JPS60249681A - Enclosed compressor - Google Patents
Enclosed compressorInfo
- Publication number
- JPS60249681A JPS60249681A JP10595684A JP10595684A JPS60249681A JP S60249681 A JPS60249681 A JP S60249681A JP 10595684 A JP10595684 A JP 10595684A JP 10595684 A JP10595684 A JP 10595684A JP S60249681 A JPS60249681 A JP S60249681A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- groove
- viscosity
- main bearing
- depth
- 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
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は冷凍サイクル等において用いられる密閉形圧縮
機に係り、とりわけ主軸受部の給油機構に特徴を有する
密閉形圧縮機に関する。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a hermetic compressor used in a refrigeration cycle or the like, and particularly to a hermetic compressor characterized by an oil supply mechanism for a main bearing.
第1図は密閉形圧縮機の一例を示す縦断面図である。密
閉形圧縮機10は、密閉ケーシング11内の上部に配設
された電動機12、この電動機12から下方に延びる、
下端側に偏心した大径部13が一体形成されているシャ
フト14、大径部13を挾むように上、下に配設され、
シャフト14を軸受支持する主軸受15および副軸受1
6、主軸受15および副軸受16の間に位置し、圧縮装
置を構成するシリンダ17、シリンダ17内に大径部1
3と外嵌した状態で配設されたローラ18、ローラ18
に弾接するブレード19を備えている。FIG. 1 is a longitudinal sectional view showing an example of a hermetic compressor. The hermetic compressor 10 includes an electric motor 12 disposed in the upper part of the hermetic casing 11, and a motor 12 extending downward from the electric motor 12.
A shaft 14 integrally formed with a large diameter portion 13 eccentric to the lower end side, disposed above and below so as to sandwich the large diameter portion 13,
A main bearing 15 and a sub-bearing 1 that support the shaft 14
6. A cylinder 17 located between the main bearing 15 and the auxiliary bearing 16 and forming a compression device; a large diameter portion 1 inside the cylinder 17;
3 and the rollers 18 and 18 disposed in an externally fitted state.
It is provided with a blade 19 that makes elastic contact with the blade 19.
また、ケーシング11の下部には、潤滑油の貯留された
油タンク21が設C−1られ、この油タンク21内から
シャフト14と主軸受15との摺動部分へ潤滑油が供給
されて主軸受部の潤滑がなされるようになっている。こ
の潤滑油の供給は、シャフト14の中心穴22内に設け
られたオイルポンプ23、およびシャツ1〜14の外周
あるいは主軸受15の内周面に設けられた螺旋状の油溝
24により潤滑油をくみ上げることにより行われる。Further, an oil tank 21 in which lubricating oil is stored is provided at the lower part of the casing 11, and the lubricating oil is supplied from inside this oil tank 21 to the sliding portion between the shaft 14 and the main bearing 15. The bearings are lubricated. This lubricating oil is supplied by an oil pump 23 provided in the center hole 22 of the shaft 14 and a spiral oil groove 24 provided on the outer circumference of the shirts 1 to 14 or on the inner circumferential surface of the main bearing 15. This is done by pumping up the water.
従来の密閉形圧縮機においては、螺旋状の油溝24は1
本のみ設けられており、このため、油の粘度が変化する
ことにより、主軸受部への給油量が変動するという問題
があった。tJ−なわち、シャフト1/Iの中心穴22
内に設けられたオイルポンプ23は、油の粘度が低下す
ると給油量が増大する特性があり、また螺旋状油溝24
は、逆に、油の粘度が低下すると給油量が低下する特性
があるため、全体としての主軸受部への給油量は、第2
図に示すように、油の粘度が低下すると急速に低下する
という傾向がある。In a conventional hermetic compressor, the spiral oil groove 24 is
Since only one shaft is provided, there is a problem in that the amount of oil supplied to the main bearing section fluctuates due to changes in the viscosity of the oil. tJ - that is, the center hole 22 of shaft 1/I
The oil pump 23 provided inside has a characteristic that the amount of oil supplied increases as the viscosity of the oil decreases, and the spiral oil groove 24
On the contrary, as the viscosity of the oil decreases, the amount of oil supplied decreases, so the amount of oil supplied to the main bearing as a whole is
As shown in the figure, there is a tendency for the viscosity of the oil to decrease rapidly as it decreases.
このため、密閉形圧縮機の過熱時など、油の粘度が低下
した時、給油量が急速に低下し、主軸受部に焼付きなど
を生ずることがあった。For this reason, when the viscosity of the oil decreases, such as when the hermetic compressor overheats, the amount of oil supplied decreases rapidly, sometimes causing seizure in the main bearing.
本発明はこのような点を考慮してなされたものであり、
油の粘度が変化しても主軸受部への給油量が大きく変動
せず、常に安定した潤滑が行われる、信頼性の高い密閉
形圧縮機を提供することを目的としている。The present invention has been made in consideration of these points,
The purpose of the present invention is to provide a highly reliable hermetic compressor in which the amount of oil supplied to the main bearing does not vary greatly even if the viscosity of the oil changes, and stable lubrication is always performed.
本発明は、シャフトまたは主軸受に給油用の螺旋状油溝
が設けられている密閉形圧縮機であって、油溝が複数本
並列に設けられているとともに、それぞれの油溝の断面
形状は互いに相違していることを特徴としている。The present invention is a hermetic compressor in which a shaft or a main bearing is provided with a spiral oil groove for oil supply, in which a plurality of oil grooves are provided in parallel, and each oil groove has a cross-sectional shape. They are characterized by being different from each other.
以下図面を参照して本発明の実施例について説明する。 Embodiments of the present invention will be described below with reference to the drawings.
第3図は本発明による密閉形圧縮機において用いられる
主軸受35を示す縦断面図である。本発明においては、
主軸受35に設けられた螺旋状の油溝は、互いに平行に
2本設(プられ、一方の油溝34.1は、他方の油溝3
4bに比べ、深さおよび溝幅を異にしている。すなわち
、第4図に示すように、一方の油溝34aは、溝の深さ
が61、溝幅が81に形成され、他方の油溝34bは、
溝の深さが62、溝幅が82に形成されている。FIG. 3 is a longitudinal sectional view showing the main bearing 35 used in the hermetic compressor according to the present invention. In the present invention,
The main bearing 35 has two spiral oil grooves parallel to each other.
Compared to 4b, the depth and groove width are different. That is, as shown in FIG. 4, one oil groove 34a has a groove depth of 61 mm and a groove width of 81 mm, and the other oil groove 34b has a groove depth of 61 mm and a groove width of 81 mm.
The groove has a depth of 62 mm and a width of 82 mm.
一般に、螺旋状の油溝を流れる油の量は次式で表わされ
る。Generally, the amount of oil flowing through a spiral oil groove is expressed by the following equation.
ここで Q : 流量
U ; 周速度
B : 溝幅
δ : 溝の深さ
μ : 油の粘度
(i−?−: 溝の長手方向の圧縮勾配x
流ff1Qは、溝の深さδに対し極大値をもち、その値
は、δで微分することにより、
δ−3UIi ・・・・・・・・・・・・・・・・・・
・・・・・・ (2)d P/d x
となる。Here, Q: Flow rate U; Peripheral speed B: Groove width δ: Groove depth μ: Oil viscosity (i-?-: Compression gradient in the longitudinal direction of the groove By differentiating the value with δ, δ−3UIi ・・・・・・・・・・・・・・・・・・
...... (2) dP/dx.
(2)式において、粘度μは、温度、冷媒の溶は込み等
に°より変化し、これに伴ない溝の深ざδの最適値も変
化する。すなわち、粘度μが低くなれば溝の深さδの最
適値は小さくなり、逆に粘度μが高くなれば溝の深さδ
の最適値は大きくなる。In equation (2), the viscosity μ changes depending on temperature, refrigerant penetration, etc., and the optimum value of the groove depth δ changes accordingly. In other words, the lower the viscosity μ, the smaller the optimal value of the groove depth δ, and conversely, the higher the viscosity μ, the smaller the groove depth δ.
The optimal value of becomes large.
そこで、一方の油溝34aの溝の深さδ1を低粘度の油
に対して最適な値に、他方の油溝34bの溝の深ざδ2
を高粘度の油に対して最適な値となるように設定すれば
、油の粘度が低粘度あるいは高粘度のいずれであっても
、いずれか一方の油溝を用いて、常に最大流JitQを
確保することができる。Therefore, the groove depth δ1 of one oil groove 34a is set to an optimal value for low viscosity oil, and the groove depth δ2 of the other oil groove 34b is set to an optimal value for low viscosity oil.
By setting JitQ to the optimum value for high viscosity oil, the maximum flow JitQ can always be achieved using either oil groove, regardless of whether the oil viscosity is low or high. can be secured.
本実施例においては、運転開始時など、油の粘度が比較
的高い時は、主として溝の深さの大きい油溝34bを通
って主軸受部に給油され、運転中高温になった時は、主
として溝の深さの小さい油溝34aを通って主軸受部に
給油され、全体としての給油量は、第5図に示すように
、粘度の変化の影響をほとんど受けない安定した状態に
保たれる。In this embodiment, when the viscosity of the oil is relatively high, such as at the start of operation, the main bearing is mainly supplied through the deep oil groove 34b, and when the temperature becomes high during operation, The main bearing is mainly supplied with oil through the oil groove 34a, which has a small groove depth, and the overall amount of oil supplied is kept stable, almost unaffected by changes in viscosity, as shown in Figure 5. It will be done.
したがって、高温時に油の粘度が低下しても、主軸受部
に油切れを生ずることがなく、また、低温時に油の粘度
が増大しても、給油量が多すぎて油タンク21の油面が
低下することもない。Therefore, even if the viscosity of the oil decreases at high temperatures, the main bearing will not run out of oil, and even if the viscosity of the oil increases at low temperatures, the amount of oil supplied will be too large and the oil level in the oil tank 21 will not occur. does not decrease.
なお、本実施例においては、油溝を主軸受35の内周面
に設けた例を示したが、主軸受35の内周面と摺動する
シャフト14の外周に設けてもよい。また、油溝の本数
は、油の粘度変化により適切に対応させるよう、3本以
上設けることもてきる。In this embodiment, an example is shown in which the oil groove is provided on the inner circumferential surface of the main bearing 35, but it may be provided on the outer circumference of the shaft 14 that slides on the inner circumferential surface of the main bearing 35. Moreover, three or more oil grooves may be provided in order to more appropriately respond to changes in oil viscosity.
以上説明したように、本発明によれば、それぞれの油の
粘度に対して@適な断面形状をしだ油溝が複数本並列に
設けられているので、油の粘度が変化しても、常に安定
した給油量を確保することができ、主軸受部の焼付き等
の事故を防止することができる。また、主軸受部への給
油の絶対量も増大し、主軸受部の潤滑の信頼性を向上さ
せることができる。As explained above, according to the present invention, a plurality of oil grooves are provided in parallel with a cross-sectional shape suitable for each oil viscosity, so even if the oil viscosity changes, A stable supply of oil can be ensured at all times, and accidents such as seizure of the main bearing can be prevented. Furthermore, the absolute amount of oil supplied to the main bearing section is increased, and the reliability of lubrication of the main bearing section can be improved.
第1図は従来の密閉形圧縮機の一例を示す縦断面図、第
2図は従来の密閉形圧縮機の主軸受部に設(−Jられた
油溝による給油量の粘度との関係を示す図、第3図は本
発明による密閉形圧縮機の主軸受を示す縦断面図、第4
図は第3図に示した主軸受の部分拡大横断面図、第5図
は本発明による給油機構を用いた場合の給油量と粘度と
の関係を示づ一図である。
14・・・シャフト、34a 、34b・・・油溝、3
5・・・主軸受。
゛出願人代理人 猪 股 消
第 1 図
第2図
tb 笈
第 3図
第4図
第5区Figure 1 is a longitudinal sectional view showing an example of a conventional hermetic compressor, and Figure 2 shows the relationship between the amount of oil supplied and the viscosity of the oil groove installed in the main bearing of the conventional hermetic compressor. FIG. 3 is a vertical sectional view showing the main bearing of the hermetic compressor according to the present invention, and FIG.
This figure is a partially enlarged cross-sectional view of the main bearing shown in FIG. 3, and FIG. 5 is a diagram showing the relationship between the amount of oil supplied and the viscosity when the oil supply mechanism according to the present invention is used. 14...Shaft, 34a, 34b...Oil groove, 3
5... Main bearing.゛Applicant's Representative Ino Mata No. 1 Fig. 2 tb Koji Fig. 4 Fig. 5 Section
Claims (1)
ている密閉形圧縮機において、前記油溝は、複数本並列
に設けられているとともに、それぞれの油溝の断面形状
は互いに相違していることを特徴とする密閉形圧縮機。In a hermetic compressor in which a spiral oil groove for oil supply is provided on the shaft or main bearing, a plurality of oil grooves are provided in parallel, and each oil groove has a different cross-sectional shape. A hermetic compressor characterized by:
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10595684A JPS60249681A (en) | 1984-05-25 | 1984-05-25 | Enclosed compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10595684A JPS60249681A (en) | 1984-05-25 | 1984-05-25 | Enclosed compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS60249681A true JPS60249681A (en) | 1985-12-10 |
Family
ID=14421268
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP10595684A Pending JPS60249681A (en) | 1984-05-25 | 1984-05-25 | Enclosed compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60249681A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7677805B2 (en) * | 2004-11-03 | 2010-03-16 | Samsung Electronics Co., Ltd. | Fluid dynamic bearing and hard disk drive employing the same |
DE102009040612B4 (en) * | 2009-09-08 | 2012-01-26 | Siemens Aktiengesellschaft | Vibration-optimized sliding bearing for a rotating anode of an X-ray tube and X-ray tube |
CN112145420A (en) * | 2019-06-28 | 2020-12-29 | 安徽美芝精密制造有限公司 | Pump body subassembly, compressor and air conditioner |
-
1984
- 1984-05-25 JP JP10595684A patent/JPS60249681A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7677805B2 (en) * | 2004-11-03 | 2010-03-16 | Samsung Electronics Co., Ltd. | Fluid dynamic bearing and hard disk drive employing the same |
DE102009040612B4 (en) * | 2009-09-08 | 2012-01-26 | Siemens Aktiengesellschaft | Vibration-optimized sliding bearing for a rotating anode of an X-ray tube and X-ray tube |
CN112145420A (en) * | 2019-06-28 | 2020-12-29 | 安徽美芝精密制造有限公司 | Pump body subassembly, compressor and air conditioner |
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