JPS63201391A - Rotary hermetic compressor - Google Patents
Rotary hermetic compressorInfo
- Publication number
- JPS63201391A JPS63201391A JP3144587A JP3144587A JPS63201391A JP S63201391 A JPS63201391 A JP S63201391A JP 3144587 A JP3144587 A JP 3144587A JP 3144587 A JP3144587 A JP 3144587A JP S63201391 A JPS63201391 A JP S63201391A
- Authority
- JP
- Japan
- Prior art keywords
- vane
- hermetic compressor
- roller
- cylinder
- rotary hermetic
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、ベーンの慣性質量軽減構造を改良した回転式
密閉形圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a rotary hermetic compressor with an improved structure for reducing the inertial mass of vanes.
従来の回転式密閉形圧縮機に関連し、実開昭６１−２１
８９４号公報が提案されている。これを第２図ないし第
４図により説明する。第２図は縦断面図、第３図は第２
図のｍ−ｍ矢視断面図、第４図は第３図のベーン斜視図
である。図において、１は密閉形容器であり、密閉形容
器１内の上部、下部にはそれぞれ電動要素２、圧縮要素
３が配設され、電動要素２は固定子４と回転子５とから
構成されている０回転子５は圧縮要素３を構成する回転
軸６に圧入または焼嵌め等の手段によって固定されてい
る。そして、回転子５が回転すると、回転軸６の偏心部
７の外周に回転自在に嵌合されたローラ８が、シリンダ
９と上軸受１０の端面と下軸受１１の端面から構成され
る空間内を回転するようになっている。ローラ８の外周
にはシリ ゛シダ９の半径方向に、シリンダ９に形成
されたスロット１６内から摺動自在に突出し背後をスプ
リング１３の張力と背圧とによって押圧付勢され先端を
摺動接触するベーン１２が取り付けられている。ローラ
８の回転する空間は吸、排気口（図示せず）にそれぞれ
連通する吸入室１４と圧縮室１５とにベーン１２によっ
て仕切られている。Related to the conventional rotary hermetic compressor,
No. 894 has been proposed. This will be explained with reference to FIGS. 2 to 4. Figure 2 is a longitudinal cross-sectional view, Figure 3 is the second
4 is a sectional view taken along line mm in the figure, and FIG. 4 is a perspective view of the vane in FIG. 3. In the figure, 1 is a closed container, and an electric element 2 and a compression element 3 are arranged in the upper and lower parts of the closed container 1, respectively, and the electric element 2 is composed of a stator 4 and a rotor 5. The zero rotor 5 is fixed to the rotating shaft 6 constituting the compression element 3 by means such as press fitting or shrink fitting. When the rotor 5 rotates, the roller 8 rotatably fitted on the outer periphery of the eccentric portion 7 of the rotating shaft 6 moves into the space formed by the cylinder 9, the end face of the upper bearing 10, and the end face of the lower bearing 11. It is designed to rotate. The outer periphery of the roller 8 is slidably protruded from within a slot 16 formed in the cylinder 9 in the radial direction of the cylinder 9, and the rear side is pressed by the tension and back pressure of the spring 13, and the tip is brought into sliding contact. A vane 12 is attached. The space in which the roller 8 rotates is partitioned by a vane 12 into a suction chamber 14 and a compression chamber 15, which communicate with suction and exhaust ports (not shown), respectively.
上記の構造において、圧縮機を高速回転させると、ベー
ン１２の慣性が大きくなるのでベーン１２をスプリング
１３の張力及び背圧によって押し付けることが出来なく
なり、騒音及び摩耗を発生させる。このため、第４図に
示すようにベーン１２に複数の中空部１７を設け、ベー
ン１２を軽量化し慣性力の低減をはかっている。しかし
、この構造においては１本来扁平状を有しているベーン
なので中部に中空部分を効果的に設けると中空部１７の
両平板側に薄肉部１８が形成され、運転中にブレード１
２に、圧縮室１５と吸入室１４との差圧により繰返し荷
重を受ける際に、薄肉部１８がストレスによるクラック
を生じ破壊に至る可能性があると云う問題がある。また
、中空部１７の加工中に異物が入り運転中に出てきて摺
動面に入り込み異常摩耗を引き起こすおそれがある。In the above structure, when the compressor is rotated at high speed, the inertia of the vanes 12 increases, so that the vanes 12 cannot be pressed by the tension and back pressure of the springs 13, causing noise and wear. For this reason, as shown in FIG. 4, a plurality of hollow portions 17 are provided in the vane 12 to reduce the weight of the vane 12 and reduce the inertial force. However, in this structure, since the vane 1 originally has a flat shape, if a hollow part is effectively provided in the middle part, thin parts 18 are formed on both flat plate sides of the hollow part 17, and the blade 18 during operation.
Second, there is a problem that when subjected to repeated loads due to the pressure difference between the compression chamber 15 and the suction chamber 14, the thin wall portion 18 may crack due to the stress, leading to destruction. Further, there is a risk that foreign matter may enter the hollow portion 17 during processing and come out during operation, enter the sliding surface, and cause abnormal wear.
上記したように従来の技術においては、ベーン１２の慣
性質量を軽減するために中空部１７を設けても、新たに
中空部１７を設けたことによって発生する薄肉部１８の
強度低下について配慮がなされていなかった。As described above, in the conventional technology, even if the hollow portion 17 is provided to reduce the inertial mass of the vane 12, consideration is not given to the decrease in strength of the thin wall portion 18 that occurs due to the newly provided hollow portion 17. It wasn't.
本発明は上記の状況に鑑みなされたものであり、ベーン
の強度を落すことなくベーンの軽量化を図ることができ
る回転式密閉形圧縮機を提供することを目的としたもの
である。The present invention was made in view of the above situation, and an object of the present invention is to provide a rotary hermetic compressor that can reduce the weight of the vane without reducing its strength.
上記目的は、密閉形容器内に配設された吸、排気口を有
するシリンダと、該シリンダ内で回転軸に゛偏心部を介
し取り付けられるローラと、上記シリンダ内壁から半径
方向へスプリングを介し付勢し摺動自在に突出され上記
ローラ外周に先端が摺動接触するように形成されている
ベーンとを設けたものにおいて、上記ベーンに中空部を
設けると共に該中空部内に樹脂が充填されている回転式
密閉形圧縮機により達成される。The above purpose is to provide a cylinder having suction and exhaust ports disposed in a closed container, a roller attached to a rotating shaft via an eccentric part within the cylinder, and a roller attached from the inner wall of the cylinder in a radial direction via a spring. A vane is provided with a vane that protrudes so as to be slidable under pressure and whose tip is in sliding contact with the outer periphery of the roller, wherein the vane is provided with a hollow portion and the hollow portion is filled with resin. Achieved by a rotary hermetic compressor.
後述の実施例の説明にも述べられであるように、ベーン
１２の中空部１７にはベーン１２に比べて比重が小さい
樹脂１９が充填硬化されている。As described in the description of the embodiments below, the hollow portion 17 of the vane 12 is filled and hardened with a resin 19 whose specific gravity is smaller than that of the vane 12.
従って、ベーン１２の中空部１７は解消された形となり
側面２０に繰返し応力が加わっても、薄肉部１８にクラ
ックの発生はなくなる。Therefore, the hollow portion 17 of the vane 12 is in a closed shape, and even if repeated stress is applied to the side surface 20, no cracks will occur in the thin wall portion 18.
以下本発明の回転式密閉形圧縮機を実施例を用い従来と
同部品は同符号をもって示し同部分の構造の説明は省略
し第１図により説明する。第１図はベーンの斜視図であ
る１図において、ベーン１２に設けられた中空部１７に
は、ベーン１２より比重の小さな樹脂１９が充填硬化さ
れている。従って、全体の質量は、ベーン１２の材質に
よって中実になっている場合より、ベーン１２の材質と
樹脂１９との比重の差分だけ軽量化されている。Hereinafter, the rotary hermetic compressor of the present invention will be explained using an embodiment and referring to FIG. 1, where the same parts as the conventional one are designated by the same reference numerals, and the explanation of the structure of the same parts will be omitted. In FIG. 1, which is a perspective view of the vane, a hollow portion 17 provided in the vane 12 is filled with a resin 19 having a specific gravity smaller than that of the vane 12 and hardened. Therefore, the overall mass is reduced by the difference in specific gravity between the material of the vane 12 and the resin 19, compared to a case where the vane 12 is solid due to the material of the vane 12.
このため、高速運転時にも慣性力は小さくなり基本的な
寸法を変更することなくベーン１２の先端が口−ラ８か
ら離れることを防ぐことが可能である。また、樹脂１９
が充填硬化されていることにより、中空状態に保持され
るよりベーン１２として補強され、運転中にベーン１２
の側面２０に繰返し曲げ応力が加わっても薄肉部１８に
クラックが発生しないためベーン１２が破壊することが
ない。さらに、ベーン１２の中空部１７に加工中に侵入
し残留した異物が残ったとしても樹脂１９により中空部
１７の内壁に固定されてしまうため、中空部１７より飛
び出し循環し摺動面に入り込み異常摩耗を引き起こすこ
とがなくなる。Therefore, even during high-speed operation, the inertial force becomes small, and it is possible to prevent the tip of the vane 12 from separating from the lip 8 without changing the basic dimensions. In addition, resin 19
By being filled and hardened, the vane 12 is reinforced rather than held in a hollow state, and the vane 12 is hardened during operation.
Even if repeated bending stress is applied to the side surface 20 of the vane 12, no cracks will occur in the thin wall portion 18, so the vane 12 will not be destroyed. Furthermore, even if foreign matter enters the hollow part 17 of the vane 12 during processing and remains, it will be fixed to the inner wall of the hollow part 17 by the resin 19, so it will fly out from the hollow part 17 and circulate and enter the sliding surface, causing an abnormality. No more wear and tear.
このように本実施例の回転式密閉形圧縮機は。In this way, the rotary hermetic compressor of this embodiment is as follows.
ベーンに中空部を設け、この中空部に樹脂を充填硬化さ
せたことによりベーンの強度を低下させることなく軽量
化され、高速運転時にベーンとローラとが離れることな
く、たたき音の騒音の発生や異常摩耗の生じることを防
止できると共に、扁平状のベーンの側面側に形成される
薄肉部に高速運転時に繰返し荷重が加わってもそれは零
に等しく、ベーンの破損を阻止し信頼性を向上できる。By providing a hollow part in the vane and filling and hardening the resin in the hollow part, the weight of the vane is reduced without reducing its strength, and the vane and roller do not separate during high-speed operation, reducing the generation of knocking noise. Abnormal wear can be prevented from occurring, and even if repeated loads are applied to the thin wall portions formed on the side surfaces of the flat vanes during high-speed operation, the load is equal to zero, preventing damage to the vanes and improving reliability.
また、中空部に加工時の異物が残留するようなことがあ
っても、異物の摺動部侵入がなく異物による摩耗を防止
できる。Further, even if foreign matter remains in the hollow portion during processing, the foreign matter will not enter the sliding portion, and wear due to the foreign matter can be prevented.
以上記述した如く本発明の回転式密閉形圧縮機は、ベー
ンの強度を落すことなくベーンの軽量化を図ることがで
きる効果を有するものである。As described above, the rotary hermetic compressor of the present invention has the effect of reducing the weight of the vane without reducing its strength.
第１図は本発明の回転式密閉形圧縮機の実施例のベーン
の斜視図、第２図は従来の回転式密閉形圧縮機の縦断面
図、第３図は第２図のｍ−ｍ矢視断面図、第４図は第３
図のベーン斜視図である。
１・・・・・・密閉形容器、６・・・・・・回転軸、７
・・・・・・偏心部、８・・・・・・ローラ、９・・・
・・・シリンダ、１２・・・・・・ベーン、１３・・・
・・・スプリング、１７・・・・・・中空部、１８・・
・・・・薄肉部、１９・・・・・・樹脂、２０・・・・
・・側面。
￥−１１２］
１２、、、 ’（−ン
１１ｏ−＋墾仰
１８・・・蓬閂舒
１９・・・）＃龍
２０−．４曖り逼ｉFig. 1 is a perspective view of a vane of an embodiment of the rotary hermetic compressor of the present invention, Fig. 2 is a vertical cross-sectional view of a conventional rotary hermetic compressor, and Fig. 3 is taken along m-m of Fig. 2. Arrow sectional view, Figure 4 is the 3rd
FIG. 3 is a perspective view of the vane shown in FIG. 1... Sealed container, 6... Rotating shaft, 7
...Eccentric part, 8...Roller, 9...
...Cylinder, 12...Vane, 13...
...Spring, 17...Hollow part, 18...
... Thin wall part, 19 ... Resin, 20 ...
··side. ￥-112] 12,,, '(-n 11o-+Kenyo 18...Pengyo 19...)#Ryu 20-. 4 ambiguity
Claims (1)
ダと、該シリンダ内で回転軸に偏心部を介し取り付けら
れるローラと、上記シリンダ内壁から半径方向へスプリ
ングを介し付勢し摺動自在に突出され上記ローラ外周に
先端が摺動接触するように形成されているベーンとを設
けたものにおいて、上記ベーンに中空部を設けると共に
該中空部内に樹脂が充填されていることを特徴とする回
転式密閉形圧縮機。1. A cylinder disposed in a closed container and having suction and exhaust ports, a roller attached to a rotating shaft via an eccentric part within the cylinder, and a roller biased from the inner wall of the cylinder in the radial direction via a spring to slide. and a vane that freely protrudes and is formed so that its tip is in sliding contact with the outer periphery of the roller, characterized in that the vane has a hollow part and the hollow part is filled with resin. A rotary hermetic compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3144587A JPS63201391A (en) | 1987-02-16 | 1987-02-16 | Rotary hermetic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3144587A JPS63201391A (en) | 1987-02-16 | 1987-02-16 | Rotary hermetic compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63201391A true JPS63201391A (en) | 1988-08-19 |
Family
ID=12331448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3144587A Pending JPS63201391A (en) | 1987-02-16 | 1987-02-16 | Rotary hermetic compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63201391A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0367086A (en) * | 1989-08-04 | 1991-03-22 | Hitachi Ltd | Rotating machine and refrigerating device using said rotating machine |
| US5473111A (en) * | 1992-10-07 | 1995-12-05 | Mitsubishi Denki Kabushiki Kaisha | Shielded enclosure for housing electronic components and manufacturing method thereof |
| KR20040040196A (en) * | 2002-11-06 | 2004-05-12 | 엘지전자 주식회사 | Structure for reducing noise/vibration for enclosed compressor |
| DE10307040A1 (en) * | 2003-02-20 | 2004-09-16 | Luk Automobiltechnik Gmbh & Co. Kg | Vacuum pump, especially for power assisted vehicle braking system, includes vane having interior hollow spaces with closed injection holes |
| JP2006105039A (en) * | 2004-10-06 | 2006-04-20 | Matsushita Electric Ind Co Ltd | Multiple cylinder compressor |
| JP2010038084A (en) * | 2008-08-07 | 2010-02-18 | Panasonic Corp | Hermetic compressor |
| EP3054117A1 (en) * | 2013-10-01 | 2016-08-10 | Hitachi Automotive Systems, Ltd. | Valve timing control device for internal combustion engine |
| CN106321443A (en) * | 2016-10-17 | 2017-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding vane for compressor and compressor with sliding vane |
-
1987
- 1987-02-16 JP JP3144587A patent/JPS63201391A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0367086A (en) * | 1989-08-04 | 1991-03-22 | Hitachi Ltd | Rotating machine and refrigerating device using said rotating machine |
| US5473111A (en) * | 1992-10-07 | 1995-12-05 | Mitsubishi Denki Kabushiki Kaisha | Shielded enclosure for housing electronic components and manufacturing method thereof |
| KR20040040196A (en) * | 2002-11-06 | 2004-05-12 | 엘지전자 주식회사 | Structure for reducing noise/vibration for enclosed compressor |
| DE10307040A1 (en) * | 2003-02-20 | 2004-09-16 | Luk Automobiltechnik Gmbh & Co. Kg | Vacuum pump, especially for power assisted vehicle braking system, includes vane having interior hollow spaces with closed injection holes |
| JP2006105039A (en) * | 2004-10-06 | 2006-04-20 | Matsushita Electric Ind Co Ltd | Multiple cylinder compressor |
| JP2010038084A (en) * | 2008-08-07 | 2010-02-18 | Panasonic Corp | Hermetic compressor |
| EP3054117A1 (en) * | 2013-10-01 | 2016-08-10 | Hitachi Automotive Systems, Ltd. | Valve timing control device for internal combustion engine |
| EP3054117A4 (en) * | 2013-10-01 | 2017-05-03 | Hitachi Automotive Systems, Ltd. | Valve timing control device for internal combustion engine |
| US9995185B2 (en) | 2013-10-01 | 2018-06-12 | Hitachi Automotive Systems, Ltd. | Valve timing control device for internal combustion engine |
| CN106321443A (en) * | 2016-10-17 | 2017-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding vane for compressor and compressor with sliding vane |
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