JPS6119834B2 - - Google Patents
Info
- Publication number
- JPS6119834B2 JPS6119834B2 JP18397081A JP18397081A JPS6119834B2 JP S6119834 B2 JPS6119834 B2 JP S6119834B2 JP 18397081 A JP18397081 A JP 18397081A JP 18397081 A JP18397081 A JP 18397081A JP S6119834 B2 JPS6119834 B2 JP S6119834B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- eccentric
- shaft
- rolling piston
- amount
- 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.)
- Expired
Links
- 238000005096 rolling process Methods 0.000 claims description 18
- 238000005192 partition Methods 0.000 claims description 4
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
Description
【発明の詳細な説明】
この発明は、２シリンダ形ローリングピストン
式圧縮機において、シリンダの中心偏心方向と、
偏心量の設定に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention provides a two-cylinder rolling piston compressor in which the center eccentric direction of the cylinder,
This relates to setting the amount of eccentricity.
従来、この種の圧縮機においては、シリンダは
主軸の回転中心と同心に設定されていたが、性能
向上のため、シリンダとローリングピストンのク
リアランスを小さくして行く、ガス圧による回転
軸のたわみにより、ローリングピストンとシリン
ダが接触し、異常音発生や、ローリングピストン
と偏心部の焼付き等が発生する恐れがあつた。そ
れを防止するには、回転軸の剛性を上げるか、シ
リンダの中心を偏心させるかであるが、本発明は
回転軸の剛性はあまり上げず（運転中の最大荷重
時の回転軸のシリンダ内でのたわみ量が５μ以
上）にシリンダの中心を偏心させることにより、
実運転条件でのローリングピストンとシリンダの
クリアランスを最適にし、軽量でかつ効率のよい
圧縮機を提供することを目的とするものである。 Conventionally, in this type of compressor, the cylinder was set concentrically with the rotation center of the main shaft, but in order to improve performance, the clearance between the cylinder and rolling piston was reduced, and the deflection of the rotating shaft due to gas pressure There was a risk that the rolling piston and cylinder would come into contact, causing abnormal noise and seizure of the rolling piston and eccentric portion. To prevent this, either increase the rigidity of the rotating shaft or make the center of the cylinder eccentric, but the present invention does not increase the rigidity of the rotating shaft so much (the inside of the cylinder of the rotating shaft at the maximum load during operation). By eccentrically centering the cylinder so that the amount of deflection at
The objective is to optimize the clearance between the rolling piston and cylinder under actual operating conditions, and to provide a lightweight and efficient compressor.
以下、本発明を図示に示す実施例を用いて説明
する。 Hereinafter, the present invention will be explained using examples shown in the drawings.
回転軸がガス圧を受けるとそのガス圧と回転軸
偏心部の角度により回転軸のたわみ量が決定す
る。第１図および第２図はそのたわみかたを模式
的に示す図である。回転角は、駆動部に近い側の
偏心部(A)部を規準にする。又偏心方向は、２個の
偏心部のガス圧によるたわみ量より、第３図およ
び第４図のようにベーンから回転方向の120゜〜
150゜の範囲が適当である。なお、第１図および
第２図に示す実線は荷重を受けない時の軸の形状
で、破線は荷重を受けた時の軸の形状を示す。ま
た、第３図および第４図に示す破線は回転中心と
同心の場合のシリンダ位置を示し、実線は回転中
心と偏心させたときのシリンダの位置を示す。 When the rotating shaft receives gas pressure, the amount of deflection of the rotating shaft is determined by the gas pressure and the angle of the eccentric portion of the rotating shaft. FIG. 1 and FIG. 2 are diagrams schematically showing the way of deflection. The rotation angle is based on the eccentric part (A) on the side closer to the drive part. Also, the eccentric direction is determined by the amount of deflection due to the gas pressure of the two eccentric parts, as shown in Figures 3 and 4.
A range of 150° is appropriate. In addition, the solid line shown in FIGS. 1 and 2 shows the shape of the shaft when no load is applied, and the broken line shows the shape of the shaft when the load is applied. Further, the broken lines shown in FIGS. 3 and 4 indicate the cylinder position when the cylinder is concentric with the rotation center, and the solid line indicates the cylinder position when the cylinder is eccentric from the rotation center.
以下、本発明を第５図に示した実施例により説
明する。 The present invention will be explained below with reference to the embodiment shown in FIG.
図において、１は電動機等により駆動される偏
心軸、２はこの偏心軸の回転中心とベーン位置か
ら120゜〜150゜方向に20μ程度偏心して設けた圧
縮室３を形成するシリンダ、４は偏心軸に嵌合さ
れ、シリンダ２の内壁に沿つて偏心回転するロー
リングピストン、５は圧縮室３を高圧室と低圧室
に仕切るベーン、６は上記シリンダ２の片側サイ
ドを気密的に密着させるサイドハウジング、７は
２個のシリンダ２の圧縮室を仕切るための仕切り
板、８は圧縮室より吐出された高圧ガスを蓄え、
圧縮機本体を収容する密閉シエル、９はベーン５
をローリングピストン４に圧設させるバネであ
る。 In the figure, 1 is an eccentric shaft driven by an electric motor, etc., 2 is a cylinder that forms a compression chamber 3, which is provided eccentrically by about 20μ in the direction of 120° to 150° from the center of rotation of this eccentric shaft and the vane position, and 4 is an eccentric shaft. A rolling piston is fitted onto the shaft and rotates eccentrically along the inner wall of the cylinder 2; 5 is a vane that partitions the compression chamber 3 into a high pressure chamber and a low pressure chamber; 6 is a side housing that airtightly fits one side of the cylinder 2; , 7 is a partition plate for partitioning the compression chambers of the two cylinders 2, 8 is a partition plate for storing high pressure gas discharged from the compression chamber,
A sealed shell that houses the compressor body, 9 is the vane 5
This is a spring that presses the rolling piston 4 into place.
次に、以上のように構成された圧縮機の動作に
ついて説明する。駆動源により偏心軸１が回転す
ると、ローリングピストン４はシリンダ２の内壁
に沿つて転動し、吸入口（図示せず）より導びか
れた圧縮室３内のガスは圧縮され、吐出バルブ
（図示せず）部を通り、シエル内の空間に導びか
れる。そして、吐出パイプ（図示せず）を介して
外部へ吐出される。 Next, the operation of the compressor configured as above will be explained. When the eccentric shaft 1 is rotated by the drive source, the rolling piston 4 rolls along the inner wall of the cylinder 2, and the gas in the compression chamber 3 led from the suction port (not shown) is compressed, and the discharge valve ( (not shown) and is guided into the space within the shell. Then, it is discharged to the outside via a discharge pipe (not shown).
この際、高圧室と低圧室の圧力差によりローリ
ングピストンを介して、偏心軸が荷重およびベー
ンの背圧によつて荷重を受ける。荷重を受けた偏
心軸は、たわみを起こし、その結果シリンダと偏
心軸が同心であるとするとローリングピストンと
シリンダのラジアル方向クリアランス１０は、Ａ
部、Ｂ部と互いの影響により約15゜〜約195゜の
所で小ささくなり、195゜〜15゜の所で大きくな
る。本実施例では最大たわみ20μ程度である。し
かし、本発明は120゜〜150゜方向にシリンダが20
μ程度偏心しているため、一回転あたりのラジア
ルクリアランス１０は本実施例では最大20μ〜最
小０μとなり、ガスの漏れに対して良好となる。
しかし従来のように、偏心軸とシリンダを同心に
した場合シリンダとローリングピストンとが接触
しないようにするには、一回転中のシリンダとロ
ーリングピストンとのラジアルクリアランスが最
大40μ〜最小０μとなる。但し、一般的にはシリ
ンダの偏心量は、ガス荷重、ベーンからの荷重、
偏心軸の軸径、剛性等により求まるものである。
しかし、偏心方向は、常に一定（クランク角度で
120゜〜150゜）である。したがつてこの発明は実
用上、偏心軸の運転時のたわみ量（シリンダ内で
の）が５μ以上の場合に適用できるものである。
すなわち、たわみ量が５μ以下の場合には、偏心
組立をした場合と同心組立をした場合圧縮機の性
能は大差は生じないためである。 At this time, the eccentric shaft receives a load due to the pressure difference between the high pressure chamber and the low pressure chamber and the back pressure of the vane via the rolling piston. The eccentric shaft under load will deflect, so that if the cylinder and eccentric shaft are concentric, the radial clearance 10 between the rolling piston and the cylinder will be A
Due to the mutual influence of parts B and B, it becomes smaller between about 15° and about 195°, and becomes larger between 195° and 15°. In this embodiment, the maximum deflection is about 20μ. However, in the present invention, the cylinder is
Since it is eccentric by about μ, the radial clearance 10 per rotation is a maximum of 20 μ to a minimum of 0 μ in this embodiment, which is good against gas leakage.
However, in order to prevent the cylinder from coming into contact with the rolling piston when the eccentric shaft and the cylinder are made concentric as in the prior art, the radial clearance between the cylinder and the rolling piston during one revolution is a maximum of 40μ to a minimum of 0μ. However, in general, the eccentricity of the cylinder is determined by the gas load, the load from the vane,
It is determined based on the shaft diameter, rigidity, etc. of the eccentric shaft.
However, the eccentric direction is always constant (depending on the crank angle).
120° to 150°). Therefore, the present invention can be practically applied when the amount of deflection (in the cylinder) of the eccentric shaft during operation is 5 μ or more.
That is, when the amount of deflection is 5 μ or less, there is no significant difference in compressor performance between eccentric assembly and concentric assembly.
この発明は、以上述べたように構成したから、
偏心軸の剛性を上げる必要がないので重量軽減、
小形化を計ることができるとともにラジアルクリ
アランスをシリンダの偏心量によりコントロール
するため、圧縮効率向上など実用的効果大であ
る。 Since this invention is configured as described above,
There is no need to increase the rigidity of the eccentric shaft, reducing weight.
Since it can be made smaller and the radial clearance is controlled by the eccentricity of the cylinder, it has great practical effects such as improved compression efficiency.
第１図ないし第４図は本発明の動作説明図、第
５図は本発明の実施例を示す２シリンダ形ローリ
ングピストン式圧縮機の断面図である。
１は偏心軸、２はシリンダ、４はローリングピ
ストン、５はベーンである。
1 to 4 are explanatory diagrams of the operation of the present invention, and FIG. 5 is a sectional view of a two-cylinder rolling piston compressor showing an embodiment of the present invention. 1 is an eccentric shaft, 2 is a cylinder, 4 is a rolling piston, and 5 is a vane.
Claims (1)
と、この軸の回転中心と偏心した２個のシリンダ
と、この軸の偏心部の外周に接し、各シリンダの
内壁に沿つて軸動する２個のローリングピストン
と、このローリングピストンの外周部に接して、
シリンダ内部を高圧室と低圧室に仕切る２個のベ
ーンとを備えた２シリンダ形ローリングピストン
式圧縮機において、シリンダの偏心方向をベーン
を収納する溝中心を０゜としたとき、偏心軸の回
転方向に角度で120゜〜150゜間にし、その偏心量
を偏心軸のシリンダ内区間での最大たわみ量と必
要ラジアルクリアランス量で設定したことを特徴
とする２シリンダ形ローリングピストン式圧縮
機。1 A shaft with two eccentric parts that are 180 degrees out of phase, two cylinders that are eccentric to the center of rotation of this shaft, and a shaft that touches the outer periphery of the eccentric part of this shaft and moves along the inner wall of each cylinder. Two rolling pistons and in contact with the outer periphery of this rolling piston,
In a two-cylinder rolling piston compressor equipped with two vanes that partition the inside of the cylinder into a high-pressure chamber and a low-pressure chamber, when the eccentric direction of the cylinder is set at 0° from the center of the groove that houses the vanes, the rotation of the eccentric shaft is A two-cylinder rolling piston compressor, characterized in that the angle in the direction is between 120° and 150°, and the amount of eccentricity is set by the maximum deflection amount of the eccentric shaft in the cylinder section and the required radial clearance amount.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18397081A JPS5885389A (en) | 1981-11-17 | 1981-11-17 | Rolling piston type compressor with two cylinders |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18397081A JPS5885389A (en) | 1981-11-17 | 1981-11-17 | Rolling piston type compressor with two cylinders |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5885389A JPS5885389A (en) | 1983-05-21 |
| JPS6119834B2 true JPS6119834B2 (en) | 1986-05-19 |
Family
ID=16145005
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18397081A Granted JPS5885389A (en) | 1981-11-17 | 1981-11-17 | Rolling piston type compressor with two cylinders |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5885389A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5006051A (en) * | 1987-12-03 | 1991-04-09 | Kabushiki Kaisha Toshiba | Rotary two-cylinder compressor with delayed compression phases and oil-guiding bearing grooves |
| JP2005240564A (en) * | 2004-02-24 | 2005-09-08 | Mitsubishi Electric Corp | Rotary compressor |
| US9267503B2 (en) | 2009-09-10 | 2016-02-23 | Caire Inc. | Rotary systems lubricated by fluid being processed |
| CN102812208A (en) | 2009-09-10 | 2012-12-05 | 查特赛科技术有限公司 | Rotary Compressor And Method |
| CN109026698B (en) * | 2018-08-08 | 2019-09-03 | 珠海凌达压缩机有限公司 | A kind of compressor |
-
1981
- 1981-11-17 JP JP18397081A patent/JPS5885389A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5885389A (en) | 1983-05-21 |
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