JPS635186A - Closed motor compressor - Google Patents
Closed motor compressorInfo
- Publication number
- JPS635186A JPS635186A JP14641186A JP14641186A JPS635186A JP S635186 A JPS635186 A JP S635186A JP 14641186 A JP14641186 A JP 14641186A JP 14641186 A JP14641186 A JP 14641186A JP S635186 A JPS635186 A JP S635186A
- Authority
- JP
- Japan
- Prior art keywords
- press
- crankshaft
- bearing
- fitted
- ball bearing
- 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
- 230000006835 compression Effects 0.000 claims description 2
- 238000007906 compression Methods 0.000 claims description 2
- 230000007423 decrease Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 235000007575 Calluna vulgaris Nutrition 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、冷蔵庫等に使用される密閉形電動圧縮機に関
するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a hermetic electric compressor used in refrigerators and the like.
従来の技術
近年、密閉形電動圧縮機（以下、圧縮機という。）は、
エネルギー効率向上の見地から、圧縮機の高効率化が要
望されている。圧縮機は高効率化が進み高いレベルに達
しているが、より一層の高効率化を計って行かなければ
ならない。Conventional technology In recent years, hermetic electric compressors (hereinafter referred to as compressors) have been
From the standpoint of improving energy efficiency, there is a demand for higher efficiency compressors. Compressors have become highly efficient and have reached a high level, but we must continue to improve efficiency even further.
以下図面を参照しながら、従来の圧縮機の一実施例につ
いて説明する。第４図は従来の圧縮機の断面図、第３図
は第４図の要部拡大断面図である。An example of a conventional compressor will be described below with reference to the drawings. FIG. 4 is a sectional view of a conventional compressor, and FIG. 3 is an enlarged sectional view of the main part of FIG. 4.
密閉容器１内に、弾性支持された圧縮要素２と電動要素
３とを備え、前記電動要素３の回転子４にはクランク軸
６がスラストワッシャー６をはさんで圧入されている。A compressor element 2 and an electric element 3 which are elastically supported are provided in a closed container 1, and a crankshaft 6 is press-fitted into a rotor 4 of the electric element 3 with a thrust washer 6 interposed therebetween.
クランク軸６はブロック７にポルト８にて固定されたジ
ャーナル軸受９により軸支されている。The crankshaft 6 is supported by a journal bearing 9 fixed to the block 7 at a port 8.
以上のように構成された圧縮機において、圧縮機が運転
を始めると回転子４が回転する事によりクランク軸が軸
受９に支持されて回転し、ピストン１ｏが往復運動して
ガスを圧縮する。In the compressor configured as described above, when the compressor starts operating, the rotor 4 rotates, the crankshaft is supported by the bearing 9 and rotates, and the piston 1o reciprocates to compress gas.
発明が解決しようとする問題点
しかしながら上記のような構成では回転子４とクランク
軸５の自重によるスラスト荷重をスラストワッシャー６
とジャーナル軸受９の間で受ける為、クランク軸６の偏
心軸座面５ａと上記軸受９の下面９ａの間にＯ，ＳＷ程
度の隙間ｌを設ける必要があり、その為、圧縮機の回転
による微振動により回転子４と固定子１１の磁気中心位
置が安定せずモーター効率の低下をまねき、圧縮機の効
率低下を招く問題点を有していた。又、ジャーナル軸受
９とクランク軸５はすべり状態にあり、摺動損失がかな
り大きく圧縮機の効率を低下させていた。Problems to be Solved by the Invention However, in the above configuration, the thrust load due to the weight of the rotor 4 and the crankshaft 5 is transferred to the thrust washer 6.
and the journal bearing 9, it is necessary to provide a gap l of approximately O, SW between the eccentric shaft bearing surface 5a of the crankshaft 6 and the lower surface 9a of the bearing 9. There was a problem in that the minute vibrations caused the magnetic center positions of the rotor 4 and stator 11 to become unstable, resulting in a decrease in motor efficiency and a decrease in compressor efficiency. In addition, the journal bearing 9 and the crankshaft 5 were in a sliding state, causing considerable sliding loss and reducing the efficiency of the compressor.
本発明は上記問題点に鑑み、磁気中心のズレが無く、効
率の安定した圧縮機を提供するものである。In view of the above problems, the present invention provides a compressor with stable efficiency and no deviation of the magnetic center.
問題点を解決するだめの手段
上記問題点を解決する為に本発明の圧縮機は、クランク
軸を軸支する２個めボールベアリングを用い、−方のボ
ールベアリングをクランク軸の位置決め段差まで圧入位
置決め固定し、他のボールベアリングを軸受本体の上部
内側に圧入位置決め固定したものである。Means to Solve the Problems In order to solve the above problems, the compressor of the present invention uses a second ball bearing that pivotally supports the crankshaft, and the negative ball bearing is press-fitted to the positioning step of the crankshaft. The ball bearing is positioned and fixed, and another ball bearing is press-fitted and positioned and fixed inside the upper part of the bearing body.
作 用
本発明は上記した構成によって、回転子のスラスト方向
の遊びが無く、回転子と固定子の磁気中心位置ズレによ
るモータ効率低下が無くなるので、圧縮機のエネルギー
効率が安定するとともに、軸受をボールベアリングにす
る事により摺動ロスが減り、より高効率の圧縮機が実現
する。Effects of the present invention With the above-described configuration, there is no play in the thrust direction of the rotor, and there is no reduction in motor efficiency due to misalignment of the magnetic centers of the rotor and stator, so the energy efficiency of the compressor is stabilized, and the bearings are By using ball bearings, sliding loss is reduced, resulting in a more efficient compressor.
実施例
以下本発明の一実施例の圧縮機について、図面を参照し
ながら説明する。第１図は本発明の一実施例における圧
縮機の要部拡大断面図、第２図は同圧縮機の断面図であ
る。図において、回転子２４に圧入固定されたクランク
軸２６にボールベアリングＢ１６を、位置決め段差２５
ａまで圧入位置決め固定し、ボールベアリングＢ１ｅに
嵌合する軸受本体２９を挿入し、ボールベアリングＡ１
ｓを、軸受本体２９の上部内側の段部位置までクランク
軸２６に圧入固定したものである。クランク軸２６．ボ
ールベアリングＡ１６．ボールベアリングＢ１６．軸受
本体２９以外は従来の圧縮機（第３図、第４図）と同一
である。また、ボールベアリングＢ１６を圧入するクラ
ンク軸２５の軸径は、ボールベアリングＡ１６を圧入す
るクランク軸２６の、軸径よりも大きくなっている事に
より、ボールベアリングＢ１６の圧入を容易にしている
。EXAMPLE Hereinafter, a compressor according to an example of the present invention will be described with reference to the drawings. FIG. 1 is an enlarged sectional view of essential parts of a compressor according to an embodiment of the present invention, and FIG. 2 is a sectional view of the same compressor. In the figure, a ball bearing B16 is attached to a crankshaft 26 press-fitted into a rotor 24, and a positioning step 25
Press-fit and position and fix the ball bearing B1e, insert the bearing body 29 that fits into the ball bearing B1e, and then
s is press-fitted and fixed to the crankshaft 26 up to the step position inside the upper part of the bearing body 29. Crankshaft 26. Ball bearing A16. Ball bearing B16. The components other than the bearing body 29 are the same as the conventional compressor (FIGS. 3 and 4). Further, the shaft diameter of the crankshaft 25 into which the ball bearing B16 is press-fitted is larger than the shaft diameter of the crankshaft 26 into which the ball bearing A16 is press-fitted, thereby facilitating the press-fitting of the ball bearing B16.
以上のように構成された圧縮機について、ボールベアリ
ングＡ１５．ボールベアリングＢ１８で軸受本体２９を
はさみ込み、クランク軸２６に圧入固定されているので
、軸受本体２９に対する、クランク軸２５に圧入固定さ
れている回転子２４のスラスト方向の遊びが無く、圧縮
機の微振動により、回転子２４と固定子２３の磁気中心
位置のズレが発生しない。Regarding the compressor configured as above, ball bearing A15. Since the bearing body 29 is sandwiched between the ball bearing B18 and press-fitted to the crankshaft 26, there is no play in the thrust direction of the rotor 24, which is press-fitted to the crankshaft 25, with respect to the bearing body 29, and the compressor The minute vibrations do not cause misalignment of the magnetic center positions of the rotor 24 and stator 23.
以上のように本実施例によれば、クランク軸２５を軸支
するボールベアリングＡ１６．ボールベアリングＢ１６
で軸受本体２９をはさみ込んでクランク軸２６に圧入位
置決め固定する事により、回転子２４と固定子２３の磁
気中心位置のズレを無くす事ができ、磁気中心位置のズ
レによるモータ効率の低下を押さえ、高効率の圧縮機を
可能にする。また、軸受をボールベアリングＡ１５．ボ
ールベアリングＢ１ｅとする事により、摺動ロスを低減
させ、さらに高効率の圧縮機とする事ができる。As described above, according to this embodiment, the ball bearing A16. which pivotally supports the crankshaft 25. Ball bearing B16
By sandwiching the bearing body 29 and press-fitting and positioning and fixing it to the crankshaft 26, it is possible to eliminate deviations in the magnetic center positions of the rotor 24 and stator 23, thereby suppressing a decrease in motor efficiency due to deviations in the magnetic center positions. , enabling a highly efficient compressor. In addition, the bearing is a ball bearing A15. By using the ball bearing B1e, sliding loss can be reduced and a compressor with even higher efficiency can be achieved.
発明の効果
以上のように本発明の密閉形電動圧縮機によれば、クラ
ンク軸を軸支する２つのボールベアリングで軸受本体を
はさみ込んで、クランク軸に圧入位置決め固定する事に
より、回転子と固定子の磁気中心位置のズレを無くす事
ができ、磁気中心位置のズレによるモータ効率の低下を
抑え、高効率の圧縮機を可能にする。また軸受をボール
ベアリングとする事により、摺動ロスを低減させ、入力
１３０Ｗクラスの圧縮機において１５Ｗの入力低減が可
能となり、高効率の圧縮機を提供する事ができる。また
偏心軸側のボールベアリング径を池のボールベアリング
径より犬とすることにより、ボールベアリングの圧入組
立が容易となる効果が得られるものである。Effects of the Invention As described above, according to the hermetic electric compressor of the present invention, the bearing body is sandwiched between two ball bearings that pivotally support the crankshaft, and the rotor and It is possible to eliminate deviations in the magnetic center position of the stator, suppress the decline in motor efficiency due to deviations in the magnetic center position, and enable a highly efficient compressor. In addition, by using a ball bearing as the bearing, sliding loss is reduced, making it possible to reduce input power by 15 W in a compressor with an input of 130 W, thereby providing a highly efficient compressor. Furthermore, by making the diameter of the ball bearing on the eccentric shaft side smaller than the diameter of the ball bearing on the other hand, it is possible to obtain the effect that the press-fit assembly of the ball bearing is facilitated.
第１図は本発明の一実施例における密閉形電動圧縮機の
要部拡大断面図、第２図は本発明の一実施例における密
閉形電動圧縮機の断面図、第３図は従来例の密閉形電動
圧縮機の要部拡大断面図、第４図は従来例の密閉形電動
圧縮機の断面図である。
２１・・・・・・密閉容器、２０・・・・・・電動要素
、２２・・・・・・圧縮要素、２４・・・・・・回転子
、２６・・・・・・クランク軸、２９・・・・・・軸受
本体、１５．１６・・・・・・ボールベアリング、２５
ａ・・・・・・クランク軸の位置決め段差。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名／５
−−−キＦルベアリングＡ
２９−一一油受、杢、Ｐト
２４−一一回板子
第 ２ 図 ２５−一−クランク
軸２ｑ−−−細受本１＝Ｔ−
第３図FIG. 1 is an enlarged cross-sectional view of the main parts of a hermetic electric compressor according to an embodiment of the present invention, FIG. FIG. 4 is an enlarged sectional view of a main part of a hermetic electric compressor. FIG. 4 is a sectional view of a conventional hermetic electric compressor. 21... Sealed container, 20... Electric element, 22... Compression element, 24... Rotor, 26... Crankshaft, 29...Bearing body, 15.16...Ball bearing, 25
a... Crankshaft positioning step. Name of agent: Patent attorney Toshio Nakao and 1 other person/5
---Kill bearing A 29-11 oil pan, heather, P24-11 plate 2nd figure 25-1-crankshaft 2q---Small receiver 1=T- Figure 3
Claims (2)
素を収納し、前記電動要素の回転子に固定されたクラン
ク軸と、前記クランク軸を軸支する軸受本体と、クラン
ク軸と軸受本体の間に挿入された２つのボールベアリン
グとを備え、１つのボールベアリングをクランク軸の偏
心に軸側の位置決め段差まで圧入位置決め固定するとと
もに他のボールベアリングを軸受本体の上部内側の段差
位置まで圧入位置決め固定した密閉形電動圧縮機。(1) An elastically supported electric element and a compression element are housed in a sealed container, a crankshaft fixed to the rotor of the electric element, a bearing body that pivotally supports the crankshaft, and a crankshaft and a bearing. It is equipped with two ball bearings inserted between the main body, and one ball bearing is press-fitted and fixed to the eccentricity of the crankshaft up to the positioning step on the shaft side, and the other ball bearing is positioned and fixed to the eccentricity of the crankshaft up to the step position inside the upper part of the bearing main body. Hermetic electric compressor with fixed press-fit positioning.
軸径を他方のボールベアリング取付軸径よりも大きくす
る構成とした特許請求の範囲第１項記載の密閉形電動圧
縮機。(2) The hermetic electric compressor according to claim 1, wherein the diameter of the ball bearing mounting shaft on the eccentric shaft side of the crankshaft is larger than the diameter of the ball bearing mounting shaft on the other side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14641186A JPS635186A (en) | 1986-06-23 | 1986-06-23 | Closed motor compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14641186A JPS635186A (en) | 1986-06-23 | 1986-06-23 | Closed motor compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS635186A true JPS635186A (en) | 1988-01-11 |
Family
ID=15407085
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14641186A Pending JPS635186A (en) | 1986-06-23 | 1986-06-23 | Closed motor compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS635186A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0574166U (en) * | 1992-03-02 | 1993-10-08 | 松下電器産業株式会社 | motor |
| US5252039A (en) * | 1991-02-05 | 1993-10-12 | Matsushita Refrigeration Co. | Enclosed motor-driven compressor |
| EP0727579A1 (en) * | 1991-01-22 | 1996-08-21 | Matsushita Refrigeration Company | Hermetically sealed compressor |
| CN105221426A (en) * | 2014-06-27 | 2016-01-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner |
| CN106050614A (en) * | 2016-08-01 | 2016-10-26 | 珠海凌达压缩机有限公司 | Compressor |
-
1986
- 1986-06-23 JP JP14641186A patent/JPS635186A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0727579A1 (en) * | 1991-01-22 | 1996-08-21 | Matsushita Refrigeration Company | Hermetically sealed compressor |
| US5252039A (en) * | 1991-02-05 | 1993-10-12 | Matsushita Refrigeration Co. | Enclosed motor-driven compressor |
| JPH0574166U (en) * | 1992-03-02 | 1993-10-08 | 松下電器産業株式会社 | motor |
| CN105221426A (en) * | 2014-06-27 | 2016-01-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner |
| CN106050614A (en) * | 2016-08-01 | 2016-10-26 | 珠海凌达压缩机有限公司 | Compressor |
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