JP3130704B2 - Hermetic compressor - Google Patents
Hermetic compressorInfo
- Publication number
- JP3130704B2 JP3130704B2 JP05146372A JP14637293A JP3130704B2 JP 3130704 B2 JP3130704 B2 JP 3130704B2 JP 05146372 A JP05146372 A JP 05146372A JP 14637293 A JP14637293 A JP 14637293A JP 3130704 B2 JP3130704 B2 JP 3130704B2
- Authority
- JP
- Japan
- Prior art keywords
- crankshaft
- compressor
- bearing
- compression mechanism
- hermetic compressor
- 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 - Fee Related
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Description
【０００１】[0001]
【発明の属する技術分野】本発明は、密閉形圧縮機及び
それを備えた冷凍装置に関するものである。TECHNICAL FIELD The present invention relates to a hermetic compressor and
The present invention relates to a refrigeration apparatus having the same.
【０００２】[0002]
【従来の技術】従来の一般的な往復動式密閉形圧縮機の
場合には、流体を圧縮するのに伴うピストンに作用する
荷重を、クランク軸を介して、フレームの軸受部にて受
ける構造になっており、小型の冷凍空調装置等に用いら
れる密閉形圧縮機においては、フレームの軸受部を１つ
とする片持ち構造として簡単化を図っている。2. Description of the Related Art In the case of a conventional general reciprocating hermetic compressor, a structure is used in which a load acting on a piston accompanying compression of a fluid is received by a bearing portion of a frame via a crankshaft. In a hermetic compressor used for a small refrigeration / air-conditioning apparatus or the like, the cantilever structure having one bearing portion of the frame is simplified.
【０００３】また、この種の片持ち構造の軸受部を有す
る密閉形圧縮機においては、製作が容易なことからクラ
ンク軸の主ジャーナル部、フレーム軸受部とも円筒形状
として、両者の間に適当なクリアランスを設けた真円滑
り軸受を主に採用している。Further, in a hermetic compressor having a cantilevered bearing of this type, the main journal portion and the frame bearing portion of the crankshaft are formed in a cylindrical shape because of easy manufacture, and an appropriate space is provided between the two. Mainly adopts a perfect circular bearing with clearance.
【０００４】また、従来の冷凍装置の冷凍サイクルに使
用されている冷媒としては、例えば冷蔵庫用にはＣＦＣ
１２、ルームエアコン用にはＨＣＦＣ２２と言った、分
子中に塩素元素を含む化合物が主に用いられている。As a refrigerant used in a refrigeration cycle of a conventional refrigeration system, for example, CFC is used for a refrigerator.
12. For room air conditioners, a compound containing a chlorine element in a molecule, such as HCFC22, is mainly used.
【０００５】なお、上記片持ち構造の軸受部を有する密
閉形圧縮機に関連するものとしては、例えば特開平４−
１１６２７７号公報が挙げられる。[0005] Incidentally, as the one related to the hermetic compressor having the above-mentioned cantilevered bearing portion, for example, Japanese Unexamined Patent Publication No.
No. 116277 is cited.
【０００６】[0006]
【発明が解決しようとする課題】上記従来技術の密閉形
圧縮機においては、ピストンに作用する圧縮荷重方向と
フレームの滑り軸受部中心が一致しない構造となるた
め、フレームの滑り軸受部で一様に荷重を受けることが
でない。また、滑り軸受にはクリアランスを設ける必要
があるため、クランク軸が滑り軸受内で傾き、滑り軸受
部の両端でエッジ状に接触して、この２点で集中的に荷
重を受けるいわゆる片当たり状態となる。このとき、モ
ーメントの釣合いを取るため、ピストンのある圧縮機構
部側の端点にもっとも大きな荷重が発生し、エッジ状に
接することもあいまって油膜が発生しにくく、この部分
の面圧が非情に高くなり、摺動部の摩耗、ひいては焼き
付き事故が発生することがあった。In the above-mentioned hermetic compressor of the prior art, the direction of the compressive load acting on the piston does not coincide with the center of the sliding bearing portion of the frame. Is not subject to any load. In addition, since it is necessary to provide clearance in the sliding bearing, the crankshaft is tilted in the sliding bearing, and the ends of the sliding bearing come into contact in an edge-like manner, and the load is concentrated at these two points, a so-called one-sided contact state. Becomes At this time, in order to balance the moment, the largest load is generated at the end point on the compression mechanism side where the piston is located, and the oil film is unlikely to be generated due to the edge contact, and the surface pressure in this part is unreasonably high In some cases, wear of the sliding portion and seizure accidents may occur.
【０００７】この対策として、従来は摺動部を長くする
ことによる軸受荷重の低減や、クランク軸に耐摩耗性の
表面処理を行う等の処置が取られ、信頼性を確保してき
た。しかし、摺動部を長くすることには限界があり、ま
た、長くしたところでフレームの滑り軸受部に作用する
加重を、ピストンの圧縮荷重より小さくすることはでき
ない。また、表面処理を行う対策ではクランク軸の主ジ
ャーナル部とフレーム滑り軸受部の金属接触は避けられ
ず、潤滑状態は境界潤滑となり、軸受摺動損失の増加を
招く。As a countermeasure against this, conventionally, measures such as reducing the bearing load by lengthening the sliding portion and performing a wear-resistant surface treatment on the crankshaft have been taken to ensure reliability. However, there is a limit to the length of the sliding portion, and the load acting on the sliding bearing portion of the frame cannot be made smaller than the compression load of the piston when the length is increased. Further, in the measures for performing the surface treatment, metal contact between the main journal portion of the crankshaft and the frame sliding bearing portion is inevitable, and the lubrication state becomes boundary lubrication, which causes an increase in bearing sliding loss.
【０００８】なお、特開平３−２３３１８１号公報記載
のスクロール圧縮機のように、クランク軸下端にも副軸
受を設けたり、実公昭５３−９９３０号公報記載のよう
に、ピストンの両側に軸受を設けてシャフトの傾きを規
制し、一様に軸を支承する方法もあるが、この方法では
圧縮機の機構が複雑で大形化となり、大幅なコストアッ
プとなる問題がある。Incidentally, a secondary bearing is provided at the lower end of the crankshaft as in the scroll compressor described in JP-A-3-233181, or bearings are provided on both sides of the piston as described in Japanese Utility Model Publication No. 53-9930. There is also a method in which the shaft is provided to regulate the inclination of the shaft and to uniformly support the shaft. However, this method has a problem that the mechanism of the compressor is complicated and large, and the cost is greatly increased.
【０００９】また、環境保護、特にオゾン層破壊の問題
から、冷媒として分子中に塩素元素を含むフロンの使用
が規制されることになった。特に冷蔵庫等に用いられて
いる分子中に水素元素を含まないフロンＣＦＣ１２等の
使用が先ず規制され、代替フロンとして塩素元素を全く
含まないＨＦＣ１３４ａ等が有力な候補に上がってお
り、その代替冷媒へ圧縮機の対応が急務となっている。[0009] In addition, due to the problem of environmental protection, especially the destruction of the ozone layer, the use of chlorofluorocarbon containing chlorine as a refrigerant has been restricted. In particular, the use of fluorocarbons such as CFC12, which does not contain hydrogen elements in the molecules used in refrigerators, etc., was first restricted, and HFC134a, which does not contain chlorine elements at all, has become a promising candidate as an alternative fluorocarbon. Compressors are urgently needed.
【００１０】しかしながら、代替候補のフロンは塩素元
素を含まないため、従来のような耐摩耗性、耐焼き付き
性に優れた塩化鉄等の皮膜の生成が期待できなくなり、
摺動部の信頼性が著しく低下することが指摘されてお
り、実際、前述のように面圧が高く、油膜も発生しにく
いクランク軸主ジャーナル部の圧縮機構部側の集中荷重
部において、クランク軸の摩耗、焼き付きと言った問題
が起こり、従来のようにクランク軸に表面処理を行う等
と言った対策だけでは不十分になってきた。However, since CFCs, which are alternative candidates, do not contain a chlorine element, the formation of a film such as iron chloride having excellent wear resistance and seizure resistance as in the prior art cannot be expected.
It has been pointed out that the reliability of the sliding portion is significantly reduced, and in fact, as described above, the concentrated load portion on the compression mechanism side of the crankshaft main journal portion where the surface pressure is high and an oil film is unlikely to be generated Problems such as abrasion and seizure of the shaft occur, and measures such as conventional surface treatment of the crankshaft have become insufficient.
【００１１】したがって、本発明の目的は、低コストで
摺動損失が低減されて効率が向上した密閉形圧縮機及び
それを備えた冷凍装置を提供することにある。Therefore, an object of the present invention is to provide a low cost
A hermetic compressor with reduced sliding loss and improved efficiency; and
In Rukoto to provide a refrigeration apparatus having the same.
【００１２】[0012]
【課題を解決するための手段】上記目的は、冷凍機油を
貯留した密閉容器内に、圧縮機構部と、この圧縮機構部
を駆動するクランク軸に連結されてこのクランク軸を回
転する電動機部と、このクランク軸の表面を前記圧縮機
構部と前記電動機部との間で支持する軸受部とを備えた
往復動式密閉形圧縮機であって、前記クランク軸の前記
軸受部の端部と摺動する表面に設けられ前記クランク軸
の径を小さくして形成された傾斜部を備えた密閉形圧縮
機により達成される。また、上記目的は、圧縮機と凝縮
器と蒸発器とが接続された冷凍サイクルを備えた冷凍装
置であって、前記圧縮機が、冷凍機油を貯留した密閉容
器内に、圧縮機構部と、この圧縮機構部を駆動するクラ
ンク軸に連結されてこのクランク軸を回転する電動機部
と、このクランク軸の表面を前記圧縮機構部と前記電動
機部との間で支持する軸受部とを備えた往復動式密閉形
圧縮機であって、前記クランク軸の前記軸受部の端部と
摺動する表面に設けられ前記クランク軸の径を小さくし
て形成された傾斜部を備えた冷凍装置によっても達成さ
れる。 The object of the present invention is to provide a refrigerating machine oil.
The compression mechanism and the compression mechanism are stored in the stored closed container.
Is connected to the crankshaft that drives the
A rotating motor section and the surface of the crankshaft
A bearing portion for supporting between the structure and the electric motor portion
A reciprocating hermetic compressor, wherein the crankshaft
The crankshaft provided on a surface that slides with an end of a bearing portion
Hermetic compression with a slope formed with a smaller diameter
Achieved by the machine . Also, the above purpose is
Refrigeration system equipped with a refrigeration cycle in which a heater and an evaporator are connected
A compressor, wherein the compressor is a sealed container storing refrigerating machine oil.
A compression mechanism and a clutch driving the compression mechanism
Motor section connected to the crankshaft to rotate this crankshaft
And the surface of the crankshaft is combined with the compression mechanism and the electric motor.
Reciprocating hermetic type with a bearing part to be supported between the machine part
An end of the bearing portion of the crankshaft;
The diameter of the crankshaft provided on the sliding surface is reduced.
Also achieved by a refrigeration system with a slope formed
It is.
【００１３】[0013]
【作用】上記の構成により、クランク軸と軸受部での圧
力が低減され、片当たりの発生が抑制される。このた
め、クランク軸と軸受部との間の油膜が破断して、焼き
付きが発生したり、摩耗が進んだりすることが抑制され
る。 According to the above construction, the pressure between the crankshaft and the bearing portion is reduced.
The force is reduced, and the occurrence of one-side contact is suppressed. others
The oil film between the crankshaft and bearing breaks,
The occurrence of sticking and the progress of wear are suppressed.
You.
【００１４】また、滑り軸受の潤滑を金属接触の起こる
ような境界潤滑から、油膜による流体潤滑状態を保つこ
とが出来るため、軸受での損失を小さくでき、効率の高
い圧縮機を提供することができる。Further, since the lubrication of the sliding bearing can be maintained in a state of fluid lubrication by an oil film from boundary lubrication in which metal contact occurs, a loss in the bearing can be reduced and a highly efficient compressor can be provided. it can.
【００１５】[0015]
【実施例】以下、図面にしたがって本発明の一実施例を
説明する。 〈実施例１〉この例では、始めに本発明の技術背景とな
る従来装置全体の構造について図７〜図１１にしたがっ
て説明し、その後に本発明の特徴部分を図１、図２にし
たがって説明する。図７は、密閉形圧縮機全体の構造を
示した縦断面図である。密閉形圧縮機は、密閉容器１内
に電動機部２、圧縮機構部３を収納し、バネ４を介して
密閉容器１に弾性的に支持されている。なお、圧縮機構
部３とは、後述するように密閉容器１内の電動機部２、
潤滑油５及びバネ４を除いた残りの圧縮機要素を総称し
たものである。An embodiment of the present invention will be described below with reference to the drawings. <Embodiment 1> In this embodiment, the overall structure of a conventional device, which is the technical background of the present invention, will be described first with reference to FIGS. 7 to 11, and then the features of the present invention will be described with reference to FIGS. I do. FIG. 7 is a longitudinal sectional view showing the structure of the whole hermetic compressor. The hermetic compressor accommodates an electric motor section 2 and a compression mechanism section 3 in a closed container 1 and is elastically supported by the closed container 1 via a spring 4. It should be noted that the compression mechanism unit 3 includes the electric motor unit 2 in the closed container 1 as described later,
This is a general term for the remaining compressor elements excluding the lubricating oil 5 and the spring 4.
【００１６】また、密閉容器１の底部には潤滑油５を貯
留しており、クランク軸６の回転遠心力により、縦穴６
ｃを通ってフレーム７の軸受部７ａ、クランク軸偏心部
６ａ等に給油する一方、クランク軸６の上部空間に吹き
上げて噴霧状とし、ピストン８の外周等にも潤滑油５を
供給する。A lubricating oil 5 is stored at the bottom of the sealed container 1.
The oil is supplied to the bearing portion 7a of the frame 7, the crankshaft eccentric portion 6a, and the like through the c, while being sprayed up into the upper space of the crankshaft 6 to supply the lubricating oil 5 to the outer periphery of the piston 8 and the like.
【００１７】電動機部２は、固定子２ａ及び回転子２ｂ
からなり、固定子２ａはフレーム７に固定され、回転子
２ｂはクランク軸６に焼き嵌めされている。The motor unit 2 includes a stator 2a and a rotor 2b.
The stator 2a is fixed to the frame 7 and the rotor 2b is shrink-fitted to the crankshaft 6.
【００１８】圧縮機構部３は、スコッチヨーク形と呼ば
れる往復動式のタイプを示しており、クランク軸６、こ
れを支承する軸受部７ａを有するフレーム７、クランク
軸６の偏心部６ａに嵌合されたスライダ９、スライダ９
が内部を往復動する管部（スライド管）８ａを一体に有
するピストン８、及びピストン８が往復運動するシリン
ダ１０、及びシリンダ１０の端面に設けられた吸入弁１
１、弁座板１２、吐出弁１３からなる弁機構、及び吸い
込みと吐出経路を分離するカバー体１４が順に設けら
れ、カバー体１４と密閉容器１外とが吐出パイプ１５に
より接続される構造となっている。The compression mechanism 3 is of a reciprocating type called a Scotch yoke type, and is fitted to a crankshaft 6, a frame 7 having a bearing 7a for supporting the same, and an eccentric portion 6a of the crankshaft 6. Slider 9, slider 9
, Which integrally has a pipe portion (slide pipe) 8 a in which the piston reciprocates, a cylinder 10 in which the piston 8 reciprocates, and a suction valve 1 provided on an end face of the cylinder 10
1, a valve mechanism including a valve seat plate 12 and a discharge valve 13, and a cover body 14 for separating suction and discharge paths are provided in order, and the cover body 14 and the outside of the sealed container 1 are connected by a discharge pipe 15. Has become.
【００１９】ピストン８の下降運動に従いシリンダ１０
内が負圧となって、吸入弁１１が開き、圧縮される流体
（主として冷媒ガス）は吸入パイプ１６より一旦密閉容
器１内に充満した後、シリンダ１０内の圧縮室１７に吸
い込まれる。次に吸い込みが終わりピストン８が下死点
から上昇運動に変わると吸入弁１１が閉じ、圧縮室１７
の容積が減少し流体の圧力が上昇する。流体の圧力が吐
出圧力に達すると、吐出弁１３が開き、ピストン８が上
死点に達するまで流体をカバー体１４の吐出室１４ａに
吐き出す。吐き出されたガスは吐出パイプ１５を通っ
て、密閉容器１外へと導かれる。以上のような吸入・圧
縮・吐出の３行程をクランク軸６の回転により繰り返
す。According to the downward movement of the piston 8, the cylinder 10
The inside becomes negative pressure, the suction valve 11 opens, and the fluid to be compressed (mainly refrigerant gas) once fills the closed vessel 1 through the suction pipe 16 and is then sucked into the compression chamber 17 in the cylinder 10. Next, when the suction is completed and the piston 8 changes from the bottom dead center to the upward movement, the suction valve 11 is closed, and the compression chamber 17 is closed.
And the pressure of the fluid increases. When the pressure of the fluid reaches the discharge pressure, the discharge valve 13 opens and discharges the fluid to the discharge chamber 14a of the cover body 14 until the piston 8 reaches the top dead center. The discharged gas is guided to the outside of the closed container 1 through the discharge pipe 15. The above three steps of suction, compression and discharge are repeated by the rotation of the crankshaft 6.
【００２０】この時、圧縮室１７内の圧力と密閉容器１
内の吸い込み圧力との差圧がピストン８に加わり、シリ
ンダ１０の中心方向に集中荷重Ｆが働くと考えられ、ス
ライダ９を介して、クランク軸偏心部６ａに作用し、ク
ランク軸主ジャーナル部６ｂを介してフレーム滑り軸受
部７ａで受ける。この集中荷重Ｆは、吸い込み圧力をほ
ぼ一定と考えると圧縮室１７の圧力上昇に比例して大き
くなり、クランク軸６の回転角に対して、図８のように
変化し、圧力が吐出圧力に達したときに最大となる。な
お、同図の横軸にはクランク軸６の回転角を括弧内に示
した。At this time, the pressure in the compression chamber 17 and the pressure in the closed vessel 1
It is considered that a pressure difference from the suction pressure in the cylinder is applied to the piston 8, and a concentrated load F acts in the center direction of the cylinder 10, acts on the crankshaft eccentric portion 6 a via the slider 9, and the crankshaft main journal portion 6 b At the frame sliding bearing 7a. When the suction pressure is considered to be substantially constant, the concentrated load F increases in proportion to the rise in the pressure in the compression chamber 17, and changes with respect to the rotation angle of the crankshaft 6 as shown in FIG. Maximum when reached. The rotation angle of the crankshaft 6 is shown in parentheses on the horizontal axis in FIG.
【００２１】図９は、一般的な滑り軸受のモデルを表わ
す横断面図である。クランク軸６が荷重Ｆ’により偏心
回転してくさび形の隙間が形成され、この隙間に潤滑油
５が供給されることにより、油膜圧力Ｐが発生して荷重
Ｆ’と釣合うと共に、最小油膜厚さｈ0離して軸６と軸
受７ａの接触を防止する。油膜の圧力Ｐは、図のように
理論的には最小油膜厚さｈ0の発生位置より後方には発
生しない。FIG. 9 is a cross-sectional view showing a model of a general plain bearing. The crankshaft 6 is eccentrically rotated by the load F ′ to form a wedge-shaped gap. By supplying the lubricating oil 5 to the gap, an oil film pressure P is generated and balanced with the load F ′. separated thickness h 0 to prevent contact of the shaft 6 and the bearing 7a. The pressure P of the oil film does not theoretically occur behind the position where the minimum oil film thickness h 0 occurs, as shown in the figure.
【００２２】ところで、ピストン８に作用する圧縮荷重
方向とフレーム滑り軸受部７ａの中心Ｏ1、Ｏ2は一致し
ない構造となるため、モーメントが発生し、フレームの
滑り軸受部７ａで一様に荷重Ｆを受けることがでない。
また、滑り軸受７ａには適当なクリアランスを設ける必
要があるため、クランク軸６が滑り軸受７ａ内で傾き、
従来の圧縮機においては、図１０に示したように、滑り
軸受部７ａの両端でエッジ状に接触して、この２点（７
ｂ、７ｃ）で集中的に荷重Ｍ１、Ｍ２が発生するいわゆ
る片当たり状態となる。この時、力及びモーメントの釣
合いより、Ｍ１、Ｍ２は次式（１）、（２）となる。Since the direction of the compressive load acting on the piston 8 and the centers O 1 and O 2 of the frame sliding bearing portion 7a do not coincide with each other, a moment is generated, and a uniform load is applied to the sliding bearing portion 7a of the frame. I can't get F.
Further, since it is necessary to provide an appropriate clearance for the slide bearing 7a, the crankshaft 6 is tilted in the slide bearing 7a,
In the conventional compressor, as shown in FIG. 10, the two ends (7
In b) and 7c), a so-called one-sided contact state in which loads M1 and M2 are concentrated occurs. At this time, M1 and M2 are given by the following equations (1) and (2) based on the balance between the force and the moment.
【００２３】[0023]
【数１】Ｍ１＝（１＋Ｌ１／Ｌ２）× Ｆ …（１）M1 = (1 + L1 / L2) × F (1)
【００２４】[0024]
【数２】Ｍ２＝ Ｌ１／Ｌ２ × Ｆ …（２） よって、ピストン８のある圧縮機構部側の端点７ｂに最
も大きな荷重Ｍ１が、ピストンに作用する流体圧縮力Ｆ
に比例して発生する。図１１は、この端点７ｂ部を拡大
し、クランク軸６の傾きによりできたくさび形部に発生
する油膜圧力分布を示した図である。油膜圧力Ｐは隙間
が大きくなると小さくなるので、軸受７ａの面取り部７
ａ’側には発生せず、ジャーナル６ｂ側に発生する範囲
も限られ、荷重Ｍ１を負荷するために図示のように高い
面圧分布となり、最小油膜厚さｈ1が厚く形成されない
傾向にある。そして１回転中で荷重Ｍ１が最大となった
とき、ついに油膜の負荷能力を越えて油膜の破断あるい
は端点７ｂ、７ｃの金属接触が起こり、摺動部の摩耗、
ひいては焼き付き事故が発生することがあった。M2 = L1 / L2 × F (2) Therefore, the largest load M1 is applied to the end point 7b on the compression mechanism side where the piston 8 is located, and the fluid compression force F acting on the piston is
Occurs in proportion to FIG. 11 is a diagram showing an oil film pressure distribution generated in a wedge-shaped portion formed by the inclination of the crankshaft 6 by enlarging the end point 7b. Since the oil film pressure P decreases as the clearance increases, the chamfered portion 7 of the bearing 7a
a 'side does not occur in, also limited range which occurs in the journal 6b side, a high surface pressure distribution as shown to a load M1, tends to minimize oil film thickness h 1 is not formed thickly . When the load M1 reaches a maximum during one rotation, the oil film finally exceeds the load capability of the oil film and breaks of the oil film or metal contact of the end points 7b and 7c occurs, and wear of the sliding portion,
Eventually, burn-in accidents occurred.
【００２５】この対策として、従来は、軸受部７ａの長
さＬ２（図１０参照）を大きくすることによる軸受荷重
の低減や、クランク軸６（特に主ジャーナル部６ｂ）に
表面処理を行うなどの処置が取られてきた。As countermeasures against this, conventionally, the bearing load has been reduced by increasing the length L2 (see FIG. 10) of the bearing portion 7a, and the crankshaft 6 (particularly the main journal portion 6b) has been subjected to surface treatment. Action has been taken.
【００２６】しかしながら、前述のＬ２を大きくするに
は構造的に限界があり、また、大きくしたところでＭ１
をＦより小さくすることはできない。また、表面処理を
行う対策ではクランク軸６の主ジャーナル部６ｂとフレ
ーム滑り軸受部７ａの端点７ｂ、７ｃの金属接触は避け
られず、潤滑状態は境界潤滑となり、軸受摺動損失の増
加を招く。However, there is a structural limit to increasing the above-mentioned L2.
Cannot be smaller than F. Further, in the measures for performing the surface treatment, metal contact between the main journal portion 6b of the crankshaft 6 and the end points 7b and 7c of the frame sliding bearing portion 7a is inevitable, and the lubricating state is boundary lubrication, which causes an increase in bearing sliding loss. .
【００２７】そこで本発明においては、以下に詳述する
ように摺動部を流体潤滑状態を保って摺動損失の低減を
図ると共に、表面処理を行わなくとも高い信頼性を確保
できる構造を実現するものである。摺動部を流体潤滑に
保つには、クランク軸６の主ジャーナル部６ｂとフレー
ムの滑り軸受部７ａの圧縮機構部側の集中荷重部の接触
部が、従来の点接触から、油膜を介して少なくとも最大
荷重点で面接触となるような形状とすればよい。さらに
詳述すれば、軸受クリアランス内でのクランク軸６の傾
きに応じた傾斜部を、クランク軸主ジャーナル部６ｂも
しくはフレーム滑り軸受部７ａの少なくとも一方に設け
ればよい。この実施例では前者のクランク軸主ジャーナ
ル部６ｂに傾斜部を設けた場合につき、図１、図２にし
たがって説明する。Therefore, in the present invention, as described in detail below, a sliding portion is maintained in a fluid lubricated state to reduce a sliding loss and realize a structure capable of securing high reliability without performing surface treatment. Is what you do. In order to maintain the sliding portion in fluid lubrication, the contact portion between the main journal portion 6b of the crankshaft 6 and the concentrated load portion on the compression mechanism side of the sliding bearing portion 7a of the frame is changed from the conventional point contact through an oil film. What is necessary is just to make it the shape which makes surface contact at least at the maximum load point. More specifically, an inclined portion corresponding to the inclination of the crankshaft 6 within the bearing clearance may be provided on at least one of the crankshaft main journal portion 6b and the frame sliding bearing portion 7a. In this embodiment, the former case in which an inclined portion is provided in the crankshaft main journal portion 6b will be described with reference to FIGS.
【００２８】図１は、軸受摺動部の要部断面図であり、
ピストン８に作用する荷重が少なくとも最大となるクラ
ンク軸６の回転角の範囲において、クランク軸主ジャー
ナル６ｂの圧縮機構部側の集中荷重部に傾斜面１８を設
けたものである。FIG. 1 is a sectional view of a main part of a bearing sliding portion.
In the range of the rotation angle of the crankshaft 6 at which the load acting on the piston 8 becomes at least the maximum, the inclined surface 18 is provided in the concentrated load portion on the compression mechanism side of the crankshaft main journal 6b.
【００２９】滑り軸受７ａの直径クリアランスは大体軸
の直径の１０００分の１程度に設定される。寸法例とし
て、冷蔵庫用の小形圧縮機の場合を挙げると、クランク
軸６の直径をφ１８ｍｍとするとクリアランスは１８μ
ｍとなる。よって、滑り軸受部７ａの長さＬ２を４０ｍ
ｍとした場合、軸受内でのクランク軸６の傾きθは、ａ
ｒｃｔａｎ（０．０１８／４０）≒０．０３°程度の微
小な角度となるので、この値、もしくは若干大きな値の
傾斜部１８を適当な幅Ｂに渡って設けている。The diameter clearance of the slide bearing 7a is set to approximately one thousandth of the diameter of the shaft. As an example of the dimensions, in the case of a small compressor for a refrigerator, if the diameter of the crankshaft 6 is φ18 mm, the clearance is 18 μm.
m. Therefore, the length L2 of the sliding bearing portion 7a is set to 40 m.
m, the inclination θ of the crankshaft 6 in the bearing is a
Since the angle is a minute angle of about rctan (0.018 / 40) ≒ 0.03 °, the inclined portion 18 having this value or a slightly larger value is provided over an appropriate width B.
【００３０】図２は、この微小傾斜部１８を拡大し、油
膜による圧力分布Ｐを示した図である。このことから、
クランク軸主ジャーナル６ｂの圧縮機構部側の集中荷重
部を軸受端７ｂの点接触状態から緩やかな面接触とする
ことができ、図示のように面圧Ｐが低下すると共に油膜
の発生が容易となる。一旦油膜５が発生すれば、油膜に
よる受圧面が拡大し、最小油膜厚さｈ2部の両側にも油
膜が発生するので、面圧（油圧）が従来に比べ小さくな
り、更に油膜厚さが増加して軸受部７ａの流体潤滑状態
が確実なものとなる。FIG. 2 is a diagram showing the pressure distribution P by the oil film by enlarging the minute inclined portion 18. As shown in FIG. From this,
The concentrated load portion on the compression mechanism side of the crankshaft main journal 6b can be changed from a point contact state of the bearing end 7b to a gradual surface contact, so that the surface pressure P decreases as shown in FIG. Become. Once the oil film 5 is generated to expand the pressure-receiving surface by the oil film, since an oil film is also generated on both sides of the minimum oil film thickness h 2 parts, the surface pressure (hydraulic pressure) becomes smaller than the conventional, more oil film thickness As a result, the fluid lubrication state of the bearing portion 7a is ensured.
【００３１】ここで、傾斜部１８を設ける幅Ｂは、流体
潤滑状態を保つのに必要な面圧低減を図り得る長さ設け
れば良く、約３〜７ｍｍ程度、傾斜部の深さｄは３〜７
μｍ程度とすれば良い。なお、深さｄの傾斜部１８の傾
斜角をθ0、軸受内でのクランク軸６の傾きをθとした
時、好ましい傾斜角θ0は２θ≧θ0≧θとなる。Here, the width B at which the inclined portion 18 is provided may be set to a length capable of reducing the surface pressure necessary for maintaining the fluid lubricating state, and is about 3 to 7 mm. 3-7
It may be about μm. When the inclination angle of the inclined portion 18 having the depth d is θ 0 and the inclination of the crankshaft 6 in the bearing is θ, a preferable inclination angle θ 0 is 2θ ≧ θ 0 ≧ θ.
【００３２】〈実施例２〉上記実施例１では、傾斜部１
８をクランク軸主ジャーナル部６ｂの一部、少なくとも
集中加重部に偏在して設けたが、軸加工の容易さを考慮
して全周に設けることもできる。図３は、この全周に設
けた例を示したものである。前述のように傾斜部の深さ
ｄは数μｍ程度であるので、クランク軸主ジャーナル部
６ｂの仕上げ研磨に用いる研磨砥石１９に、予め傾斜部
１８に相当する部分を砥石ドレッシング時に設けてお
き、主ジャーナルの研磨加工と同時に傾斜部１８の加工
を行うものである。<Embodiment 2> In Embodiment 1 described above, the inclined portion 1
Although 8 is unevenly provided at a part of the crankshaft main journal portion 6b, at least in the concentrated weight portion, it may be provided on the entire circumference in consideration of easiness of shaft machining. FIG. 3 shows an example provided on the entire circumference. As described above, since the depth d of the inclined portion is about several μm, a portion corresponding to the inclined portion 18 is provided in advance in the grinding wheel 19 used for finish polishing of the crankshaft main journal portion 6b at the time of dressing the grindstone. The processing of the inclined portion 18 is performed simultaneously with the polishing of the main journal.
【００３３】よって、従来別工程で行っていた表面処理
を行う場合に比べ、コストを下げることが可能である。
また、この時の傾斜部１８の形状は、全周に渡って傾斜
面となるテーパ状となるため、クランク軸６の１回転中
に渡り、圧縮機構部側の集中荷重部を緩やかな面接触と
することができ、信頼性を高めることができる。Therefore, the cost can be reduced as compared with the case where the surface treatment is conventionally performed in a separate process.
In addition, since the shape of the inclined portion 18 at this time is a tapered shape that becomes an inclined surface over the entire circumference, the concentrated load portion on the compression mechanism side has gentle surface contact over one rotation of the crankshaft 6. And the reliability can be improved.
【００３４】なお、このようにクランク軸にテーパ部を
設けるものとしては、先に示した実公昭５３−９９３０
号公報にも見られるが、この例はピストンの両側に軸受
を設けてシャフトの傾きを規制し、一様に軸を支承する
構造のもので、本件発明のように片持ち支承構造ではな
く、また、給油穴から軸受に侵入してくる１００μｍの
大きさの異物を排除するために、給油穴から鉛直下方に
向けて直径で２００μｍ程度の大きなテーパを必要とし
ており、本発明の如き面圧低減を目的とした微小テーパ
を設けるものではない。The provision of the tapered portion on the crankshaft is described in Japanese Utility Model Publication No. 53-9930 described above.
However, this example has a structure in which bearings are provided on both sides of the piston to restrict the inclination of the shaft and to uniformly support the shaft. Further, a large taper having a diameter of about 200 μm is required vertically downward from the oil supply hole in order to eliminate foreign matter having a size of 100 μm entering the bearing from the oil supply hole. It does not provide a minute taper for the purpose.
【００３５】〈実施例３〉図４は、本発明に係るさらに
異なる他の実施例を示す軸受摺動部の要部断面図を示し
たもので、フレーム７側における軸受７ａの集中荷重部
に傾斜部１８を設けた場合である。この場合も傾斜部１
８の寸法は、実施例１のクランク軸側に傾斜部を設ける
場合と同様である。傾斜部１８を設ける周方向位置は、
ピストン荷重方向が一定のため、この一方向のみに設け
れば、クランク軸１回転中に渡って、圧縮機構部側の集
中荷重部を緩やかな面接触とすることができる。<Embodiment 3> FIG. 4 is a cross-sectional view of a main part of a bearing sliding portion showing a further different embodiment according to the present invention. This is a case where the inclined portion 18 is provided. Also in this case, the inclined portion 1
The size of 8 is the same as that of the first embodiment in which the inclined portion is provided on the crankshaft side. The circumferential position where the inclined portion 18 is provided is
Since the piston load direction is constant, if it is provided only in this one direction, the concentrated load portion on the compression mechanism side can be in gentle surface contact during one rotation of the crankshaft.
【００３６】〈実施例４〉図４に示した実施例３と基本
的には同様の構造であるが、フレーム７における軸受７
ａの端部全周に渡って傾斜部１８を設けた。図面は省略
したが、実施例２の場合と同様に全周にわたり傾斜部を
設けるため傾斜加工が容易である。<Embodiment 4> The structure is basically the same as that of Embodiment 3 shown in FIG.
The inclined portion 18 is provided over the entire periphery of the end portion a. Although illustration is omitted, as in the case of the second embodiment, the inclined portion is provided over the entire circumference, so that the inclined processing is easy.
【００３７】〈実施例５〉上記のように圧縮機の軸受摺
動部の信頼性が向上するのであるが、特に次ぎのような
場合に重要である。すなわち、冷凍空調分野の圧縮機は
作動媒体として、フロン系の冷媒を主に使用している。
冷蔵庫ではＣＦＣ１２、ルームエアコンではＨＣＦＣ２
２などが用いられており、冷媒の一部は潤滑油中に溶解
して潤滑油の粘度が下がり、摺動部の信頼性を下げる働
きをするが、前記冷媒は分子中に塩素を含んでおり、摺
動条件が厳しくなると冷媒分子が分解してできた塩素が
摺動部の表面金属と化合物（例えば塩化鉄など）皮膜を
形成する。塩化鉄皮膜は自己潤滑性をもっており極圧添
加剤として働き、摺動部の摩耗、焼き付きを防いで信頼
性を高める働きを持っていた。しかしフロン中に含まれ
る塩素がオゾン層を破壊するということから、環境保全
上これら塩素を含むフロンガスは使用が規制されること
になっており、塩素を含まない代替フロンの使用が検討
されている。<Embodiment 5> As described above, the reliability of the bearing sliding portion of the compressor is improved, but it is particularly important in the following cases. That is, a compressor in the field of refrigeration and air conditioning mainly uses a CFC-based refrigerant as a working medium.
CFC12 for refrigerator, HCFC2 for room air conditioner
2 and the like are used, a part of the refrigerant is dissolved in the lubricating oil, the viscosity of the lubricating oil is reduced, and works to reduce the reliability of the sliding portion, but the refrigerant contains chlorine in the molecule. When the sliding conditions become severe, chlorine formed by the decomposition of the refrigerant molecules forms a compound film (for example, iron chloride) with the surface metal of the sliding portion. The iron chloride film had a self-lubricating property, functioned as an extreme pressure additive, and had a function of preventing abrasion and seizure of sliding parts and improving reliability. However, since chlorine contained in CFCs destroys the ozone layer, the use of these CFCs containing chlorine is to be regulated for environmental protection, and the use of alternative CFCs that do not contain chlorine is being considered. .
【００３８】代替冷媒の候補としてＨＦＣ１３４ａなど
が検討されているが、運転圧力条件的には吐出と吸入と
の圧力差が従来より大きくなり、摺動条件が厳しく、さ
らに塩素がないため、摺動部の摩耗、焼き付きが起き易
く、信頼性が低下する問題がでてきた。しかし本発明の
構造を用いれば、フレーム軸受部の摺動信頼性は向上し
ているため、塩素を含まない代替冷媒の使用を可能とす
ることができる。HFC134a has been studied as a candidate for an alternative refrigerant. However, in terms of operating pressure conditions, the pressure difference between discharge and suction is larger than before, and the sliding conditions are strict. Abrasion and seizure of the part are apt to occur, and there has been a problem that reliability is lowered. However, when the structure of the present invention is used, since the sliding reliability of the frame bearing portion is improved, it is possible to use an alternative refrigerant containing no chlorine.
【００３９】本発明の圧縮機を冷凍システムにて使用し
た場合の一実施例を説明する。図５は、本発明の圧縮機
を用いた冷蔵庫、ルームエアコン等で用いられる最も単
純な冷凍サイクルの模式図である。An embodiment in which the compressor of the present invention is used in a refrigeration system will be described. FIG. 5 is a schematic diagram of the simplest refrigeration cycle used in refrigerators, room air conditioners, and the like using the compressor of the present invention.
【００４０】配管により、圧縮機２０の吐出側は凝縮器
２１、絞り機構２２、蒸発器２３とつながれ、圧縮器２
０の吸入側に接続される。圧縮機２０はサイクル内に封
入された冷媒ガスを圧縮して圧力、温度を高めて循環さ
せる働きをする。冷媒は凝縮器２１で周囲に熱を放出し
て液体となり、絞り機構２２で圧力を減じられ低圧・低
温となり、蒸発器２３で周囲の熱を奪って再びガスとな
り圧縮機に戻り、これを繰り返す。このような冷凍空調
システム等の機器の心臓部といえるものが圧縮機であ
り、圧縮機の効率がこれらのシステムの消費電力量を決
める大きな要因となる。本発明の効率の高い圧縮機を用
いれば、これら年間使用電力量の大きなシステムの節電
に大いに貢献することができる。The discharge side of the compressor 20 is connected to a condenser 21, a throttle mechanism 22, and an evaporator 23 by piping.
0 is connected to the suction side. The compressor 20 functions to compress the refrigerant gas sealed in the cycle, increase the pressure and temperature, and circulate the refrigerant gas. The refrigerant emits heat to the surroundings in the condenser 21 to become a liquid, the pressure is reduced by the expansion mechanism 22 to a low pressure and low temperature, the surrounding heat is removed in the evaporator 23 to return to a gas, and returns to the compressor. . Compressors are at the heart of such refrigeration and air conditioning systems, and the efficiency of the compressor is a major factor in determining the power consumption of these systems. The use of the high-efficiency compressor of the present invention can greatly contribute to power saving of these systems that use a large amount of electric power annually.
【００４１】図６は、本発明の実施例１〜４の圧縮機
と、比較例としてクランク軸主ジャーナル部６ｂに傾斜
部１８を設けない従来構造の圧縮機とについて、それぞ
れ軸受の集中荷重部における摩耗量を計測し、対比した
結果を示したものである。なお、摩耗試験の条件は、何
れも図５と同等な冷蔵庫の運転状態を模擬した冷凍サイ
クルを用い、冷媒としては、塩素元素を含むフロンガス
ＣＦＣ−１２と、塩素元素を含まないＨＦＣ−１３４ａ
とについてそれぞれ計測した。FIG. 6 shows the concentrated load portions of the bearings of the compressors according to the first to fourth embodiments of the present invention and the conventional compressor having no inclined portion 18 in the crankshaft main journal portion 6b as a comparative example. 5 shows the results of measurement of the amount of abrasion and comparison of the results. In addition, the conditions of the abrasion test used the refrigerating cycle which simulated the operation state of the refrigerator equivalent to FIG. 5, and as the refrigerant, Freon gas CFC-12 containing chlorine element and HFC-134a containing no chlorine element.
And were respectively measured.
【００４２】この特性図から明らかなように、本実施例
の場合は、塩素元素を含まない冷媒ＨＦＣ−１３４ａで
あっても塩素元素を含むＣＦＣ−１２と大差なく、ま
た、塩素元素を含まない冷媒ＨＦＣ−１３４ａにおいて
は、従来の圧縮機よりも格段に摩耗量が少なく、信頼性
の高い圧縮機であることを確認した。As is clear from this characteristic diagram, in the case of the present embodiment, even the refrigerant HFC-134a containing no chlorine element is not much different from the CFC-12 containing chlorine element, and does not contain chlorine element. In the refrigerant HFC-134a, the amount of wear was remarkably smaller than that of the conventional compressor, and it was confirmed that the refrigerant was a highly reliable compressor.
【００４３】[0043]
【発明の効果】以上詳述したように、本発明により低コ
ストで摺動損失が低減されて効率が向上した密閉形圧縮
機及びそれを備えた冷凍装置を実現するという所期の目
的を達成することができた。As described in detail above, according to the present invention, low cost
Hermetic compression with reduced sliding loss and improved efficiency
The intended purpose of realizing a chiller and a refrigeration apparatus including the same has been achieved.
【００４４】[0044]
【００４５】[0045]
【図１】本発明に係る一実施例を示す軸受摺動要部断面
図。FIG. 1 is a sectional view of a main part of a bearing slide showing an embodiment according to the present invention.
【図２】図１の要部拡大図。FIG. 2 is an enlarged view of a main part of FIG.
【図３】同じく他の実施例となる傾斜部の加工方法を示
すモデル図。FIG. 3 is a model diagram showing a method of processing an inclined portion according to another embodiment.
【図４】同じく軸受摺動要部断面図。FIG. 4 is a cross-sectional view of a main part of the sliding bearing.
【図５】同じく本発明に係る圧縮機の一応用例示す冷凍
サイクルの模式図。FIG. 5 is a schematic view of a refrigeration cycle showing another application example of the compressor according to the present invention.
【図６】同じく軸受の摩耗量を従来装置と対比して計測
した特性図。FIG. 6 is a characteristic diagram in which a wear amount of a bearing is measured in comparison with a conventional device.
【図７】同じく圧縮機全体の構造を示した縦断面図。FIG. 7 is a longitudinal sectional view showing the structure of the entire compressor.
【図８】クランク軸の回転位置とピストンに作用する荷
重との関係を示した特性図。FIG. 8 is a characteristic diagram showing a relationship between a rotational position of a crankshaft and a load acting on a piston.
【図９】一般的な滑り軸受のモデル図。FIG. 9 is a model diagram of a general plain bearing.
【図１０】従来の密閉形圧縮機の軸受要部断面図。FIG. 10 is a sectional view of a main part of a bearing of a conventional hermetic compressor.
【図１１】図９の要部拡大図。FIG. 11 is an enlarged view of a main part of FIG. 9;
５…潤滑油、 ６…クランク軸、 ６
ａ…偏心部、７…フレーム、 ７ａ…滑り軸受
部、 ８…ピストン、８ａ…スライド管、
１０…シリンダ、 １８…傾斜部、Ｂ…傾斜部
の幅、 ｄ…傾斜部の深さ、θ…軸受内でのクラ
ンク軸６の傾き角度。5 ... lubricating oil, 6 ... crankshaft, 6
a: eccentric portion, 7: frame, 7a: sliding bearing portion, 8: piston, 8a: slide tube,
10: cylinder, 18: slope, B: width of slope, d: depth of slope, θ: angle of inclination of crankshaft 6 in bearing.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 内田 宏政 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業 部内 (72)発明者 山本 光司 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業 部内 (72)発明者 鈴木 一浩 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業 部内 (72)発明者 大和田 弘康 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業 部内 (56)参考文献 特開 昭59−208180（ＪＰ，Ａ) 実開 平２−94451（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F04B 39/00 103 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hiromasa Uchida 800, Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture Living Equipment Division, Hitachi, Ltd. Hitachi, Ltd. Living Equipment Division (72) Inventor Kazuhiro Suzuki 800, Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture Hitachi, Ltd. Living Equipment Division (72) Hiroya Owada 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Shares (56) References JP-A-59-208180 (JP, A) JP-A-2-94451 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F04B 39/00 103
Claims (4)
構部と、この圧縮機構部を駆動するクランク軸に連結さ
れてこのクランク軸を回転する電動機部と、このクラン
ク軸の表面を前記圧縮機構部と前記電動機との間で支持
する軸受部とを備えた往復動式密閉形圧縮機であって、
前記クランク軸の前記軸受部の端部と摺動する表面に設
けられ前記クランク軸の径を小さくして形成された傾斜
部を備えた密閉形圧縮機。1. A compressor in a closed container storing refrigerating machine oil.
And構部, it is connected to a crank shaft for driving the compression mechanism section
Motor that rotates the crankshaft
The shaft surface is supported between the compression mechanism and the electric motor.
A reciprocating hermetic compressor provided with a bearing portion for,
The crankshaft is provided on the surface that slides with the end of the bearing.
The inclination formed by reducing the diameter of the crankshaft
Hermetic compressor with a section .
受部の端部と摺動する、前記クランク軸の表面に形成さ
れた請求項１に記載の密閉形圧縮機。2. The shaft according to claim 1, wherein the inclined portion is provided on the shaft on the compression mechanism side.
Formed on the surface of the crankshaft, which slides with the end of the receiving part
The hermetic compressor according to claim 1 .
される流体が、塩素元素を含まない物質からなる冷媒で
ある請求項１もしくは２記載の密閉形圧縮機。3. The compressor of the hermetic compressor is compressed by the compression mechanism.
Fluid is a refrigerant made of a substance that does not contain chlorine.
Hermetic compressor of a claim 1 or 2 wherein.
凍サイクルを備えた冷凍装置であって、 前記圧縮機が、冷凍機油を貯留した密閉容器内に、圧縮
機構部と、この圧縮機構部を駆動するクランク軸に連結
されてこのクランク軸を回転する電動機部と、このクラ
ンク軸の表面を前記圧縮機構部と前記電動機との間で支
持する軸受部とを備えた往復動式密閉形圧縮機であっ
て、前記クランク軸の前記軸受部の端部と摺動する表面
に設けられ前記クランク軸の径を小さくして形成された
傾斜部を備えた冷凍装置。 4. A cooling system in which a compressor, a condenser and an evaporator are connected.
A refrigeration apparatus provided with a freezing cycle, wherein the compressor compresses the refrigerant in a closed container storing refrigerating machine oil.
Connected to the mechanism and the crankshaft that drives this compression mechanism
The motor section that rotates the crankshaft
The surface of the link shaft is supported between the compression mechanism and the motor.
Reciprocating hermetic compressor with bearings
The surface of the crankshaft that slides with the end of the bearing portion
Formed with a reduced diameter of the crankshaft
A refrigeration system having a slope.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05146372A JP3130704B2 (en) | 1993-06-17 | 1993-06-17 | Hermetic compressor |
| KR1019930017952A KR940007372A (en) | 1992-09-11 | 1993-09-08 | Enclosed Type Voltage Accumulator |
| CN93119077A CN1036021C (en) | 1992-09-11 | 1993-09-11 | Closed type electromotive compressor |
| KR2019970030362U KR0129804Y1 (en) | 1992-09-11 | 1997-10-31 | Hermetic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05146372A JP3130704B2 (en) | 1993-06-17 | 1993-06-17 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH074355A JPH074355A (en) | 1995-01-10 |
| JP3130704B2 true JP3130704B2 (en) | 2001-01-31 |
Family
ID=15406232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05146372A Expired - Fee Related JP3130704B2 (en) | 1992-09-11 | 1993-06-17 | Hermetic compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3130704B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008121633A (en) * | 2006-11-15 | 2008-05-29 | Sanden Corp | Compressor |
| JP4894750B2 (en) * | 2007-12-25 | 2012-03-14 | 株式会社デンソー | Compressor |
| US11143442B2 (en) | 2016-11-18 | 2021-10-12 | Panasonic Intellectual Property Management Co., Ltd. | Refrigerant compressor and freezer including same |
| JP2019190427A (en) * | 2018-04-27 | 2019-10-31 | 日立グローバルライフソリューションズ株式会社 | Compressor and apparatus using the same |
| US20210340967A1 (en) * | 2018-11-08 | 2021-11-04 | Panasonic Appliances Regrigeration Devices Singapore | Refrigerant compressor and refrigeration apparatus using the same |
| JP2020190266A (en) * | 2019-05-20 | 2020-11-26 | 日立グローバルライフソリューションズ株式会社 | Bearing structure, compressor incorporated with bearing structure, and refrigeration cycle device having compressor |
-
1993
- 1993-06-17 JP JP05146372A patent/JP3130704B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH074355A (en) | 1995-01-10 |
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