JPH11247761A - Hermetic compressor - Google Patents
Hermetic compressorInfo
- Publication number
- JPH11247761A JPH11247761A JP5176398A JP5176398A JPH11247761A JP H11247761 A JPH11247761 A JP H11247761A JP 5176398 A JP5176398 A JP 5176398A JP 5176398 A JP5176398 A JP 5176398A JP H11247761 A JPH11247761 A JP H11247761A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- crankshaft
- outer diameter
- crank shaft
- sliding member
- 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.)
- Granted
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、冷凍、空調用の冷
媒圧縮機として用いられる密閉形圧縮機に関するもので
ある。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic compressor used as a refrigerant compressor for refrigeration and air conditioning.
【０００２】[0002]
【従来の技術】密閉形圧縮機として、レシプロ、ロータ
リ、スクロール等の様々なタイプの圧縮機が知られてい
る。ここでは従来技術の説明をスクロール圧縮機を例と
って説明する。図５にスクロール圧縮機の縦断面図を示
す。密閉容器１内に、圧縮機構部２と電動機部９とがク
ランク軸６を介して連結して収納される。圧縮機構部２
は、鏡板に渦巻き状のラップを有する固定スクロール３
と旋回スクロール４を、ラップ同士が互いに噛み合うよ
うにすることで圧縮室５を形成する。さらに、圧縮機構
部２には、旋回スクロール４を旋回運動させるための自
転阻止（防止）部材であるオルダムリング１３と前記固
定スクロールと結合されたフレーム７を備えている。2. Description of the Related Art As hermetic compressors, various types of compressors, such as reciprocating, rotary and scroll type compressors, are known. Here, the description of the prior art will be described taking a scroll compressor as an example. FIG. 5 shows a vertical sectional view of the scroll compressor. The compression mechanism unit 2 and the electric motor unit 9 are housed in the closed container 1 by being connected via the crankshaft 6. Compression mechanism 2
Is a fixed scroll 3 having a spiral wrap on a head plate.
And the orbiting scroll 4 so that the wraps mesh with each other to form the compression chamber 5. Further, the compression mechanism unit 2 includes an Oldham ring 13 which is a rotation preventing (preventing) member for rotating the orbiting scroll 4 to orbit, and a frame 7 coupled to the fixed scroll.
【０００３】電動機部９は、前記フレーム７の軸受けを
介して回転自在に支持されるクランク軸６に連結されて
いる。The electric motor 9 is connected to a rotatable crankshaft 6 via a bearing of the frame 7.
【０００４】特開平５−１９５９６７号公報には、脆性
材料たとえばカーボン材やセラミック材などを円筒状に
加工し軸受け摺動部材７ａ、４ａとして、前記フレーム
の軸受け部および前記旋回スクロールの軸受け部に圧入
して主軸受けと旋回スクロール軸受けとすることが記載
されている。Japanese Unexamined Patent Publication No. 5-195957 discloses that a brittle material such as carbon or ceramic is machined into a cylindrical shape and used as bearing sliding members 7a and 4a on a bearing portion of the frame and a bearing portion of the orbiting scroll. It is described that the main bearing and the orbiting scroll bearing are press-fitted.
【０００５】クランク軸の軸受け接触部近傍にはスラス
ト面６ａがあり、クランク軸外径とスラスト面が公差す
る部分のクランク軸外径が、軸受け内径側に突き出るこ
とがないよう、スラスト面近傍のクランク軸外径に外径
を小さくした段差部分６ｂを設け、加工を容易にしてい
る。A thrust surface 6a is provided in the vicinity of the bearing contact portion of the crankshaft. A step portion 6b having a smaller outer diameter is provided on the outer diameter of the crankshaft to facilitate machining.
【０００６】また、脆性材料たとえばカーボン材やセラ
ミック材などを円筒状に加工した軸受け摺動部材７ａ、
４ａは、外径端部に圧入するための面取りを設け、内径
端部にはバリやエッジを除去するため面取りを設けてい
る。Further, a bearing sliding member 7a formed by processing a brittle material such as a carbon material or a ceramic material into a cylindrical shape,
4a is provided with a chamfer for press-fitting the outer diameter end, and a chamfer for removing burrs and edges at the inner diameter end.
【０００７】また、密閉形回転式圧縮機、密閉形往復式
圧縮機においても、圧縮機構部と電動機部とを介するク
ランク軸を回転自在に支持する軸受けについて、脆性材
料を円筒状に加工し圧入する軸受け部材とクランク軸外
径を小さくした段差部分は同じ構造としている。[0007] In the hermetic rotary compressor and hermetic reciprocating compressor as well, a brittle material is formed into a cylindrical shape by press-fitting a bearing rotatably supporting a crankshaft via a compression mechanism and an electric motor. The bearing member to be formed and the stepped portion having a reduced crankshaft outer diameter have the same structure.
【０００８】[0008]
【発明が解決しようとする課題】前記従来の構造では、
次に説明するような問題がある。◆圧縮機が高負荷運転
されるとクランク軸のたわみが大きくなる。それによ
り、図６に示すように前記クランク軸のスラスト面近傍
のクランク軸外径に外径を小さくした段差部Ａ点および
図７に示すクランク軸端部Ａ点が、軸受け摺動部材７
ａ、４ａの内径に線接触もしくは点接触して、油膜切れ
が発生し摩耗に至る場合がある。In the above conventional structure,
There is a problem as described below. ◆ When the compressor is operated under high load, the deflection of the crankshaft increases. As a result, as shown in FIG. 6, the point A where the outer diameter is reduced to the outer diameter of the crankshaft near the thrust surface of the crankshaft and the point A of the crankshaft end shown in FIG.
A line contact or a point contact with the inner diameters of a and 4a may result in oil film breakage and wear.
【０００９】この摩耗を防止するため、図８に示すよう
にクランク軸のスラスト面近傍のクランク軸外径を小さ
くした段差部Ａ点もしくは図９に示すクランク軸端部Ａ
点を軸受け摺動部材の内径端部Ｂ点より、軸方向で軸受
け摺動面の外側に位置させる（Ａ点を軸受摺動部材７
ａ、４ａに接触しないように軸受摺動部材より突出させ
る）ことにより、Ａ点が軸受摺動部材７ａ、４ａに接触
しなくなるので、クランク軸のたわみによる荷重に起因
した摩耗はこの点について云えば防止することができ
る。In order to prevent this abrasion, as shown in FIG. 8, a step A point where the outer diameter of the crankshaft is reduced near the thrust surface of the crankshaft or a crankshaft end A shown in FIG.
The point is located outside the bearing sliding surface in the axial direction from the point B of the inner diameter end of the bearing sliding member (point A is the bearing sliding member 7).
a, 4a), so that the point A does not contact the bearing sliding members 7a, 4a, so that the wear caused by the load due to the deflection of the crankshaft is not considered in this regard. For example, it can be prevented.
【００１０】しかし、今度はクランク軸のたわみによる
荷重が軸受け摺動部材内径端部Ｂ点に集中することにな
る。ところで、この場合、軸受け摺動部材外径端部を軸
受内に圧入するため面取りを大きく取っている。この結
果、軸受け摺動部材内径端部Ｂ点の位置は、軸受け摺動
部材外径端部Ｃ点の位置よりも軸方向で軸受け摺動面の
外側（旋回スクロール側）に位置する。それにより、軸
受け摺動部材内径端部Ｂ点にかかった荷重を支えるため
の荷重は、結果的に軸受け摺動部材外径端部Ｃ点に集中
して、軸受け摺動部材の外径内径両面取りにより断面積
が小さくなった部分に曲げモーメントが発生し、軸受け
摺動部材端部が割れに至る恐れがある。However, this time, the load due to the deflection of the crankshaft concentrates on the inner end B of the bearing sliding member. By the way, in this case, a large chamfer is taken to press-fit the outer diameter end of the bearing sliding member into the bearing. As a result, the position of the end point B of the inner diameter of the bearing sliding member is located outside the bearing sliding surface (on the orbiting scroll side) in the axial direction than the position of the point C of the outer diameter end of the bearing sliding member. As a result, the load for supporting the load applied to the point B of the bearing sliding member inner diameter end is concentrated on the point C of the bearing sliding member outer diameter end. A bending moment is generated in the portion where the cross-sectional area is reduced by the cutting, and the end of the bearing sliding member may be cracked.
【００１１】特に、従来から使用しているＨＣＦＣ系冷
媒Ｒ２２の代替としてＨＦＣ系２種混合冷媒であるＲ４
１０Ａ、もしくは３種混合冷媒であるＲ４０４Ａを用い
た際、Ｒ２２に比べ高圧力となるため高負荷になり、軸
受け摺動部材が摩耗、割れに至る恐れが強くなる。Particularly, as an alternative to the conventionally used HCFC-based refrigerant R22, R4, which is an HFC-based two-class mixed refrigerant, is used.
When 10A or R404A, which is a mixed refrigerant of three kinds, is used, the pressure is higher than that of R22, so that the load becomes higher and the bearing sliding member is more likely to be worn or cracked.
【００１２】本発明の目的は、圧縮機のクランク軸がた
わんでも、軸受か若しくはクランク軸の摩耗を低減する
構造を備えた圧縮機を提供することにある。It is an object of the present invention to provide a compressor having a structure for reducing wear of a bearing or a crankshaft even if the crankshaft of the compressor is bent.
【００１３】[0013]
【課題を解決するための手段】前記目的は、密閉容器に
収納され、クランク軸を介して接続された圧縮機構部と
圧縮機構部を駆動する電動機部とを備え、前記クランク
軸を、軸受け摺動部材を前記軸受けの内径部に挿入した
軸受けに摺動自在に支持した密閉形圧縮機において、前
記クランク軸に外径を小さくした段差部を設け、前記軸
受け摺動部材端部がこの段差部に当接しないようにこの
軸受け摺動部材内径端部を面取りし、この軸受け摺動部
材の前記端部より施された面取り部の角部が、前記軸受
け摺動部材内径端部の面取り角部よりもこの軸受け摺動
部端部側に位置するようにしたことにより達成される。The object of the present invention is to provide a compression mechanism housed in a closed container and connected via a crankshaft, and an electric motor section for driving the compression mechanism. In a hermetic compressor in which a moving member is slidably supported by a bearing inserted into an inner diameter portion of the bearing, a step portion having a smaller outer diameter is provided on the crankshaft, and the end of the bearing sliding member is formed by the step portion. The inner edge of the bearing sliding member is chamfered so as not to come into contact with the inner periphery of the bearing sliding member. The chamfered portion formed from the end of the bearing sliding member is a chamfered corner of the inner diameter end of the bearing sliding member. This is achieved by being located closer to the end of the bearing sliding part than the bearing sliding part.
【００１４】[0014]
【発明の実施の形態】密閉形圧縮機として、レシプロ、
ロータリ、スクロール等の様々なタイプの圧縮機がある
が、ここではスクロール圧縮機の構成を例に、以下本発
明の一実施例を図１、図２、図３、図４及び図５を用い
て説明する。BEST MODE FOR CARRYING OUT THE INVENTION As a hermetic compressor, a reciprocating compressor,
There are various types of compressors such as a rotary type and a scroll type. Here, an example of the present invention will be described with reference to FIGS. 1, 2, 3, 4 and 5 taking the configuration of a scroll type compressor as an example. Will be explained.
【００１５】図５に示したスクロール圧縮機は、密閉容
器１内に、圧縮機構部２と電動機部９とがクランク軸６
を介して連結して収納される。圧縮機構部２は、鏡板に
渦巻き状のラップを有する固定スクロール３と旋回スク
ロール４を、ラップ同士が互いに噛み合うようにするこ
とで圧縮室５を形成する。この圧縮機構部２は、クラン
ク軸６を介して駆動用の電動機９に連結されている。前
記旋回スクロール４の自転を阻止し旋回運動させるため
のオルダムリング１３と固定スクロール３と結合し且つ
密閉容器１と溶接により固定されるフレーム７を有す
る。フレーム７には、前記電動機部９と連結したクラン
ク軸６を摺動自在に支持する主軸受けを形成する。In the scroll compressor shown in FIG. 5, a compression mechanism 2 and an electric motor 9
It is connected and stored via The compression mechanism 2 forms a compression chamber 5 by making the fixed scroll 3 and the orbiting scroll 4 having a spiral wrap on the end plate engage with each other. The compression mechanism 2 is connected to a driving electric motor 9 via a crankshaft 6. An Oldham ring 13 for preventing the orbiting scroll 4 from rotating and making a revolving motion is combined with the fixed scroll 3 and has a frame 7 fixed to the closed casing 1 by welding. A main bearing for slidably supporting the crankshaft 6 connected to the motor unit 9 is formed on the frame 7.
【００１６】密閉容器１の外周部には吸入口１０を備
え、この吸入口１０からガス（冷媒）を吸入し、吸入さ
れたガスは、前記両スクロールにより形成される圧縮室
５を中心部に移動させつつ容積を減少させてガスを圧縮
させ、固定スクロール３の中央部の吐出ポート３ａより
吐出される。圧縮室５は常に複数個存在する。 また、
固定スクロール３には圧縮室５の圧力が過圧縮になった
際に圧力を逃がすリリース弁１１が設けられている。A suction port 10 is provided on an outer peripheral portion of the closed container 1, and a gas (refrigerant) is sucked from the suction port 10, and the sucked gas flows through a compression chamber 5 formed by the two scrolls. The gas is compressed by reducing the volume while moving, and is discharged from the discharge port 3a at the center of the fixed scroll 3. There are always a plurality of compression chambers 5. Also,
The fixed scroll 3 is provided with a release valve 11 for releasing the pressure when the pressure in the compression chamber 5 becomes excessively compressed.
【００１７】図３に示すように、脆性材料たとえばカー
ボン材やセラミック材などを円筒状に加工し軸受け部材
７ａ、４ａとして、前記フレーム７及び旋回スクロール
４の軸受け部に圧入して軸受けを形成する。クランク軸
６のスラスト面近傍には他の部分より外径を小さくした
段差部分６ｂが設けられ、スラスト面との交差部のクラ
ンク軸外径の加工を容易にしている。図３において、ク
ランク軸６は、電動機の回転子に挿入される部分（シャ
フトという）、フレーム７とスラスト面を形成する円盤
部（円周部にバランサを取り付ける）及び軸心が偏心し
たクランク部から構成されこれら３つの部材は１つの材
料から削りだしにより加工形成される。シャフトを削り
出す際、円盤側に向かって加工していくが、円盤部とシ
ャフトの接続部（スラスト面との交差部）は大きな工具
で加工すると直角に加工することができず、両者の接続
部は曲面が形成されてしまう。この曲面が存在するとシ
ャフト径よりも大きな径となる場合、この曲面と軸受と
が接触してしまい摩耗の原因となる。そこで、この曲面
を削る必要があるが、ここでは加工精度を高くする（シ
ャフトと円盤部と接続部における角度を厳密に直角とす
る必要はない（シャフトと円盤とは直角となるように加
工しなければならない））必要はないため、本実施例で
は、小さな工具を用いて曲面部をシャフトの外周面より
も少し多く削ることを許容することにより、加工を容易
にしている。As shown in FIG. 3, a brittle material such as a carbon material or a ceramic material is machined into a cylindrical shape, and pressed into the bearing portions of the frame 7 and the orbiting scroll 4 as bearing members 7a and 4a to form a bearing. . In the vicinity of the thrust surface of the crankshaft 6, a step portion 6b having an outer diameter smaller than that of the other portions is provided to facilitate machining of the outer diameter of the crankshaft at the intersection with the thrust surface. In FIG. 3, a crankshaft 6 includes a portion (referred to as a shaft) inserted into a rotor of an electric motor, a disk portion (a balancer is attached to a circumferential portion) forming a thrust surface with a frame 7, and a crank portion having an eccentric shaft center. These three members are formed by machining from one material. When machining the shaft, it is machined toward the disk, but the connection between the disk and the shaft (the intersection with the thrust surface) cannot be machined at a right angle if it is machined with a large tool. The portion has a curved surface. If the curved surface has a diameter larger than the diameter of the shaft, the curved surface comes into contact with the bearing, causing wear. Therefore, it is necessary to cut this curved surface, but in this case, it is necessary to increase the processing accuracy (the angle between the shaft, the disk portion, and the connection portion does not need to be strictly a right angle (the processing is performed so that the shaft and the disk become a right angle). In the present embodiment, machining is facilitated by allowing the curved surface to be cut slightly more than the outer peripheral surface of the shaft using a small tool.
【００１８】また、図１及び図２に示すように脆性材料
たとえばカーボン材やセラミック材などを円筒状に加工
した軸受け部材７ａ、４ａの、外径端部には軸受け部材
７ａ、４ａをフレーム７に圧入するための面取りを設け
ている。図１及び図２において、軸受け部材の内径端部
Ｂを外径端部Ｃより軸方向で軸受け摺動面の内側（深
部）に位置させる。換言すると、フレーム７側（図１）
では、軸受け部材７ａの外径端部Ｃを内径端部Ｂよりも
スラスト面側（旋回スクロール側）に位置させ、旋回ス
クロール４側軸受け（図２）では、軸受け部材４ａの外
径端部Ｃを内径端部Ｂよりも旋回スクロール側に位置さ
せる。そのために、図１に示すように軸受け摺動部材内
径端部を段付きとするか、もしくは図４に示すように内
径面取りを外径面取りより大きくする。As shown in FIGS. 1 and 2, the bearing members 7a, 4a formed by processing a brittle material, such as carbon or ceramic, into a cylindrical shape. A chamfer for press-fitting is provided. 1 and 2, the inner diameter end B of the bearing member is positioned on the inner side (deep part) of the bearing sliding surface in the axial direction from the outer diameter end C. In other words, the frame 7 side (FIG. 1)
Then, the outer diameter end C of the bearing member 7a is positioned closer to the thrust surface (the orbiting scroll side) than the inner diameter end B. In the orbiting scroll 4 side bearing (FIG. 2), the outer diameter end C of the bearing member 4a is set. Is located closer to the orbiting scroll than the inner diameter end B. For this purpose, the inner end of the bearing sliding member is stepped as shown in FIG. 1 or the inner chamfer is made larger than the outer chamfer as shown in FIG.
【００１９】また、クランク軸たわみによる荷重がクラ
ンク軸段差角部Ａから軸受け摺動部材内径にかからない
ように、図１に示すクランク軸外径段差部Ａ点もしくは
図２に示すクランク軸端部Ａ点が、軸受け摺動部材の内
径端部Ｂ点より、軸方向で軸受け摺動面の外側（軸受け
摺動面にかからない）に位置させる。Also, to prevent the load due to the deflection of the crankshaft from being applied to the inner diameter of the bearing sliding member from the crankshaft stepped corner A, the crankshaft outer diameter stepped point A shown in FIG. 1 or the crankshaft end A shown in FIG. The point is positioned outside the bearing sliding surface in the axial direction (not on the bearing sliding surface) from the inner end B of the bearing sliding member.
【００２０】前記課題の中で述べたように従来の構造で
は、高負荷の場合もしくは従来から使用しているＨＣＦ
Ｃ系冷媒Ｒ２２に比べ高圧力となるＨＦＣ系２種混合冷
媒であるＲ４１０Ａ、もしくは３種混合冷媒であるＲ４
０４Ａを用いた際、クランク軸のたわみにより軸受けが
摩耗や割れなどに至る恐れがあったが、上記構造とする
ことにより、クランク軸と軸受け部材内径が線接触もし
くは点接触となることなく、軸受け部材内径の摩耗を防
止でき、かつ、軸受け部材端部の外径内径両面取りによ
り断面積が小さくなった部分に曲げモーメントが集中す
ることなく、軸受け部材端部の割れを防止できる。それ
により高負荷時においても軸受けの摩耗、割れ等が発生
することなく、信頼性の高いスクロール圧縮機とするこ
とができる。As described in the above-mentioned problem, in the conventional structure, in the case of a high load or a conventionally used HCF,
R410A, which is a HFC-based two-type mixed refrigerant having a higher pressure than the C-based refrigerant R22, or R4, a three-type mixed refrigerant
When the 04A was used, there was a possibility that the bearing would be worn or cracked due to the deflection of the crankshaft. Abrasion of the inner diameter of the member can be prevented, and a bending moment does not concentrate on a portion having a reduced cross-sectional area due to both sides of the outer diameter of the inner end of the bearing member. As a result, a highly reliable scroll compressor can be provided without abrasion, cracking, and the like of the bearing even under a high load.
【００２１】図を用いて説明する。図１及び図６におい
て、図６に示した従来構造では、クランク軸６がたわん
だ場合、軸受け部材よりも固いクランク軸の段差の始ま
り部である軸段差角部Ａが、軸受け部材７ａの内壁に接
触してこの軸受け部材７ａを摩耗に至らしめてしまう。
これに対して、図１に示した本実施例では、この軸段差
角部Ａは、軸受け部材７ａの内壁面に径方向で対向して
いないので、接触することはない。このため、摩耗等を
防止することができる。This will be described with reference to the drawings. 1 and 6, in the conventional structure shown in FIG. 6, when the crankshaft 6 bends, the shaft step angle portion A which is the beginning of the step of the crankshaft which is harder than the bearing member is formed on the inner wall of the bearing member 7a. And causes the bearing member 7a to wear.
On the other hand, in the present embodiment shown in FIG. 1, the shaft step angle portion A does not come into contact with the inner wall surface of the bearing member 7a because it does not face the inner wall surface in the radial direction. Therefore, abrasion and the like can be prevented.
【００２２】また、図１及び図８を対比すると、図８に
示した従来構造では、クランク軸６がたわんだ結果、摺
動部材内径端部Ｂに荷重が集中し、この荷重を摺動部材
外径端部Ｃにて受けることとなり、この部分に応力が集
中し軸受け摺動部材を破損に至らしめてしまう。これに
対して、図１に示す本実施例においては、摺動部内径端
部Ｂの位置を、摺動部外径端部Ｃの位置よりも、軸方向
摺動面方向に深く面取りを施したので、クランク軸６が
たわんで摺動部内径端部Ｂに荷重がかかっても、摺動部
外径端部Ｃに応力が集中することはない。In comparison with FIGS. 1 and 8, in the conventional structure shown in FIG. 8, as a result of the crankshaft 6 being bent, a load is concentrated on the inner end B of the sliding member, and this load is transferred to the sliding member. Since the bearing slide member is received at the outer diameter end portion C, stress concentrates on this portion and the bearing sliding member is damaged. On the other hand, in the present embodiment shown in FIG. 1, the position of the inner end B of the sliding portion is chamfered deeper in the axial sliding surface direction than the position of the outer end C of the sliding portion. Therefore, even when the crankshaft 6 is bent and a load is applied to the inner end B of the sliding portion, stress does not concentrate on the outer end C of the sliding portion.
【００２３】ちなみに、摺動部内径端部Ｂは、角度があ
るためこの角にてクランク軸６の外周を傷つけることが
懸念されるが、クランク軸６は軸受け摺動部材７ａに比
べ固い材料で形成しているのでクランク軸６が摩耗する
恐れは少ない。一方、摺動部内径端部Ｂの摩耗である
が、この部分が接触する部材は、クランク軸６の外周部
であり、点接触はしなく、例え、片当たりしても摺動部
内径端部Ｂの頂部の角が取れる方向に摩耗するので、何
ら問題がない。Incidentally, since the inner end B of the sliding portion has an angle, the outer periphery of the crankshaft 6 may be damaged at this angle, but the crankshaft 6 is made of a harder material than the bearing sliding member 7a. Since it is formed, there is little possibility that the crankshaft 6 will be worn. On the other hand, although the wear of the inner end portion B of the sliding portion is caused to come in contact with the outer peripheral portion of the crankshaft 6, there is no point contact. Since there is abrasion in the direction in which the corner of the top of the part B can be removed, there is no problem.
【００２４】[0024]
【発明の効果】以上詳細説明したように、本発明によれ
ば、高負荷で運転された場合においても、信頼性の高い
密閉形スクロール圧縮機を提供することができる。As described above in detail, according to the present invention, it is possible to provide a hermetic scroll compressor having high reliability even when operated under a high load.
【図１】本発明の密閉形圧縮機の軸受け構造断面図であ
る。FIG. 1 is a sectional view of a bearing structure of a hermetic compressor of the present invention.
【図２】本発明の密閉形圧縮機の軸受け構造断面図であ
るFIG. 2 is a sectional view of a bearing structure of the hermetic compressor of the present invention.
【図３】本発明の実施例のスクロール圧縮機の圧縮機構
部断面図であるFIG. 3 is a sectional view of a compression mechanism of the scroll compressor according to the embodiment of the present invention.
【図４】本発明の密閉形圧縮機の軸受け構造断面図であ
るFIG. 4 is a sectional view of a bearing structure of the hermetic compressor of the present invention.
【図５】スクロール圧縮機の縦断面図であるFIG. 5 is a vertical sectional view of a scroll compressor.
【図６】従来の密閉形圧縮機の軸受け構造断面図であ
る。FIG. 6 is a sectional view of a bearing structure of a conventional hermetic compressor.
【図７】従来の密閉形圧縮機の軸受け構造断面図であ
る。FIG. 7 is a sectional view of a bearing structure of a conventional hermetic compressor.
【図８】従来の密閉形圧縮機の軸受け構造断面図であ
る。FIG. 8 is a sectional view of a bearing structure of a conventional hermetic compressor.
【図９】従来の密閉形圧縮機の軸受け構造断面図であ
る。FIG. 9 is a sectional view of a bearing structure of a conventional hermetic compressor.
１…密閉容器、２…圧縮機構部、３…固定スクロール、
４…旋回スクロール、５…圧縮室、６…クランク軸、７
…フレーム、９…電動機部、１０…吸入口、１１…リリ
ース弁、１３…オルダムリング。DESCRIPTION OF SYMBOLS 1 ... Closed container, 2 ... Compression mechanism part, 3 ... Fixed scroll,
4: orbiting scroll, 5: compression chamber, 6: crankshaft, 7
... Frame, 9 ... Motor part, 10 ... Suction port, 11 ... Release valve, 13 ... Oldham ring.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 田村 和己 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冷熱事業部内 (72)発明者 金子 正人 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冷熱事業部内 (72)発明者 田所 哲也 栃木県下都賀郡大平町富田709番地の２ 株式会社日立栃木エレクトロニクス内 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazumi Tamura 800, Tomita, Odai-cho, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Inside the Hitachi, Ltd.Cooling Division (72) Tetsuya Tadokoro, Hitachi, Ltd.
Claims (2)
接続された圧縮機構部と圧縮機構部を駆動する電動機部
とを備え、前記クランク軸を、軸受け摺動部材を前記軸
受けの内径部に挿入した軸受けに摺動自在に支持した密
閉形圧縮機において、前記クランク軸に外径を小さくし
た段差部を設け、前記軸受け摺動部材端部がこの段差部
に当接しないようにこの軸受け摺動部材内径端部を面取
りし、この軸受け摺動部材の前記端部より施された面取
り部の角部が、前記軸受け摺動部材内径端部の面取り角
部よりもこの軸受け摺動部端部側に位置するようにした
密閉型圧縮機。1. A compression mechanism housed in an airtight container and connected via a crankshaft, and an electric motor section for driving the compression mechanism section, wherein the crankshaft is connected to a bearing sliding member by an inner diameter portion of the bearing. In the hermetic compressor, which is slidably supported by a bearing inserted into the bearing, a stepped portion having a reduced outer diameter is provided on the crankshaft, and the bearing is arranged such that the end of the bearing sliding member does not contact the stepped portion. The inner end of the sliding member is chamfered, and the corner of the chamfer formed from the end of the bearing sliding member is larger than the chamfered corner of the inner diameter of the bearing sliding member. Hermetic compressor located on the side of the unit.
は冷媒であり、この冷媒をＨＦＣ系２種混合冷媒、もし
くは３種混合冷媒とした密閉形圧縮機。2. The hermetic compressor according to claim 1, wherein the working fluid of the compressor is a refrigerant, and the refrigerant is a mixed refrigerant of two or three types of HFC.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05176398A JP4051121B2 (en) | 1998-03-04 | 1998-03-04 | Hermetic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05176398A JP4051121B2 (en) | 1998-03-04 | 1998-03-04 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11247761A true JPH11247761A (en) | 1999-09-14 |
| JP4051121B2 JP4051121B2 (en) | 2008-02-20 |
Family
ID=12896002
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05176398A Expired - Lifetime JP4051121B2 (en) | 1998-03-04 | 1998-03-04 | Hermetic compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4051121B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002057631A3 (en) * | 2001-01-22 | 2002-12-12 | Hnp Mikrosysteme Gmbh | Miniature precision bearings and method for assembling the same |
| JP2003003970A (en) * | 2001-06-20 | 2003-01-08 | Fujitsu General Ltd | Scroll compressor |
| WO2004029461A1 (en) * | 2002-09-24 | 2004-04-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US7419821B2 (en) | 2002-03-05 | 2008-09-02 | I-Stat Corporation | Apparatus and methods for analyte measurement and immunoassay |
| JP2020037943A (en) * | 2016-11-18 | 2020-03-12 | パナソニックＩｐマネジメント株式会社 | Refrigerant compressor and refrigeration device with the same |
| CN111788394A (en) * | 2018-03-05 | 2020-10-16 | 三菱电机株式会社 | Compressor with a compressor housing having a plurality of compressor blades |
| 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 |
-
1998
- 1998-03-04 JP JP05176398A patent/JP4051121B2/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7698818B2 (en) | 2001-01-22 | 2010-04-20 | Hnp Mikrosysteme Gmbh | Method for assembling precision miniature bearings for minisystems and microsystems |
| WO2002057631A3 (en) * | 2001-01-22 | 2002-12-12 | Hnp Mikrosysteme Gmbh | Miniature precision bearings and method for assembling the same |
| JP2003003970A (en) * | 2001-06-20 | 2003-01-08 | Fujitsu General Ltd | Scroll compressor |
| US8222024B2 (en) | 2002-03-05 | 2012-07-17 | Abbott Point Of Care Inc. | Apparatus and methods for analyte measurement and immunoassay |
| US7419821B2 (en) | 2002-03-05 | 2008-09-02 | I-Stat Corporation | Apparatus and methods for analyte measurement and immunoassay |
| US8017382B2 (en) | 2002-03-05 | 2011-09-13 | Abbott Point Of Care Inc. | Apparatus and methods for analyte measurement and immunoassay |
| US8642322B2 (en) | 2002-03-05 | 2014-02-04 | Abbott Point Of Care Inc. | Apparatus and methods for analyte measurement immunoassay |
| US8679827B2 (en) | 2002-03-05 | 2014-03-25 | Abbott Point Of Care Inc. | Apparatus and methods for analyte measurement and immunoassay |
| WO2004029461A1 (en) * | 2002-09-24 | 2004-04-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JP2020037943A (en) * | 2016-11-18 | 2020-03-12 | パナソニックＩｐマネジメント株式会社 | Refrigerant compressor and refrigeration device with the same |
| US11143442B2 (en) | 2016-11-18 | 2021-10-12 | Panasonic Intellectual Property Management Co., Ltd. | Refrigerant compressor and freezer including same |
| US11959670B2 (en) | 2016-11-18 | 2024-04-16 | Panasonic Intellectual Property Management Co., Ltd. | Refrigerant compressor and freezer including same |
| CN111788394A (en) * | 2018-03-05 | 2020-10-16 | 三菱电机株式会社 | Compressor with a compressor housing having a plurality of compressor blades |
| 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 |
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| Publication number | Publication date |
|---|---|
| JP4051121B2 (en) | 2008-02-20 |
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