JPS58217791A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPS58217791A JPS58217791A JP9961182A JP9961182A JPS58217791A JP S58217791 A JPS58217791 A JP S58217791A JP 9961182 A JP9961182 A JP 9961182A JP 9961182 A JP9961182 A JP 9961182A JP S58217791 A JPS58217791 A JP S58217791A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- motor
- piston
- compression chamber
- vanes
- 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
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
- 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
- F04C18/3566—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 more than line or surface
Abstract
Description
【発明の詳細な説明】
本発明は冷凍装置等に使用する回転型圧縮機に関し、2
個の吐出孔における吐出行程の位相をずらすことにより
、吐出圧力変動のピストンに対する合成成分を小さくす
ることにより、モータのトルク負荷・トルク変動の減少
によるモータの小型化及び振動の低減及び、吐出管系の
圧力脈動による損失の減少による効率向上を計ることを
目的と2ベーミf
するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary compressor used in refrigeration equipment, etc.
By shifting the phase of the discharge stroke in each discharge hole and reducing the composite component of discharge pressure fluctuations for the piston, the motor can be made smaller and vibrations can be reduced by reducing the motor torque load and torque fluctuation, and the discharge pipe The objective is to improve efficiency by reducing losses due to pressure pulsations in the system.
第4図に示す様に従来の回転型圧縮機aは各吐出孔す、
cが回転軸dに対して、対称に配置しであるため、各吐
出孔す、cからの圧縮動作流体の吐出は同位相で行われ
、また、ピストンeも回転軸dに対して軸対称であるた
め、第5図に示されるが如くピストンeに対する各圧縮
室f、g内の変動圧力は相加されるため、ピストンeに
対する圧力変動分は倍加される。従ってモータのトルク
負荷やトルク変動が大きくなり、また吐出管系の圧力脈
動も増加する傾向にあり配管振動、強度面の問題も生じ
ていた。As shown in Fig. 4, in a conventional rotary compressor a, each discharge hole is
Since c is arranged symmetrically with respect to the rotation axis d, the compressed working fluid is discharged from each discharge hole c in the same phase, and the piston e is also axially symmetrical with respect to the rotation axis d. Therefore, as shown in FIG. 5, the pressure fluctuations in the compression chambers f and g relative to the piston e are added, so that the pressure fluctuation relative to the piston e is doubled. Therefore, the torque load and torque fluctuation of the motor become large, and the pressure pulsations in the discharge pipe system also tend to increase, causing problems in terms of pipe vibration and strength.
本発明は、上記の欠点に鑑み、ベーン位置を、軸対称か
らずらし、圧縮動作流体の吐出される位相をずらすこと
により、前記ピストンに対する圧力変動の低減を図るも
のである。In view of the above-mentioned drawbacks, the present invention aims to reduce pressure fluctuations against the piston by shifting the vane position from axial symmetry and shifting the discharge phase of the compressed working fluid.
以下本発明の一実施例を第1図〜第3図を参照しながら
詳細に説明する。An embodiment of the present invention will be described in detail below with reference to FIGS. 1 to 3.
1は電動圧縮要素2を収納する密閉ケースで、3は電動
機要素、4は圧縮要素である。5は清ら3ペー〕゛
かな曲線にて、2つの頂部5aが均等位置に配設された
円状の形状をなすピストンであり、6はピストン5を固
定したシャフトで、電動機要素4と連結されている。こ
のシャフト6は円形断面を有するシリンダ7の上下部に
固定して配設された上軸受8及び下軸受9によって回転
自在に装着されている。さらにシリンダ7内に位置する
ピストン5はシャフト6と同心であシ、ピストン5の各
頂部5aにてシリンダ70円周面と一定の隙間を保持し
ながら回転運動を行う。2個のベーン10゜11の先端
は後部に設置したスプリング12によりピストン5と接
触するようシリンダ7に設けた溝7a、了す内に摺動自
在に組み込丑れており、ベーン11はベーン10と回転
軸に対して対称な位置より30°回転方向に進んだ位置
に配置しである。吐出孔13.14及び吸入孔15.1
6は各々、各ベー710.11の両側に近接して設置さ
れている。Reference numeral 1 designates a closed case that houses an electric compression element 2, 3 a motor element, and 4 a compression element. 5 is a circular piston with a straight curve and two tops 5a arranged at equal positions; 6 is a shaft to which the piston 5 is fixed, and is connected to the electric motor element 4; has been done. This shaft 6 is rotatably mounted by an upper bearing 8 and a lower bearing 9 fixedly disposed at the upper and lower parts of a cylinder 7 having a circular cross section. Furthermore, the piston 5 located within the cylinder 7 is concentric with the shaft 6, and rotates while maintaining a constant gap from the circumferential surface of the cylinder 70 at each top 5a of the piston 5. The tips of the two vanes 10 and 11 are slidably installed in a groove 7a provided in the cylinder 7 so that they come into contact with the piston 5 by means of a spring 12 installed at the rear. 10 and is arranged at a position 30 degrees further in the rotational direction than the symmetrical position with respect to the rotation axis. Discharge hole 13.14 and suction hole 15.1
6 are each located close to each side of each bay 710.11.
かかる構成において、ピストン5がシャフト6を介して
電動機要素3によシ回転すると、シリンダ7の内周面と
ピストン5の外周面にて四重れる空間はベーン10,1
1により圧縮室1了a。In this configuration, when the piston 5 is rotated by the electric motor element 3 via the shaft 6, the space overlapped by the inner circumferential surface of the cylinder 7 and the outer circumferential surface of the piston 5 becomes the vane 10,1.
1 allows the compression chamber to open.
17bと吸入室18a、18bに区切られ圧縮仕事を行
う。この時ベーン11はベーン10と回転軸に対して対
称な位置より3o0回転方向に進んだ位置に設けられて
いるために、第3図に示す如く、各圧縮室17a 、
17bにおける圧縮動作流体の変動圧力のピークの位相
はずれ、圧縮室17d。It is divided into suction chamber 17b and suction chambers 18a and 18b to perform compression work. At this time, since the vane 11 is provided at a position 3o0 forward in the rotation direction from a position symmetrical to the vane 10 with respect to the rotation axis, each compression chamber 17a,
The peak of the fluctuating pressure of the compressed working fluid in 17b is out of phase in the compression chamber 17d.
17bのどちらか一方の圧力が急激に減少している時に
、他方の圧力は急激に増加するため、ピストン5に対す
る合成変動圧力のピークは、従来例に比べて著しるしく
低減する。従って、モータのトルク負荷やトルク変動は
低減し、吐出管系の圧力脈動も低減するため、モータの
小型化、回転方向の振動の低減、及び吐出管系の損失減
少による効率向上を計ることができる。When the pressure of either one of the pistons 17b is rapidly decreasing, the pressure of the other is rapidly increasing, so the peak of the resultant fluctuating pressure on the piston 5 is significantly reduced compared to the conventional example. Therefore, the torque load and torque fluctuations on the motor are reduced, and the pressure pulsations in the discharge piping system are also reduced, making it possible to improve efficiency by downsizing the motor, reducing vibration in the direction of rotation, and reducing losses in the discharge piping system. can.
以上のように本発明は、円形断面を有するシリンダと、
外周面上に均等に分配された2つの頂部 ゛を備え
、これらの頂部が前記シリンダ七一定の隙間を有するよ
うに配置した非円形断面のピストン5ペーご
と、シリンダの一部に摺動自在に設けられスプリングに
よりその先端が前記ピストンに圧接するような少なくと
も2個のベーンを備え、このベーンをシリンダ内に不均
等に配置させることにより、各ベーン間にて仕切られる
圧縮室内の変動圧力のピークの位相をずらし、合成変動
圧力のピーク値を従来に比べて低減させることができ、
モータの小型化、振動低減、及び効率の向上を図れるも
のである。As described above, the present invention provides a cylinder having a circular cross section,
A piston with a non-circular cross section, which is provided with two apexes evenly distributed on the outer circumferential surface and arranged such that these apexes have a constant gap between the cylinders, is slidable on a part of the cylinder. At least two vanes are provided in the cylinder, the tips of which are pressed against the piston by a spring, and by arranging the vanes unevenly within the cylinder, fluctuation pressure in the compression chamber partitioned between each vane can be reduced. By shifting the phase of the peak, the peak value of the composite fluctuating pressure can be reduced compared to the conventional method.
This makes it possible to reduce the size of the motor, reduce vibration, and improve efficiency.
第1図は本発明の一実施例を示す要部中央断面図、第2
図は第1図のII−I’線における断面図、第3図は本
発明の一実施例における圧縮動作流体の圧力変動を示す
図、第4図は従来例を示す圧縮部の断面図、第5図は従
来例における圧縮動作流体の圧力変動を示す図である。
5−−−−・・ピストン、7・・e・・0シリンダ、5
a・・・・・・−頂部、10,11・・豊6φ・ベーン
。
代理人の氏名 弁理士 中 尾 敏 男 ほか1名第1
因
第2図
グイ
第3図
ビス[ソ@東(違々(°]
第4図
第5区FIG. 1 is a central sectional view of the main part showing one embodiment of the present invention, and FIG.
The figure is a sectional view taken along the line II-I' in FIG. 1, FIG. 3 is a diagram showing pressure fluctuations of the compression working fluid in an embodiment of the present invention, and FIG. 4 is a sectional view of the compression section showing a conventional example. FIG. 5 is a diagram showing pressure fluctuations of compressed working fluid in a conventional example. 5----...Piston, 7...e...0 cylinder, 5
a...-Top, 10, 11...Yutaka 6φ vane. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Fig. 2 Gui Fig. 3 Bis [So @ East (different (°) Fig. 4 Section 5)
Claims (1)
れた2つの頂部を備え、これらの頂部が前記シリンダと
一定の隙間を有するように配置した非円形断姑のピスト
ンと、前記シリンダの一部に摺動自在に設けられ、スプ
リングによりその先端が前記ピストンに圧接する少なく
とも2個のベーンとを備え、前記ベーンを対称位置から
互々ずらして配置した回転型圧縮機。A cylinder having a circular cross section, a non-circularly cut piston having two tops evenly distributed on the outer circumferential surface and arranged such that these tops have a certain gap with the cylinder, and one of the cylinders. A rotary compressor, comprising at least two vanes that are slidably disposed on a portion of the rotor and whose tips are pressed against the piston by a spring, and the vanes are arranged offset from symmetrical positions.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9961182A JPS58217791A (en) | 1982-06-09 | 1982-06-09 | Rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9961182A JPS58217791A (en) | 1982-06-09 | 1982-06-09 | Rotary compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS58217791A true JPS58217791A (en) | 1983-12-17 |
JPH0115714B2 JPH0115714B2 (en) | 1989-03-20 |
Family
ID=14251887
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9961182A Granted JPS58217791A (en) | 1982-06-09 | 1982-06-09 | Rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58217791A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1316729A2 (en) * | 2001-11-30 | 2003-06-04 | Seiko Instruments Inc. | Gas compressor |
CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
EP3194780A4 (en) * | 2014-09-19 | 2018-05-09 | LG Electronics Inc. | Compressor |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4890010A (en) * | 1972-03-06 | 1973-11-24 | ||
JPS5429405U (en) * | 1977-08-01 | 1979-02-26 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52130419A (en) * | 1976-04-26 | 1977-11-01 | Daido Plant Kogyo | Molding sand clean polishing device |
-
1982
- 1982-06-09 JP JP9961182A patent/JPS58217791A/en active Granted
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4890010A (en) * | 1972-03-06 | 1973-11-24 | ||
JPS5429405U (en) * | 1977-08-01 | 1979-02-26 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1316729A2 (en) * | 2001-11-30 | 2003-06-04 | Seiko Instruments Inc. | Gas compressor |
EP1316729A3 (en) * | 2001-11-30 | 2003-09-10 | Seiko Instruments Inc. | Gas compressor |
US6824370B2 (en) | 2001-11-30 | 2004-11-30 | Calsonic Compressors Manufacturing Inc. | Rotary vane gas compressor having unequal intervals between vane grooves and/or unequal distances between vane grooves and rotor center |
CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
EP3194780A4 (en) * | 2014-09-19 | 2018-05-09 | LG Electronics Inc. | Compressor |
US10962010B2 (en) | 2014-09-19 | 2021-03-30 | Lg Electronics Inc. | Compressor |
Also Published As
Publication number | Publication date |
---|---|
JPH0115714B2 (en) | 1989-03-20 |
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