JPS5851292A - Rotary fluid machine - Google Patents
Rotary fluid machineInfo
- Publication number
- JPS5851292A JPS5851292A JP15043881A JP15043881A JPS5851292A JP S5851292 A JPS5851292 A JP S5851292A JP 15043881 A JP15043881 A JP 15043881A JP 15043881 A JP15043881 A JP 15043881A JP S5851292 A JPS5851292 A JP S5851292A
- Authority
- JP
- Japan
- Prior art keywords
- groove
- rotor
- cylinder
- gap
- seal member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/08—Axially-movable sealings for working fluids
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、ロータリ一式流体機械に関し、特に、スライ
ディングベーン式ロータリー圧縮機のロータナイドクリ
アランスにおける流体の漏れ防止に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary fluid machine, and particularly to prevention of fluid leakage in a rotanide clearance of a sliding vane rotary compressor.
従来のスライディングベーン式圧縮機は、第1図に示す
通り、内部に円筒空間を有するシリンダ1と、このシリ
ンダ1内に偏心して回転l:iT能に設ケラれだロータ
2と、シリンダ1の両側面に固定され、シリンダ1の内
部空間である羽根室3をその側面において密閉し、ロー
タ2をニードルベアリング等の軸受で支持する側板(図
示せず)と、ロータ2に設けたスリット4に摺動可能に
係合されたべ一76より構成されている。6はシリンダ
1に形成された吸入孔、7はシリンダ1に形成された吐
出孔であり、シリンダ1の羽根室3を吐出側と吸入側に
隔てる個所がシリンダトップ8であるが、このようなロ
ータリーコンプレツナ−では、最も大きな圧力差を生じ
る吐出側と吸入側の境界であるトップ近傍のロータナイ
ドクリアランスにおいて、吐出側から吸入側へのガスの
漏れ(第1図の矢印六方向)が発生し、体積効率の低r
を招いた。As shown in Fig. 1, a conventional sliding vane compressor includes a cylinder 1 having a cylindrical space inside, a rotor 2 eccentrically installed in the cylinder 1 to rotate, and a rotor 2 installed in the cylinder 1 to rotate. Side plates (not shown) that are fixed to both sides, seal the blade chamber 3, which is the internal space of the cylinder 1, on the sides and support the rotor 2 with a bearing such as a needle bearing, and a slit 4 provided in the rotor 2. It consists of a member 76 that is slidably engaged. 6 is a suction hole formed in the cylinder 1, 7 is a discharge hole formed in the cylinder 1, and the cylinder top 8 is the part that separates the blade chamber 3 of the cylinder 1 into the discharge side and the suction side. In a rotary compressor, gas leaks from the discharge side to the suction side (in the six directions of arrows in Figure 1) at the rotanide clearance near the top, which is the boundary between the discharge side and suction side where the largest pressure difference occurs. generated and low volumetric efficiency r
was invited.
ロータナイドクリアランスを小さくすることにより、ロ
ータナイドでのガスの漏れ管を減少させることができる
が、ロータ2を側板において支持する、二〜ドルベアリ
ング等の軸受の剛性には限界があり、液圧縮又はガスの
過圧縮などによりロータに高い圧力がかかるため、ロー
タ2がわずかに傾いて、側板とロータ2が接触して、ト
ルク増加や焼き付きを起こす原因になる。よって、ロー
タナイドクリアランスを小さくすることには限度がある
。By reducing the rotanide clearance, gas leakage pipes in the rotanide can be reduced, but there is a limit to the rigidity of bearings such as two-dollar bearings that support the rotor 2 on the side plates, and liquid compression Alternatively, high pressure is applied to the rotor due to overcompression of gas, etc., which causes the rotor 2 to tilt slightly, causing contact between the side plate and the rotor 2, causing increased torque and seizure. Therefore, there is a limit to reducing the rotanide clearance.
本発明は上記問題点を改善するものであり、第2図〜第
4図にその一実施例を示す。両側板のロータ2との摺動
面に、第2図の長方形の破線で示す付近の位置に、例え
ば長方形の浅い溝9を形成し、溝9の深さよりも若干小
さい厚みと、溝9とほぼ同一形状で、溝9に容易に嵌合
できる程度の形状を有するシート状シール部材10をは
め、込むことにより、フローティングシールを形成スる
。The present invention is intended to improve the above-mentioned problems, and one embodiment thereof is shown in FIGS. 2 to 4. For example, a rectangular shallow groove 9 is formed in the sliding surface of the both side plates on the sliding surface with the rotor 2 at a position near the rectangular broken line shown in FIG. A floating seal is formed by fitting and inserting a sheet-like seal member 10 having substantially the same shape and a shape that can be easily fitted into the groove 9.
第3図aは、第2図のB−B断面を拡大したものである
。ロータ2.シー1シール部材101側板11で挾まれ
る隙間を、隙間12.隙間13゜隙間14及び隙間16
の四ケ所に分けて考えると、隙間12は吐出側に位置す
るために、吸入側に位置する隙間13よりも隙間12の
方が圧力が高くなる。従って、シール部材に、圧力差に
よる力F1が働き、シール部材1oは、溝9の吸入側の
端部16において溝9と接触する。そのため、隙間14
の圧力は、隙間12の圧力とほぼ等しくなり、隙間15
の圧力は、隙間12の圧力と隙間13の圧力の中間にな
る。よって、シール部材10には圧力差による力F2が
働き、シール部材10は、ロータ2へ押し付けられる。FIG. 3a is an enlarged view of the BB cross section in FIG. 2. Rotor 2. The gap between the sea 1 sealing member 101 and the side plate 11 is defined as the gap 12. Gap 13° Gap 14 and Gap 16
Considering the four locations, since the gap 12 is located on the discharge side, the pressure is higher in the gap 12 than in the gap 13 located on the suction side. Therefore, a force F1 due to the pressure difference acts on the sealing member, and the sealing member 1o comes into contact with the groove 9 at the suction side end 16 of the groove 9. Therefore, the gap 14
The pressure in the gap 12 is almost equal to the pressure in the gap 15.
The pressure in the gap 12 is between the pressure in the gap 12 and the pressure in the gap 13. Therefore, a force F2 due to the pressure difference acts on the seal member 10, and the seal member 10 is pressed against the rotor 2.
この様にして、隙間15を通して漏れるガスの量が減少
し、隙間12と13は高い圧力差を保つことができる。In this way, the amount of gas leaking through gap 15 is reduced and gaps 12 and 13 can maintain a high pressure difference.
また、ベーン6がロータ2から、熱膨張率の違い等によ
りわずかに突き出ている場合でも、ベーン5とシール部
材10が滑らかに摺動可能な様に、シール部材10の高
圧側の端部17を、例えば円弧状に厚みを変化させてお
く。Further, even if the vane 6 protrudes slightly from the rotor 2 due to a difference in coefficient of thermal expansion, the high-pressure side end 17 of the seal member 10 is designed so that the vane 5 and the seal member 10 can slide smoothly. For example, the thickness is changed in an arc shape.
なお、第3図a及び第4図の矢印Cは、ロータ側面の進
行方向を示す。Note that arrow C in FIGS. 3a and 4 indicates the direction of movement of the rotor side surface.
第3図すは、隙間15の圧力分布、第3図Cは、隙間1
4の圧力分布を示す説明である。第3図す及び第3図C
のPlは隙間13の圧力、P2は隙間12の圧力を示す
。Figure 3 shows the pressure distribution in the gap 15, Figure 3C shows the pressure distribution in the gap 1.
This is an explanation showing the pressure distribution of No. 4. Figure 3 S and Figure 3 C
Pl indicates the pressure in the gap 13, and P2 indicates the pressure in the gap 12.
第4図は本発明の他の実施例を示し、シール部材10が
、最初に、溝9の底面に密着した場合でも、隙間12か
ら隙間14へ、ガスが流れ込んで、圧力差による力F2
が生じるようにしたものであり、溝9の底面の、高圧側
の溝18を、他の部分より若干深く構成されている。従
って最初にシール部材10が溝9の底面に密着していて
も、まず、溝9の低面の高圧側の一部分18付近が隙間
12とほぼ等しい圧力になり、シール部材10がロータ
2の側へ押し付けられて、隙間14が生じる。FIG. 4 shows another embodiment of the present invention, in which even if the sealing member 10 first comes into close contact with the bottom surface of the groove 9, gas flows from the gap 12 to the gap 14, causing a force F2 due to the pressure difference.
The groove 18 on the high pressure side of the bottom surface of the groove 9 is configured to be slightly deeper than the other portions. Therefore, even if the sealing member 10 is initially in close contact with the bottom surface of the groove 9, the pressure near the high-pressure side portion 18 of the lower surface of the groove 9 becomes approximately equal to that of the gap 12, and the sealing member 10 is placed on the side of the rotor 2. , and a gap 14 is created.
第6図は更に別の実施例であり吐出側から吸入側への漏
れを防止するだめのフローティングシールの溝9の他に
、羽根室間の圧力差による冷媒の漏れを防止する位置、
即ち、第6図の矢印E方向の漏れに対して溝19の位置
に、矢印G方向の漏れに対して溝20の位置に、それぞ
れフローティングシールを用いるものである。溝19.
20に用いるフローティングシールは、リングの一部を
切断した形状のものや、9と同様の矩形状のものを隣接
して並べたものを用いることができる。FIG. 6 shows yet another embodiment in which, in addition to the groove 9 of the floating seal that prevents leakage from the discharge side to the suction side, there are also grooves 9 that prevent refrigerant from leaking due to the pressure difference between the blade chambers.
That is, a floating seal is used at the groove 19 for leakage in the direction of arrow E in FIG. 6, and at the groove 20 for leakage in the arrow G direction in FIG. Groove 19.
The floating seal used in 20 can be one in the shape of a partially cut ring, or one in which rectangular shapes similar to those in 9 are arranged adjacent to each other.
以上、本発明によれば、ロータと側板の隙間における、
高圧側から低圧側へのガスの漏れ量を減少させることに
より、圧縮機の体積効率を向上させることができる。As described above, according to the present invention, in the gap between the rotor and the side plate,
By reducing the amount of gas leaking from the high pressure side to the low pressure side, the volumetric efficiency of the compressor can be improved.
【図面の簡単な説明】
第1図は従来のロータリー圧縮機の正面断面図、第2図
は本発明の一実施例におけるロータリー圧縮機の正面断
面図、第3図(a)はg2図のB−B断面の拡大図、第
3図(b)及び第3図tc+は隙間の圧力分布を示す説
明図、第4図は他の実施例のシール部材を有した溝近傍
の断面図、第6図は更に別の実施例のロータリー圧縮機
の正面断面図である。
1 ・・・・・・シリンダ、2・・龜・・・ロータ、3
・・・・・・羽根室、5・・・・・・ベーン 8・・・
・・・シリンダトップ、9・・・−溝、1o・・・・・
・シール部材、11・Φ・・・・側板、12,13,1
4.15・・・・・・隙間、17・・・・・・シール部
材の高圧側端部、18・・・・・・高圧側の溝。
代理人の氏名 弁理士 中 尾 敏 男 ほか1名第1
図
第2図
第3図
(CLl
第3図[Brief Description of the Drawings] Fig. 1 is a front sectional view of a conventional rotary compressor, Fig. 2 is a front sectional view of a rotary compressor according to an embodiment of the present invention, and Fig. 3(a) is a front sectional view of a rotary compressor according to an embodiment of the present invention. An enlarged view of the B-B cross section, FIG. 3(b) and FIG. 3tc+ are explanatory diagrams showing the pressure distribution in the gap, FIG. FIG. 6 is a front sectional view of a rotary compressor according to yet another embodiment. 1...Cylinder, 2...Rotor, 3
...Blade chamber, 5...Vane 8...
...Cylinder top, 9...-groove, 1o...
・Seal member, 11・Φ・・・Side plate, 12, 13, 1
4.15...Gap, 17...High pressure side end of sealing member, 18...Groove on high pressure side. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 2 Figure 3 (CLl Figure 3
Claims (2)
ータ及び前記ベーンを収納するシリンダと、前記シリン
ダの両側面に固定され、前記ベーン、前記ロータ、前記
シリンダで形成される羽根室の空間をその側面において
密閉する側板よりなり、前記ロータと前記シリンダが最
も近接した個所をシリンダトップとするロータリ一式流
体機械において、前記側板前記シリンダトップ近傍の前
記ロータとの摺動面に、溝を形成し、前記溝に隙間を有
して嵌合可能な形状を有するシール部材を設けたロータ
リ一式流体機械。(1) A rotor on which a vane is slidably provided, a cylinder housing the rotor and the vane, and a blade chamber fixed to both sides of the cylinder and formed by the vane, the rotor, and the cylinder. In a rotary complete fluid machine consisting of a side plate that seals a space on its side surface, and in which the cylinder top is the point where the rotor and the cylinder are closest to each other, a groove is formed in a sliding surface between the side plate and the rotor near the cylinder top. and a sealing member having a shape that can be fitted into the groove with a gap therebetween.
ーパ状又は円弧状に厚みを形成した特許請求の範囲第1
項記載のロータリ一式流体機械。 (31前記溝の底部の高圧側部を深く形成した特許請求
の範囲第1項記載のロータリ一式流体機械。(2) The end portion of the sealing member located on the high pressure side is formed to have a tapered or arcuate thickness.
The rotary complete fluid machine described in Section 1. (31) The rotary complete fluid machine according to claim 1, wherein the high-pressure side of the bottom of the groove is formed deeply.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15043881A JPS5851292A (en) | 1981-09-21 | 1981-09-21 | Rotary fluid machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15043881A JPS5851292A (en) | 1981-09-21 | 1981-09-21 | Rotary fluid machine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5851292A true JPS5851292A (en) | 1983-03-25 |
Family
ID=15496927
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15043881A Pending JPS5851292A (en) | 1981-09-21 | 1981-09-21 | Rotary fluid machine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5851292A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59231187A (en) * | 1983-06-15 | 1984-12-25 | Nippon Denso Co Ltd | Vane type compressor |
JPS62164140A (en) * | 1986-01-14 | 1987-07-20 | インタ−ナショナル ビジネス マシ−ンズ コ−ポレ−ション | Testing of data processing system |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4949207A (en) * | 1972-05-12 | 1974-05-13 |
-
1981
- 1981-09-21 JP JP15043881A patent/JPS5851292A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4949207A (en) * | 1972-05-12 | 1974-05-13 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59231187A (en) * | 1983-06-15 | 1984-12-25 | Nippon Denso Co Ltd | Vane type compressor |
JPS62164140A (en) * | 1986-01-14 | 1987-07-20 | インタ−ナショナル ビジネス マシ−ンズ コ−ポレ−ション | Testing of data processing system |
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