JP2553747B2 - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JP2553747B2 JP2553747B2 JP2209992A JP20999290A JP2553747B2 JP 2553747 B2 JP2553747 B2 JP 2553747B2 JP 2209992 A JP2209992 A JP 2209992A JP 20999290 A JP20999290 A JP 20999290A JP 2553747 B2 JP2553747 B2 JP 2553747B2
- Authority
- JP
- Japan
- Prior art keywords
- main bearing
- rotary compressor
- hermetically sealed
- bearing
- compression element
- 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 - Lifetime
Links
Landscapes
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、冷凍冷蔵装置等に用いられる回転型圧縮機
に関する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used for a refrigerator or the like.
従来の技術 近年、冷凍冷蔵装置等に用いられる圧縮機は、省エネ
ルギー,省スペースに見地から往復型から回転型へと移
行してきている。特に省スペースの観点から超コンパク
ト化が望まれていた。2. Description of the Related Art In recent years, compressors used in refrigerating machines and the like have been shifting from reciprocating type to rotating type in terms of energy saving and space saving. In particular, there has been a demand for ultra compactness from the viewpoint of space saving.
そのため、回転型圧縮機のコンパクト化を図った従来
の技術としては、例えば、特開昭62−58092号公報に示
されているように、通常用いられている副軸受と主軸受
からなる両持ち軸受構造から副軸受を廃止した片持ち軸
受構造等が考案されている。Therefore, as a conventional technique for reducing the size of the rotary compressor, for example, as shown in Japanese Patent Laid-Open No. 62-58092, a two-sided support consisting of a commonly used auxiliary bearing and a main bearing is used. A cantilever bearing structure has been devised in which auxiliary bearings are eliminated from the bearing structure.
以下、図面を参照しながら、上述した従来の回転型圧
縮機の一例について説明する。Hereinafter, an example of the above-described conventional rotary compressor will be described with reference to the drawings.
第3図、第4図は従来の回転型圧縮機の縦断面図及び
II−II′断面図である。図において、1は密閉容器で、
電動機部2と圧縮要素部3を収納している。電動機部2
は、固定子2aと回転子2bとで構成されており、シャフト
4を介してシリンダ5、ローラ6、ベーン7、主軸受
8、シリンダカバー9、圧縮室10とから構成される圧縮
要素部3と連結している。主軸受8は吐出バルブ11を収
納したバルブ収納凹部12を有しており、外周部を90゜等
間隔に分割した4箇所の溶接部13にて密閉容器1と溶接
固定している。14は吐出カバーで主軸受8に圧入固定さ
れている。15は密閉容器1内の底部に貯溜された潤滑油
であり、16、17は吸入管と吐出管である。FIG. 3 and FIG. 4 are vertical sectional views of a conventional rotary compressor and
FIG. 11 is a sectional view taken along line II-II ′. In the figure, 1 is a closed container,
The electric motor unit 2 and the compression element unit 3 are housed. Motor part 2
Is composed of a stator 2a and a rotor 2b, and a compression element portion 3 including a cylinder 5, a roller 6, a vane 7, a main bearing 8, a cylinder cover 9 and a compression chamber 10 via a shaft 4. Connected with. The main bearing 8 has a valve accommodating recess 12 accommodating a discharge valve 11, and is welded and fixed to the hermetically sealed container 1 by means of four welded portions 13 whose outer peripheral portion is divided at equal intervals of 90 °. A discharge cover 14 is press-fitted and fixed to the main bearing 8. Reference numeral 15 is a lubricating oil stored at the bottom of the closed container 1, and 16 and 17 are a suction pipe and a discharge pipe.
以上のように構成された回転型圧縮機について、以下
その動作を説明する。The operation of the rotary compressor configured as described above will be described below.
外部冷却システム(図示せず)からの冷媒ガスは吸入
管16より導かれて、圧縮要素部3の圧縮室10に至り電動
機部2の回転に伴う圧縮要素部3の圧縮作動により漸次
圧縮される。圧縮された冷媒ガスは吐出バルブ11より吐
出カバー14を介して密閉容器1内に一旦吐出された後、
吐出管17より外部冷却システム(図示せず)へ吐出され
る。また潤滑油15は適宜な給油手段により圧縮要素部3
へ給油される。Refrigerant gas from an external cooling system (not shown) is introduced from the suction pipe 16 to reach the compression chamber 10 of the compression element section 3 and is gradually compressed by the compression operation of the compression element section 3 accompanying the rotation of the electric motor section 2. . The compressed refrigerant gas is once discharged from the discharge valve 11 through the discharge cover 14 into the closed container 1,
It is discharged from the discharge pipe 17 to an external cooling system (not shown). Further, the lubricating oil 15 is supplied to the compression element portion 3 by an appropriate oil supply means.
To be refueled.
発明が解決しようとする課題 しかしながら上記した従来の構成では、外周部を90゜
等間隔に分割した4箇所の溶接部13にて密閉容器1と溶
接固定しているため、主軸受8はバルブ収納凹部12近辺
の剛性と弱い部分に溶接部13を設けることになる。この
ため溶接時の熱エネルギーにより密閉容器1が変形し主
軸受8を軸心方向に押さえつけたときに主軸受8のバル
ブ収納部12近辺に大きな応力が働くこととなり、主軸受
8は大きく歪んでしまう。従って、圧縮要素部8の圧縮
作動時にこの主軸受8の歪の影響により、こじりやロッ
ク等が発生するという課題があった。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the above-mentioned conventional structure, the main bearing 8 is accommodated in the valve because the outer peripheral portion is welded and fixed to the closed container 1 by the four welded portions 13 divided at equal intervals. The welded portion 13 is provided in a portion near the recess 12 where the rigidity is weak. For this reason, the sealed container 1 is deformed by the heat energy during welding, and when the main bearing 8 is pressed in the axial direction, a large stress acts on the main bearing 8 in the vicinity of the valve housing portion 12, and the main bearing 8 is largely distorted. I will end up. Therefore, there is a problem that twisting or locking occurs due to the influence of the distortion of the main bearing 8 during the compression operation of the compression element portion 8.
本発明は上記課題に鑑み、主軸受と密閉容器との溶接
時に発生する主軸受の歪を極力小さくし、こじりやロッ
ク等の心配のないコンパクトで高性能な回転型圧縮機を
提供するものである。In view of the above problems, the present invention provides a compact and high-performance rotary compressor that minimizes distortion of the main bearing that occurs during welding of the main bearing and the hermetically sealed container, and does not cause prying or locking. is there.
課題を解決するための手段 上記課題を解決するために本発明の回転型圧縮機は、
バルブ収納凹部を有する主軸受を、その外周を略120゜
間隔で密閉容器に溶接することにより固定するととも
に、前記バルブ収納凹部を2箇所の溶接部の略中央に設
けたものである。Means for Solving the Problems In order to solve the above problems, the rotary compressor of the present invention is
A main bearing having a valve accommodating recess is fixed by welding its outer periphery to a hermetically sealed container at intervals of approximately 120 °, and the valve accommodating recess is provided substantially at the center of two welded portions.
作用 本発明は上記した構成によって、主軸受と密閉容器と
の溶接時に発生する熱エネルギーによる密閉容器の変形
は、主軸受のバルブ収納部凹部を避けた3箇所で主軸受
を軸心方向に押さえつけるように変形するため、主軸受
に働く応力は剛性の強いところでバランスし主軸受に発
生する歪を極力小さくできる。Effect of the Invention According to the present invention, due to the above-described structure, deformation of the hermetic container due to thermal energy generated during welding of the main bearing and the hermetic container presses the main bearing in the axial direction at three locations avoiding the recessed portion of the valve housing of the main bearing. As described above, the stress acting on the main bearing is balanced in a place where the rigidity is high, and the strain generated in the main bearing can be minimized.
実 施 例 以下、本発明の回転型圧縮機の一実施例について図面
を参照しながら説明する。尚、説明の重複を避けるた
め、従来例と同一部分については同一符号を付して説明
を省略する。Examples Hereinafter, one example of the rotary compressor of the present invention will be described with reference to the drawings. In order to avoid duplication of description, the same parts as those of the conventional example are designated by the same reference numerals and the description thereof will be omitted.
第1図,第2図は本発明の回転型圧縮機の縦断面図と
I−I′断面図である。1 and 2 are a longitudinal sectional view and an II 'sectional view of a rotary compressor of the present invention.
圧縮機の基本的な構成及び作動は従来と同様である
が、主軸受8の外周部を略120゜間隔に分割した3箇所
の溶接部18にて密閉容器1と溶接固定している。そして
主軸受8には2箇所の溶接部18,18の略中央に位置して
バルブ収納凹部12が形成されている。The basic structure and operation of the compressor are the same as those of the conventional one, but the outer peripheral portion of the main bearing 8 is welded and fixed to the hermetically sealed container 1 at three welded portions 18 divided into approximately 120 ° intervals. The main bearing 8 is provided with a valve accommodating recess 12 located substantially at the center of the two welds 18, 18.
以上のように構成された回転型圧縮機のについて、以
下その動作を説明する。The operation of the rotary compressor configured as described above will be described below.
主軸受8と密閉容器1との溶接時に発生する熱エネル
ギーにより、溶接部18の3箇所において密閉容器1が変
形し主軸受8を軸心方向に押さえつける。このとき、バ
ルブ収納凹部12が溶接部18を避け、2箇所の溶接部18,1
8の中間に形成されているため、溶接部18,18に作用する
軸心方向の熱応力に対して剛性を低下させることがな
い。従って120゜毎の溶接部18,18,18に作用する3方向
の応力がバランスし、主軸受8に発生する歪を極力小さ
く、且均等化できる。これにより、回転式圧縮要素部3
の圧縮作動時に発生するこじりやロック等を抑制し軽減
することができる。また、主軸受8の端面とローラ6と
の摺動を良化することができる。Due to the thermal energy generated during the welding of the main bearing 8 and the hermetically sealed container 1, the hermetically sealed container 1 is deformed at the three locations of the welded portion 18 and presses the main bearing 8 in the axial direction. At this time, the valve housing recess 12 avoids the welded portion 18 and the welded portions 18
Since it is formed in the middle of 8, the rigidity does not decrease with respect to the thermal stress acting on the welded portions 18, 18 in the axial direction. Therefore, the stresses in the three directions acting on the welded parts 18, 18, 18 at 120 ° intervals are balanced, and the strain generated in the main bearing 8 can be minimized and equalized. Thereby, the rotary compression element portion 3
It is possible to suppress and reduce twisting and locking that occur during the compression operation of the. Further, sliding between the end surface of the main bearing 8 and the roller 6 can be improved.
発明の効果 以上のように本発明は、密閉容器と密閉容器内に収納
された電動機部及び主軸受にバルブ収納凹部を有した圧
縮要素部とで構成されるものであって、主軸受を、その
外周を略120゜間隔で密閉容器に溶接することにより固
定するとともに、前記バルブ収納凹部を2箇所の溶接部
の略中央に設けたことにより、主軸受と密閉容器の溶接
時に発生する主軸受の歪を極力小さくできる。これによ
り、主軸受とシャフトのこじりやロックを抑制軽減し、
かつ微小な歪も均等化するので主軸受端面とローラの摺
動を良化することができ、コンパクトで高性能な回転型
圧縮機を提供することができる。Effects of the Invention As described above, the present invention comprises a hermetically sealed container, a motor portion housed in the hermetically sealed container, and a compression element portion having a main bearing with a valve accommodating recess. The outer periphery of the main bearing is fixed by welding at an interval of about 120 ° to the hermetically sealed container, and the valve housing recess is provided substantially at the center of the two welded portions. The distortion of can be minimized. This reduces and reduces twisting and locking of the main bearing and shaft,
In addition, since even minute distortions are equalized, sliding of the main bearing end surface and the rollers can be improved, and a compact and high-performance rotary compressor can be provided.
第1図は本発明の一実施例を示す回転型圧縮機の縦断面
図、第2図は同圧縮機のI−I′線の断面図、第3図は
従来の回転型圧縮機の縦断面図、第4図は同圧縮機のII
−II′線の断面図である。 1……密閉容器、2……電動機部、3……圧縮要素部、
8……主軸受、12……バルブ収納凹部、18……溶接部。FIG. 1 is a vertical sectional view of a rotary compressor showing an embodiment of the present invention, FIG. 2 is a sectional view taken along the line I-I 'of the same compressor, and FIG. 3 is a vertical sectional view of a conventional rotary compressor. Fig. 4 and Fig. 4 show the compressor II
FIG. 11 is a cross-sectional view taken along the line II ′. 1 ... airtight container, 2 ... electric motor part, 3 ... compression element part,
8 …… Main bearing, 12 …… Valve housing recess, 18 …… Welding part.
Claims (1)
部及び回転式圧縮要素部から成り、前記回転式圧縮要素
部と構成する主軸受に、バルブ収納凹部を設けたものに
おいて、前記主軸受はその外周を略120゜間隔で密閉容
器に溶接することにより固定されるとともに、前記バル
ブ収納凹部を2箇所の溶接部の略中央に設けたことを特
徴とする回転型圧縮機。1. A main bearing comprising a hermetically sealed container, an electric motor section and a rotary compression element section housed in the hermetically sealed vessel, wherein the main bearing constituting the rotary compression element section is provided with a valve accommodating recess. The bearing is fixed by welding the outer periphery of the bearing to a closed container at intervals of approximately 120 °, and the valve accommodating recess is provided at approximately the center of two welds.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2209992A JP2553747B2 (en) | 1990-08-07 | 1990-08-07 | Rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2209992A JP2553747B2 (en) | 1990-08-07 | 1990-08-07 | Rotary compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0494492A JPH0494492A (en) | 1992-03-26 |
JP2553747B2 true JP2553747B2 (en) | 1996-11-13 |
Family
ID=16582066
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2209992A Expired - Lifetime JP2553747B2 (en) | 1990-08-07 | 1990-08-07 | Rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2553747B2 (en) |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57102593A (en) * | 1980-12-19 | 1982-06-25 | Hitachi Ltd | Rotary closed type compressor |
JPS6258092A (en) * | 1985-09-09 | 1987-03-13 | Matsushita Refrig Co | Rotary compressor |
-
1990
- 1990-08-07 JP JP2209992A patent/JP2553747B2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JPH0494492A (en) | 1992-03-26 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
LAPS | Cancellation because of no payment of annual fees |