraulic pressure can be maintained at a high level, and the clearances δ6 and δb between the roller and the main bearing and sub bearing are reduced to prevent leakage. IM is actually maintained at the minimum δ6=δb. As a result, the amount of oil flowing into the compression chamber and suction chamber is reduced, improving volumetric efficiency and reducing leakage loss.

実施例 以下実施例につき、第１図、第２図にて説明する。Example Examples will be explained below with reference to FIGS. 1 and 2.

尚、従来例と同一の部分は同一符号を付し説明を省略す
る。Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted.

１９はローラであり、従来と同様にシャフト３のクラン
ク３ｃに回転自在に保持されている。ローラ１９の端面
１９ａ、１９ｂには、内周側に内周部が凹状となる段差
１９ｃ、１９ｄが設けられており、さらに、溝２０〜２
４〜２７及び溝２８〜３２〜３５が同数だけ設けられて
いる。溝２０〜３５はローラ１９の内周側の段差１９Ｇ
、１９ｄとの連通部２０　ａ〜３５ａ及び円周方向に沿
って連通部２０ａ〜３５ａより伸び且つ連通部２０ａ〜
３５ａより離れるに伴い断面積を減少する封止部２０ｂ
〜３６ｂ及び２ｏＣ〜３５ｃにより形成されている。Reference numeral 19 denotes a roller, which is rotatably held by the crank 3c of the shaft 3 as in the conventional case. The end surfaces 19a and 19b of the roller 19 are provided with steps 19c and 19d on the inner periphery side, the inner periphery of which is concave, and grooves 20 to 2.
The same number of grooves 4 to 27 and grooves 28 to 32 to 35 are provided. The grooves 20 to 35 are the steps 19G on the inner circumferential side of the roller 19.
, 19d, and the communicating portions 20a to 35a extending from the communicating portions 20a to 35a along the circumferential direction.
Sealing portion 20b whose cross-sectional area decreases as it moves away from 35a
~36b and 2oC~35c.

かかる構成において、吸入管１３より吸入された冷媒ガ
スは、従来と同様に圧縮され吐出管１７より冷却システ
ムに吐出される。In this configuration, the refrigerant gas sucked through the suction pipe 13 is compressed in the same way as in the conventional case and is discharged from the discharge pipe 17 to the cooling system.

１だ、冷媒の溶は込んだ密閉ケーシング１内の高圧の潤
滑油１８も従来と同様に機械部本体９を潤滑するが、ロ
ーラ１９の内周側に流入した潤滑油１８は、ローラ１９
ａ、１９ｂを潤滑した後従来と同様に密閉ケーシングの
下部に戻る。1. The high-pressure lubricating oil 18 in the sealed casing 1 filled with refrigerant also lubricates the mechanical body 9 as in the past, but the lubricating oil 18 that has flowed into the inner circumferential side of the roller 19
After lubricating parts a and 19b, return to the lower part of the sealed casing as in the conventional case.

ローラ１９は、従来と同様にシャフト３の回転に伴い、
公転運動と自転運動を行い、この結果ローラ１９はら旋
運動を行う。このら旋運動のある瞬間の運動の方向を従
来と同様に実線の矢印方向とし、又ローラ１９の運動に
より潤滑油１８が流れる方向を破線の矢印方向とする。As the shaft 3 rotates, the roller 19 rotates as in the conventional case.
The roller 19 performs a revolution movement and an autorotation movement, and as a result, the roller 19 performs a spiral movement. The direction of this spiral motion at a certain moment is the direction of the solid line arrow, as in the conventional case, and the direction in which the lubricating oil 18 flows due to the movement of the roller 19 is the direction of the broken line arrow.

このとき、ローラ１９の端面１９ａ上の溝２゜〜２７で
は、封止部２０ｂ　〜２７　ｂ　、　２０ｃ　〜２７Ｃ
！のうち封止部２０Ｃ，２１ｃ、２３ｂ、２４ｂ。At this time, in the grooves 2° to 27 on the end surface 19a of the roller 19, the sealing parts 20b to 27b, 20c to 27C
! Among them, the sealing portions 20C, 21c, 23b, and 24b.

２５ｂ、２６ｂ、２６Ｇ　、２７ｃが、破線の矢印方向
で示す潤滑油１８の流れ方向に対して、断面積を減少す
ることとなＶ、連通部２０ａ〜２７ａより流入する潤滑
油１Ｂにより油圧力を発生する。25b, 26b, 26G, and 27c reduce the cross-sectional area with respect to the flow direction of the lubricating oil 18 indicated by the dashed arrow direction. Occur.

即ち、溝２０〜２７のうち、溝２２以外の溝では、封止
部２０ｂ　〜２７ｂ　、２０ｃ　〜２７ｃのどちらか一
方又は両方で油圧力が発生し、油圧力の発生位置が、従
来の一箇所だけと異なり、ローラ端面１９ａ上に分散さ
れる。又、端面１９ｂ上の溝２８〜３６においても、端
面１９ａ上の溝２０〜２了と同様に溝２２と対称位置溝
３０以外の溝で、封止部２８ｂ〜ｓｓｂ、２ｓｃ〜３６
ｃのどちらか一方又は両方で油圧が発生し、且つ油圧の
発生位置は、端面１９　ａと１９ｂで対称位置となる。That is, in the grooves 20 to 27 other than the groove 22, hydraulic pressure is generated in one or both of the sealing parts 20b to 27b and 20c to 27c, and the position of the hydraulic pressure generation is different from the conventional one point. Unlike in the case where the particles are separated from each other, they are dispersed on the roller end surface 19a. Also, in the grooves 28 to 36 on the end surface 19b, the sealing portions 28b to ssb, 2sc to 36 are located at grooves other than the groove 22 and the symmetrical groove 30, similar to the grooves 20 to 2 on the end surface 19a.
Hydraulic pressure is generated at one or both of the end faces 19a and 19b, and the positions at which the oil pressure is generated are symmetrical between the end faces 19a and 19b.

更に、ローラ１９のら旋運動を形成する自転成分におい
ては、略円周方向に断面積を減少する封止部２０ｂ〜３
５ｂ　、２０ｃ　、３５ｃを形成しているために、どち
らの自転方向に対してもクサビ効果による油圧力を発生
する。また油圧力は、封止部２ｏｂ〜３５ｂ、２ｏＣ〜
３５Ｃの近傍で発生するので油圧力の逃げ場がなく、油
圧力は高く保持される。従って、ローラ１９の端面１９
ａ。Furthermore, in the autorotation component forming the spiral motion of the roller 19, the sealing portions 20b to 3 whose cross-sectional area decreases in the substantially circumferential direction
5b, 20c, and 35c, hydraulic pressure is generated due to the wedge effect in either direction of rotation. In addition, the hydraulic pressure is
Since it occurs near 35C, there is no escape for the hydraulic pressure, and the hydraulic pressure is kept high. Therefore, the end surface 19 of the roller 19
a.

１９ｂＫは常に同じ大きさの油圧力が分散した位置に発
生しバランスすることになる。また、この油圧力は、自
転成分により発生する油圧力針と、油圧力が逃げず高く
保持される分だけ従来より高い油圧力となるため、ロー
ラ１９は、−回転中従来以上に確実にクリアランスδａ
；δｂの位置に保持され、体積効率が向上する。In 19bK, the same amount of hydraulic pressure is always generated at dispersed positions, resulting in a balance. In addition, this hydraulic pressure is higher than before due to the hydraulic pressure needle generated by the rotational component and the hydraulic pressure that does not escape and is kept high, so the roller 19 has a more secure clearance than before during rotation. δa
; It is held at the position of δb, and the volumetric efficiency is improved.

さらに、ローラ肉厚が厚い場合においても、ローラ１９
の内周側に内周側凹状となる段差１９Ｃ１１９ｄを設け
ているため、ローラ端面の面積を小さくできるため、ロ
ーラ端面１９ａ、１９ｂと主軸受７または副軸受８との
接触部における密着力をくさび効果による油圧力より弱
くでき、ローラが片面に寄ったまま回転することがなく
なる。Furthermore, even when the roller wall thickness is large, the roller 19
Since the step 19C119d that is concave on the inner circumferential side is provided, the area of the roller end face can be reduced, so that the adhesion force at the contact portion between the roller end faces 19a, 19b and the main bearing 7 or the sub bearing 8 is reduced. It can be made weaker than the hydraulic pressure caused by the effect, and the rollers will not rotate while being biased to one side.

このために、圧縮室や吸入室へ流入する潤滑油の量が減
少し体積効率が向上する。Therefore, the amount of lubricating oil flowing into the compression chamber and suction chamber is reduced, improving volumetric efficiency.

尚、本実施例においては、断面積の変化を溝巾にて行っ
たが、溝の深さで行っても良い。In this embodiment, the cross-sectional area was changed by changing the groove width, but it may also be changed by changing the groove depth.

発明の効果 以上の説明から明らかな様に本発明は、シリンダと、シ
リンダの端面に固定された主軸受及び副軸受と、主軸受
及び副軸受内を回転摺動し且つクランクを有するシャフ
トと、シャフトのクランクに自転自在に収納されたロー
ラと、ローラに当接し且つシリンダに設けられた溝内を
往復摺動するベーンと、ローラの内周側で主軸受及び副
軸受と対向する端面のそれぞれに設けられた内周側凹状
の段差とローラの内周側に設けられた段差との連通部、
および略円周方向に伸び連通部より離れるに伴い断面積
を減少する複数の封止部より形成される溝を備えたもの
であるから、ローラのら旋運動を形成する自転運動に対
しても油圧力が発生するために油圧力が高くなり、また
油圧力の発生部位はそれぞれの端面上の２．箇所以上に
分散して発生し、更に封止部に流入した潤滑油は逃げ場
がないので発生した油圧力を高く維持できることとなる
ので、ローラの端面と主軸受、副軸受間のクリアランス
を常に均等に保持することができ、漏れ損失が減少し体
積効率が向上する。Effects of the Invention As is clear from the above description, the present invention comprises a cylinder, a main bearing and a sub-bearing fixed to the end face of the cylinder, a shaft that rotates and slides within the main bearing and the sub-bearing and has a crank; A roller that is rotatably housed in the crank of the shaft, a vane that contacts the roller and slides back and forth in a groove provided in the cylinder, and an end face that faces the main bearing and sub-bearing on the inner circumferential side of the roller. a communication portion between a concave step provided on the inner circumferential side of the roller and a step provided on the inner circumferential side of the roller;
and a groove formed by a plurality of sealing portions that extend in the circumferential direction and decrease in cross-sectional area as they move away from the communication portion, so it is resistant to the rotational movement that forms the spiral movement of the roller. The hydraulic pressure increases due to the generation of hydraulic pressure, and the hydraulic pressure is generated at 2. on each end face. Since the lubricating oil that is generated dispersed over multiple locations and flows into the sealing part has no place to escape, the generated hydraulic pressure can be maintained high, so the clearance between the roller end face, main bearing, and sub-bearing is always equalized. This reduces leakage loss and improves volumetric efficiency.

さらにローラ肉厚が厚い場合においても、ロラの内周側
に設けられた段差により、ローラ端面の面積が小さくな
ることからローラ端面と軸受面とが接触した場合の密着
力をくさび効果による油圧力より弱くでき、ローラが片
面に寄ったまま回転することがなくなり、ローラ端面と
主軸受、副軸受間のクリアランスを均等に保持すること
ができ体積効率の高い圧縮機を供給することができる。Furthermore, even when the roller wall thickness is thick, the area of the roller end face is reduced due to the step provided on the inner circumference of the roller, so the hydraulic pressure due to the wedge effect reduces the adhesion force when the roller end face and bearing surface come into contact. It can be made weaker, the rollers do not rotate while being biased to one side, and the clearance between the roller end face, the main bearing, and the sub-bearing can be maintained evenly, and a compressor with high volumetric efficiency can be provided.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の一実施例を示す回転式圧縮機のローラ
の正面図、第２図は本発明の機械部の拡大断面図、第３
図は従来の回転技圧縮機の縦断面図、第４図は第３図の
ｙ　−■’線における矢視図、第５図は第３図の機械部
の拡大断面図、第６図は従来のローラ正面図である。 ３・・・・・・シャフト、３Ｃ・・・・・・クランク、
４・・・°°°シリンダ、６・・・・・・ベーン、７・
・・・・・主軸受、８・・・・・・副軸受、１９・・・
・・・ローラ、１９ａ、１９ｂ・・・・・・ローラ端面
、１９ｃ、１９ｄ・旧・・段差、２０〜２４〜２７．２
８〜３２〜３５・・・・・・溝、２０　ａ〜２４ａ〜２
７ａ　、２８ａ〜３２ａ〜３５ａ・・・・・・連通部、
２０ｂ〜２４ｂ　〜２７ｂ　、２０Ｃ〜２４ｃ〜２７Ｃ
。 ２８ｂ〜３２ｂ〜３５ｂ、２８ｃ〜３２ｃ〜３５ｃ・・
・・・・封止部。FIG. 1 is a front view of a roller of a rotary compressor showing an embodiment of the present invention, FIG. 2 is an enlarged sectional view of the mechanical part of the present invention, and FIG.
The figure is a longitudinal sectional view of a conventional rotary compressor, Figure 4 is a view along the y-■' line in Figure 3, Figure 5 is an enlarged sectional view of the mechanical part in Figure 3, and Figure 6 is FIG. 3 is a front view of a conventional roller. 3...Shaft, 3C...Crank,
4...°°° cylinder, 6... vane, 7.
...Main bearing, 8...Sub bearing, 19...
...Roller, 19a, 19b...Roller end face, 19c, 19d, old...Step, 20-24-27.2
8-32-35...Groove, 20a-24a-2
7a, 28a to 32a to 35a... communication part,
20b~24b~27b, 20C~24c~27C
. 28b~32b~35b, 28c~32c~35c...
...Sealing part.

Claims (1)

【特許請求の範囲】[Claims] シリンダと、前記シリンダの端面に固定された主軸受及
び副軸受と、前記主軸受及び副軸受内を回転摺動し且つ
クランクを有するシャフトと、前記シャフトのクランク
に自転自在に収納されたローラと、前記ローラに当接し
且つ前記シリンダに設けられた溝内を往復摺動するベー
ンと、前記ローラの内周側で前記主軸受及び副軸受と対
向する端面のそれぞれに設けられた内周側凹状の段差と
前記ローラの内周側に設けられた段差との連通部および
略円周方向に伸び前記連通部より離れるに伴い断面積を
減少する複数の封止部より形成される溝を備えた回転式
圧縮機。a cylinder; a main bearing and a sub-bearing fixed to an end surface of the cylinder; a shaft that rotates and slides within the main bearing and the sub-bearing and has a crank; and a roller that is rotatably housed in the crank of the shaft. , a vane that contacts the roller and slides back and forth in a groove provided in the cylinder; and an inner concave shape provided on each of the end faces facing the main bearing and the sub bearing on the inner circumference side of the roller. and a groove formed by a communication portion between the step and the step provided on the inner circumferential side of the roller, and a plurality of sealing portions extending approximately in the circumferential direction and decreasing in cross-sectional area as the distance from the communication portion increases. Rotary compressor.