JP2004270495A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To equalize the imbalance caused by whirling motion of lubricating oil 96 existing in a space 97 surrounded by a frame 6 of a scroll compressor, a whirling scroll 2 and a boss 23 (a space behind the whirling scroll). <P>SOLUTION: The unstable imbalance due to the whirling motion of the lubricating oil 96 existing in the space 97 surrounded by the frame 6, the whirling scroll 2 and the boss 23 is balanced more than ever by preventing the lubricating oil from building up in the space behind the whirling scroll, so that the vibration of the scroll compressor is reduced. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【００１１】
で表され、さらに軸にかかる遠心力の釣り合い、つまり、静的な釣り合いは、
【００１２】
【数２】

【００１３】
で表される。ここで、可動部材の不釣合い量ｍ１、重心の回転半径ｒ１及びスラスト面９８からの軸方向距離Ｌ１は既知であるので、例えば、上側バランスウエイト９０重心の回転半径ｒ２、下側バランスウエイト９１重心の回転半径ｒ３及び、それらの重心のスラスト面９８からの軸方向距離Ｌ２，Ｌ３を適当に設定してやれば、２つの式を連立させて解くことにより、ｍ２，ｍ３を求めることができる。この様にして算出したバランスウエイトの位置、質量としてやることによりアンバランスは最小となり、圧縮機の振動を防止することができる。
【００１４】
【特許文献１】
特開昭５７−１４８０９１号公報（第１−５頁、第１図）
【００１５】
【発明が解決しようとする課題】
しかしながら、前記従来の構成では、旋回スクロール２の背面に形成された背面空間９７に存在する潤滑油の質量によるアンバランスが考慮されておらず、圧縮機の振動を充分に低減することは困難であった。すなわち、背面空間９７は旋回スクロールの固定スクロールに対する偏心方向とは逆方向に偏心して配置されているので、そこに存在する潤滑油は回転アンバランスを生じることになり、その結果潤滑油の質量を考慮に入れた従来のスクロール圧縮機のバランス釣り合いは図８に示されるようなものになる。
【００１６】
また、背面空間９７に流れ込む潤滑油の量は、回転シャフト５で駆動されるオイルポンプ９５で汲み上げられている為、回転軸５の回転数により変化する。すなわち、潤滑油の質量による回転アンバランスは、潤滑油の質量自体が運転中に変化するので、予めバランスウエイトを設けて相殺することが困難であり、特に回転数が広範囲に変化するインバーター制御圧縮機において、アンバランスによる振動を充分に低減させることが出来ないという課題を有していた。
【００１７】
本発明は、潤滑油による不安定なアンバランスを無くす為に、バランスウエイトを背面空間内に設け、潤滑油が背面空間に溜まらないようにし、不規則なアンバランスの発生を防止して、振動が少ないスクロール圧縮機を提供することを目的とする。
【００１８】
【課題を解決するための手段】
前記従来の課題を解決するために本発明のスクロール圧縮機は、旋回スクロールの背面空間内をほぼ満たす大きさのバランスウェイトを設けることにより、潤滑油が背面空間内に出入りすることによる不安定なアンバランスの発生を防止するものである。そして、背面空間内にアンバランスウェイトを設けた分、ロータ端面に設けるアンバランスウェイト質量を小さくしたものである。
【００１９】
本構成によって、背面空間に出入りする潤滑油を最小限に抑えて不安定な遠心力を発生させる要因を排除することができ、その結果、圧縮機の振動を低減させることができる。
【００２０】
【発明の実施の形態】
以下本発明の実施の形態について、図面を参照しながら説明する。
【００２１】
（実施の形態１）
図１は、本発明の実施の形態１におけるスクロール圧縮機の縦断面図、図２は同じく実施の形態１におけるドライブブッシュの斜視図、図３は実施の形態１における旋回スクロールとバランスウェイトのバランス図を示す。図において図６乃至図９と同じ構成要素については同じ符号を用い、説明を省略する。
【００２２】
図１において密閉ハウジング８はその内部に、ステータＭｂとロータＭａから成る電動モータＭと、電動モータＭによって駆動される圧縮機構部Ｃと、電動モータＭからの回転駆動力を圧縮機構部Ｃに伝達するための回転シャフト５とを収納している。圧縮機構部Ｃはフレーム６と、固定スクロール羽根を有する固定スクロール１と、この固定スクロール羽根と噛み合わせて複数個の圧縮作業空間を形成するように旋回スクロール羽根を旋回スクロール鏡板２１（端板）上に配設した旋回スクロール２と、旋回スクロール２の自転を防止するためのオルダムリング３とで構成されている。旋回スクロール２を含む可動部材の旋回運動によるアンバランスを相殺するためにロータＭａ上側にバランスウエイト９０を設置し、ロータＭａ下側にもバランスウエイト９１を設置している。また、密閉ハウジング８内の底面には、潤滑油９６が貯溜されている。潤滑油９６はオイルポンプ９５で汲み上げられ、回転シャフト５内に設置されているオイル通路９４を通り、フレーム６と旋回スクロール２とボス２３との間の旋回スクロール背面空間９７に吐き出される。この旋回スクロール背面空間９７には、該背面空間９７をほぼ満たすバランスウエイト９２を設けることにより、背面空間９７内に潤滑油９６が溜まることはなくなる、しかも、バランスウエイトなので、体積、質量は一定である。これにより、旋回スピードの変化による、旋回スクロール周辺の遠心力は一定になる。
【００２３】
ここで、図４，図５を参照してさらに詳細に説明する。図４は旋回スクロール背面空間９７内の様子を模式的に表したもので、旋回スクロール背面空間９７に設けたバランスウエイト９２によって生じる遠心力Ｆｏが、旋回スクロール２の遠心力Ｆｐと回転シャフト５中心Ｏに対して反対に作用するので、ＦｐとＦｏを合成した遠心力Ｆｐ’はＦｐよりも小さくなる。
【００２４】
したがって、釣り合いを示す図５における可動部材の不釣り合い量ｍ１’と可動部材の回転半径ｒ１’の積ｍ１’・ｒ１’は、図９の可動部材の不釣り合い量ｍ１と可動部材の回転半径ｒの積ｍ１・ｒ１よりも小さくなる。
【００２５】
このアンバランスの分、前記可動部材のアンバランス量がかわるので、バランスウエイトを設定し直す必要がある。
【００２６】
図５に示す動的な釣り合いの式は、ロータＭａ上側のバランスウエイト９０の質量をｍ２’、ロータＭａ下側のバランスウエイト９１の質量をｍ３’、 さらに、可動部材不釣り合い量重心のスラスト面９８からの軸方向の距離をＬ１、ロータＭａ上端のバランスウエイト９０重心のスラスト面９８からの軸方向の距離をＬ２、ロータＭａ下側のバランスウエイト９１重心のスラスト面９８からの軸方向の距離をＬ３とすると、
【００２７】
【数３】

【００２８】
で表される。
【００２９】
さらに、静的な釣り合いは、
【００３０】
【数４】

【００３１】
で表される。ここで、数１乃至数４よりｍ２’およびｍ３’はそれぞれ、
【００３２】
【数５】

【００３３】
【数６】

【００３４】
となる。したがって、ロータ上側のバランスウエイトを、
【００３５】
【数７】

【００３６】
ロータ下側のバランスウエイトを、
【００３７】
【数８】

【００３８】
だけ小さく設定し直す。これにより従来の潤滑油による不安定なアンバランスを想定したものよりも圧縮機本体のバランスがよくなり、圧縮機の振動を低減することができる。
【００３９】
また、旋回スクロール背面空間９７に設けたバランスウエイト９２の遠心力Ｆｏは次のように計算される。図４において仮に旋回スクロール背面空間９７が斜線部であり、ここに比質量ρｏのバランスウエイトが設けられているとする。旋回スクロール背面空間９７の部屋の直径をＤ、旋回スクロール２のボスの直径をｄとし、背面空間９７の高さは旋回スクロール２のボス高さとほぼ同じｈとし、このｈ分の高さの斜線部のバランスウエイトがドライブブッシュ５４の旋回運動とともに回転するとする。Ｏを中心とする回転バランスを考えると、斜線部の重心の位置Ｏｏ、およびアンバランス質量ｍｏは、旋回スクロール背面空間９７にバランスウエイト９２で満たし、その反対側に旋回スクロール２のボスと同じ大きさでバランスウエイト９２と同じ比質量ρｏの円板を置いたのと同じことになるので、
【００４０】
【数９】

【００４１】
【数１０】

【００４２】
となる。
【００４３】
したがって、回転角速度をωとすると、
【００４４】
【数１１】

【００４５】
となる。
【００４６】
一方ボス２３の遠心力Ｆｐはその重心位置がｒ１で、アンバランス量ｍｐは、旋回スクロール２のボスの比質量をρ１とすれば、
【００４７】
【数１２】

【００４８】
となる。
【００４９】
したがって、
【００５０】
【数１３】

【００５１】
となり、旋回スクロール２のボスと回転するバランスウエイト９２の回転アンバランスＦｏを考慮するということは、
【００５２】
【数１４】

【００５３】
となり、旋回スクロール２のボスの比質量を（ρ１−ρｏ）で計算し、バランスウエイトを設定すればバランスウエイト９２の回転のアンバランスを考慮したバランスウエイトの設定が可能となる。
【００５４】
以上、密閉型の電動圧縮機で説明したが、本発明は開放型のスクロール圧縮機にも適用できる。
【００５５】
【発明の効果】
前記実施例から明らかなように、請求項１に記載の発明は、吸入口と吐出口を有するハウジングと、端板上に形成された渦巻体を有し、前記ハウジング内に設けられた固定スクロールと、端板上に形成された渦巻体を有し、前記固定スクロールと中心をずらして噛み合うように組み込まれた可動スクロールと、前記ハウジングに回転自在に支持された回転シャフトと、前記回転シャフト端部に偏心して配置され、前記可動スクロールに公転運動を与えるドライブブッシュと、前記可動スクロールの公転のみを許容し、自転を阻止するオルダムリングとを有し、前記可動スクロールの公転運動によって、前記可動スクロールと前記固定スクロール間の密閉空間が容積を減少しながら渦巻体の中心方向へ移動し、前記密閉空間内の流体の圧縮が行われるスクロール型圧縮機において、前記フレームと前記旋回スクロールとボスとの間の空間（旋回スクロール背面空間）をほぼ満たすバランスウエイトを設ける圧縮機は、旋回スクロール背面空間９７をほぼ満たすバランスウエイト９２を設けるもので、この構成によれば上記潤滑油９６による不安定なアンバランスが無くなるので、圧縮機本体のバランスがよくなり、圧縮機本体の振動を低減することができる。
【００５６】
記請求項２又は前記請求項３のバランスウエイトを安価な焼結材料で構成することにより、コストを低減できる。
【００５７】
また、請求項５に記載に発明は、前記請求項２又は前記請求項３のバランスウエイトを旋回スクロールの比重より大きい材料で構成することにより、ローターに設けるバランスウエイトの大きさを小さくできる。
【図面の簡単な説明】
【図１】本発明のスクロール圧縮機の縦断面図
【図２】本発明のドライブブッシュの斜視図
【図３】本発明のバランス図
【図４】旋回スクロール背面空間の模式図
【図５】本発明の実施例を示す回転シャフトのバランス図
【図６】従来のスクロール圧縮機の縦断面図
【図７】潤滑油の質量を考慮しない従来例のスクロール圧縮機のバランス図
【図８】潤滑油の質量を考慮した従来のスクロール圧縮機のバランス図
【図９】従来の回転シャフトのバランス図
【符号の説明】
１ 固定スクロール
２ 旋回スクロール
３ オルダムリング
５ 回転シャフト
６ フレーム
８ 密閉ハウジング
１１ 固定スクロール鏡板
１２ 固定スクロールの渦巻状ラップ
１３ 吐出ポート
１４ 吐出キャビティ
１５ 吸入通路
１７ 逆止弁
２１ 旋回スクロール鏡板
２２ 旋回スクロールの渦巻状ラップ
２３ ボス
２４ 密閉空間
５４ ドライブブッシュ
５５ スライド孔
５９ 偏心ピン
７１ 上部軸受
７２ 下部軸受
７３ 旋回軸受
８２ 吸入管
８３ 吐出管
９０ バランスウエイト
９１ バランスウエイト
９２ バランスウエイト
９３ オイル排出溝
９４ オイル通路
９５ オイルポンプ
９６ 潤滑油
９８ スラスト面
９７ 旋回スクロール背面空間
Ｃ 圧縮機構
Ｍ 電動モータ
Ｍａ ロータ
Ｍｂ ステータ[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a scroll compressor, and particularly to a balance weight thereof.
[0002]
[Prior art]
As a conventional scroll compressor, a path used for storing the lubricating oil flowing into the back space of the orbiting scroll in the back space and used for lubrication between the back of the orbiting scroll and the frame and a path for discharging the lubricating oil to the bottom of the housing are provided. (See, for example, Patent Document 1). FIG. 6 is a sectional view of a main part of a conventional scroll compressor described in Patent Document 1. As shown in FIG.
[0003]
In FIG. 6, a closed housing 8 houses therein a scroll compression mechanism C connected to an electric motor M by a rotating shaft 5.
[0004]
The scroll compression mechanism C includes the fixed scroll 1, the orbiting scroll 2, the Oldham ring 3, the frame 6, the upper bearing 71, the orbiting bearing 73, the drive bush 54, etc. The orbiting scroll 2 is sandwiched between the fixed scroll 1 and the frame 6. While being held by the Oldham ring 3 disposed between the frame 6 and the frame 6, the Older ring 3 is held so as to be able to make a revolving motion whose rotation is restricted.
[0005]
The fixed scroll 1 is provided with a spiral wrap 12 on one end surface of a head plate 11 provided with a discharge port 13 in the center. The orbiting scroll 2 is provided with a spiral wrap 22 on one end surface of a head plate 21, and a hollow cylindrical boss 23 is provided on the other end surface of the head plate 21. A drive bush 54 is rotatably fitted to the inner periphery of the boss 23 via a swing bearing 73. An eccentric pin 59 projecting from the upper end of the rotary shaft 5 is fitted in a slide hole 55 formed in the drive bush 54. A part of the side surface of the eccentric pin 59 is cut in parallel with a straight line connecting the rotation center of the rotary shaft 5 and the drive center of the orbiting scroll 2, and a part of the inner surface of the slide hole 55 also has the cut portion. Are formed in a straight line so as to be in sliding contact. The drive bush 54 slides along the linear side surface of the eccentric pin 59 by sliding on the linear inner surface of the slide hole 55. The orbiting scroll 2 slides following the sliding movement of the drive bush 54. A plurality of closed spaces 24 are formed by displacing the fixed scroll 1 and the orbiting scroll 2 with each other by a predetermined distance, that is, an orbiting radius r, and engaging them at an angle shifted by 180 degrees.
[0006]
By driving the electric motor, the orbiting scroll 2 is driven via a revolving orbiting mechanism composed of the rotating shaft 5, the eccentric pin 59, the drive bush 54, the boss 23, and the like, and the orbiting scroll 2 is prevented from rotating by the Oldham ring 3. A revolving orbiting motion is performed on a circular orbit having a turning radius r. As a result, the gas is sucked into the closed space 24 via the suction passage 15, and as the volume of the closed space 24 decreases due to the revolving orbiting motion of the orbiting scroll 2, the gas reaches the central portion while being compressed, and reaches the discharge port 13. The check valve 17 is further pushed open to enter the discharge cavity 14, from which it is discharged to the outside via the discharge pipe 83.
[0007]
Further, by the rotation of the rotary shaft 5, the lubricating oil 96 stored in the bottom of the sealed housing 8 is pumped up by the pump 95 and supplied to the scroll compression mechanism C via the oil supply passage 94 provided in the rotary shaft 5. The lubricating oil 96 supplied to the scroll compression mechanism C passes through the gaps between the eccentric pin 59, the drive bush 54, and the eccentric bearing 73 housed inside the boss 23, and lubricates the respective sliding portions, while lubricating the respective sliding portions. The water is discharged into the space 97, a part of which is supplied to a thrust sliding surface between the orbiting scroll 2 and the frame 6, and the other part is discharged through the oil discharge passage 93 to the bottom of the sealed container.
[0008]
On the other hand, in the scroll compressor, since there is a movable member that performs an eccentric motion such as an orbiting scroll, a balance weight is added to the rotary shaft 5 or the rotor Ma so as to cancel the imbalance due to the motion of the movable member. There is a need to.
[0009]
FIG. 9 is a diagram showing a balance balance in a conventional scroll compressor in which lubricating oil and the like are not taken into account. 6 and 9, balance weights 90 and 91 are provided at both ends of the rotor Ma so as to cancel the unbalance amount of the movable member including the orbiting scroll member 2. Here, the unbalance amount of the movable member is m1, the mass of the balance weight 90 on the upper side of the rotor M is m2, the mass of the lower balance weight 91 is m3, the rotation radius of the center of gravity of the movable member is r1, and the center of gravity of the balance weight 90 is , The rotation radius of the center of gravity of the balance weight 91 is r3, the axial distance from the thrust surface 98 to the center of gravity of the movable member is L1, the axial distance from the balance weight 90 to the center of gravity is L2, and the balance weight 91 is Assuming that the axial distance to the center of gravity is L3, the moment balance in the direction perpendicular to the axis, that is, the dynamic balance is:
[0010]
(Equation 1)

[0011]
The balance of the centrifugal force acting on the shaft, that is, the static balance,
[0012]
(Equation 2)

[0013]
Is represented by Here, since the unbalance amount m1 of the movable member, the rotation radius r1 of the center of gravity, and the axial distance L1 from the thrust surface 98 are known, for example, the rotation radius r2 of the center of gravity of the upper balance weight 90, the center of gravity of the lower balance weight 91, and the like. By appropriately setting the rotational radius r3 and the axial distances L2 and L3 of their centers of gravity from the thrust surface 98, m2 and m3 can be obtained by solving the two equations simultaneously. By calculating the position and mass of the balance weight calculated in this way, the unbalance is minimized, and vibration of the compressor can be prevented.
[0014]
[Patent Document 1]
JP-A-57-148091 (pages 1-5, FIG. 1)
[0015]
[Problems to be solved by the invention]
However, in the above-described conventional configuration, the imbalance due to the mass of the lubricating oil existing in the back space 97 formed on the back of the orbiting scroll 2 is not considered, and it is difficult to sufficiently reduce the vibration of the compressor. there were. That is, since the back space 97 is eccentrically arranged in the direction opposite to the eccentric direction of the orbiting scroll with respect to the fixed scroll, the lubricating oil present there causes rotational imbalance, and as a result, the mass of the lubricating oil is reduced. The balance balance of the conventional scroll compressor taken into account is as shown in FIG.
[0016]
Further, the amount of the lubricating oil flowing into the back space 97 is changed by the rotation speed of the rotating shaft 5 because it is pumped by the oil pump 95 driven by the rotating shaft 5. In other words, the rotational unbalance due to the mass of the lubricating oil changes during the operation of the lubricating oil itself, so it is difficult to offset by providing a balance weight in advance. In the machine, there was a problem that vibration due to imbalance could not be sufficiently reduced.
[0017]
According to the present invention, in order to eliminate unstable unbalance due to lubricating oil, a balance weight is provided in the back space to prevent lubricating oil from accumulating in the back space, to prevent occurrence of irregular imbalance, and to reduce vibration. An object of the present invention is to provide a scroll compressor having a small number of scroll compressors.
[0018]
[Means for Solving the Problems]
In order to solve the conventional problem, the scroll compressor according to the present invention has an unstable balance due to lubricating oil flowing into and out of the back space by providing a balance weight having a size substantially filling the back space of the orbiting scroll. This is to prevent the occurrence of imbalance. The mass of the unbalance weight provided on the rotor end face is reduced by the amount of the unbalance weight provided in the back space.
[0019]
With this configuration, it is possible to minimize the amount of lubricating oil flowing into and out of the rear space and to eliminate a factor that causes unstable centrifugal force. As a result, vibration of the compressor can be reduced.
[0020]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0021]
(Embodiment 1)
FIG. 1 is a vertical sectional view of a scroll compressor according to Embodiment 1 of the present invention, FIG. 2 is a perspective view of a drive bush according to Embodiment 1, and FIG. The figure is shown. In the drawings, the same components as those in FIGS. 6 to 9 are denoted by the same reference numerals, and description thereof will be omitted.
[0022]
In FIG. 1, the sealed housing 8 includes an electric motor M including a stator Mb and a rotor Ma, a compression mechanism C driven by the electric motor M, and a rotational driving force from the electric motor M to the compression mechanism C. The rotary shaft 5 for transmitting the power is housed. The compression mechanism section C includes a frame 6, a fixed scroll 1 having fixed scroll blades, and a revolving scroll blade 21 (end plate) that meshes with the fixed scroll blades to form a plurality of compression work spaces. The orbiting scroll 2 is provided with an Oldham ring 3 for preventing the orbiting scroll 2 from rotating. A balance weight 90 is provided above the rotor Ma and a balance weight 91 is provided below the rotor Ma in order to offset imbalance due to the orbiting motion of the movable member including the orbiting scroll 2. Further, a lubricating oil 96 is stored on the bottom surface in the closed housing 8. The lubricating oil 96 is pumped up by an oil pump 95, passes through an oil passage 94 provided in the rotary shaft 5, and is discharged into a turning scroll back space 97 between the frame 6, the turning scroll 2 and the boss 23. By providing the balance weight 92 which substantially fills the back space 97 in the orbiting scroll back space 97, the lubricating oil 96 does not accumulate in the back space 97, and since the balance weight is used, the volume and mass are constant. is there. Thus, the centrifugal force around the orbiting scroll due to the change in the orbiting speed becomes constant.
[0023]
Here, a more detailed description will be given with reference to FIGS. FIG. 4 schematically shows the state in the orbiting scroll back space 97. The centrifugal force Fo generated by the balance weight 92 provided in the orbiting scroll back space 97 is equal to the centrifugal force Fp of the orbiting scroll 2 and the center of the rotary shaft 5. Since O acts in the opposite direction, the centrifugal force Fp ′ obtained by combining Fp and Fo becomes smaller than Fp.
[0024]
Therefore, the product m1 ′ · r1 ′ of the unbalanced amount m1 ′ of the movable member and the radius of rotation r1 ′ of the movable member in FIG. 5, which indicates the balance, is the unbalanced amount m1 of the movable member and the radius of rotation r of the movable member in FIG. M1 · r1.
[0025]
Since the unbalance amount of the movable member is changed by the amount of the unbalance, it is necessary to reset the balance weight.
[0026]
The dynamic balance equation shown in FIG. 5 is such that the mass of the balance weight 90 above the rotor Ma is m2 ′, the mass of the balance weight 91 below the rotor Ma is m3 ′, and the unbalance amount of the movable member is the thrust surface of the center of gravity. L1 is the axial distance from 98, L2 is the axial weight of the balance weight 90 at the upper end of the rotor Ma from the thrust surface 98, and L2 is the axial weight of the balance weight 91 below the rotor Ma. Is L3,
[0027]
[Equation 3]

[0028]
Is represented by
[0029]
In addition, the static balance is
[0030]
(Equation 4)

[0031]
Is represented by Here, from Equations 1 to 4, m2 ′ and m3 ′ are respectively
[0032]
(Equation 5)

[0033]
(Equation 6)

[0034]
It becomes. Therefore, the balance weight above the rotor is
[0035]
(Equation 7)

[0036]
The balance weight on the lower side of the rotor
[0037]
(Equation 8)

[0038]
Only set it smaller. As a result, the balance of the compressor main body is better than that in the conventional case where unstable unbalance is assumed by the lubricating oil, and the vibration of the compressor can be reduced.
[0039]
The centrifugal force Fo of the balance weight 92 provided in the orbiting scroll rear space 97 is calculated as follows. In FIG. 4, it is assumed that the orbiting scroll rear space 97 is a hatched portion, and a balance weight having a specific mass ρo is provided here. The diameter of the room of the orbiting scroll back space 97 is D, the diameter of the boss of the orbiting scroll 2 is d, and the height of the back space 97 is substantially the same as the height of the boss of the orbiting scroll 2. It is assumed that the balance weight of the section rotates with the turning motion of the drive bush 54. Considering the rotational balance around O, the position Oo of the center of gravity of the hatched portion and the unbalance mass mo fill the orbiting scroll back space 97 with the balance weight 92, and have the same size as the boss of the orbiting scroll 2 on the opposite side. This is the same as placing a disk with the same specific mass ρo as the balance weight 92,
[0040]
(Equation 9)

[0041]
(Equation 10)

[0042]
It becomes.
[0043]
Therefore, if the rotational angular velocity is ω,
[0044]
[Equation 11]

[0045]
It becomes.
[0046]
On the other hand, the centrifugal force Fp of the boss 23 has its center of gravity at r1, and the unbalance amount mp is given by ρ1 where the specific mass of the boss of the orbiting scroll 2 is
[0047]
(Equation 12)

[0048]
It becomes.
[0049]
Therefore,
[0050]
(Equation 13)

[0051]
Considering the rotational unbalance Fo of the rotating balance weight 92 that rotates with the boss of the orbiting scroll 2,
[0052]
[Equation 14]

[0053]
By calculating the specific mass of the boss of the orbiting scroll 2 by (ρ1−ρo) and setting the balance weight, the balance weight can be set in consideration of the imbalance in rotation of the balance weight 92.
[0054]
Although the above description has been made with reference to the hermetic electric compressor, the present invention can be applied to an open scroll compressor.
[0055]
【The invention's effect】
As is apparent from the above embodiment, the invention according to claim 1 has a housing having a suction port and a discharge port, and a spiral scroll formed on an end plate and provided in the housing. A movable scroll having a spiral body formed on an end plate and being incorporated so as to be offset from the fixed scroll and a center, a rotary shaft rotatably supported by the housing, and an end of the rotary shaft. A drive bush that is eccentrically disposed on the portion and imparts a revolving motion to the orbiting scroll, and an Oldham ring that allows only the orbiting of the orbiting scroll and prevents rotation. The closed space between the scroll and the fixed scroll moves toward the center of the spiral while reducing the volume, and the fluid in the closed space is compressed. In a scroll type compressor, a balance weight that substantially fills a space between the frame, the orbiting scroll, and the boss (a space behind the orbiting scroll) is provided with a balance weight 92 that substantially fills a space 97 behind the orbiting scroll. According to this configuration, since the unstable imbalance due to the lubricating oil 96 is eliminated, the balance of the compressor body is improved, and the vibration of the compressor body can be reduced.
[0056]
The cost can be reduced by forming the balance weight of claim 2 or 3 from an inexpensive sintered material.
[0057]
In the invention described in claim 5, the size of the balance weight provided in the rotor can be reduced by configuring the balance weight according to claim 2 or 3 from a material having a specific gravity larger than that of the orbiting scroll.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a scroll compressor of the present invention. FIG. 2 is a perspective view of a drive bush of the present invention. FIG. 3 is a balance diagram of the present invention. FIG. FIG. 6 is a longitudinal sectional view of a conventional scroll compressor. FIG. 7 is a balance diagram of a conventional scroll compressor that does not consider the mass of lubricating oil. FIG. Balance diagram of conventional scroll compressor considering oil mass [Fig. 9] Balance diagram of conventional rotary shaft [Explanation of reference numerals]
REFERENCE SIGNS LIST 1 fixed scroll 2 orbiting scroll 3 Oldham ring 5 rotating shaft 6 frame 8 hermetic housing 11 fixed scroll head plate 12 fixed scroll scroll wrap 13 discharge port 14 discharge cavity 15 suction passage 17 check valve 21 orbiting scroll head plate 22 orbiting scroll swirl Wrap 23 Boss 24 Sealed space 54 Drive bush 55 Slide hole 59 Eccentric pin 71 Upper bearing 72 Lower bearing 73 Swivel bearing 82 Suction pipe 83 Discharge pipe 90 Balance weight 91 Balance weight 92 Balance weight 93 Oil discharge groove 94 Oil passage 95 Oil pump 96 Lubricating oil 98 Thrust surface 97 Orbiting scroll back space C Compression mechanism M Electric motor Ma Rotor Mb Stator

Claims (1)

A fixed scroll having a spiral wrap formed on a head plate having a discharge port at the center is fixed to a housing, a spiral wrap is formed on the head plate, and a revolving boss having a cylindrical boss is provided at the center of the side of the anti-swirl wrap of the head plate. The scroll is combined so that the fixed scroll and the spiral wrap mesh with each other to form a compression chamber. The orbiting scroll is held by the fixed scroll and a frame so as to be able to make a revolving motion whose rotation is restricted, and the boss is turned by the boss. A rotary shaft for driving the scroll is slidably connected, and at the same time, a scroll compression mechanism is provided on the outer peripheral side of which is formed a rotary scroll back space allowing rotary motion, and the boss and rotary shaft are lubricated. A scroll compressor in which lubricating oil flows into the space behind the orbiting scroll; Scroll compressor Le rear space, characterized in that they are substantially filled by balance weight which rotates together with the rotating shaft.

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