JPS62168976A - Structure of rotor of rotation speed variable compressor - Google Patents

Abstract

PURPOSE:To prevent an oil face from being disturbed by the end part of a rotor and prevent lubricating oil from flowing out of a compressor by keeping the balance of rotation without forming irregularity on the end part on the oil face side of a rotor. CONSTITUTION:A part of the periphery of the end ring 15 of a rotor formed with aluminum, etc. is cut out, forming a projected part 15'. A cutout ring 20 having the same shape as the cut-out part while having a different specific gravity from that of the projected part 15', e.g., of a zinc alloy brass, etc. is formed. And, this cutout ring 20 is closely installed to the cut-out part of the end ring 15 leaving no space between them, to keep the balance of rotation by means of difference in specific gravity between the projected part 15' and the cutout ring 20.

Description

【発明の詳細な説明】 で変化させて運転する回転数可変圧縮機に使用する回転
子の構造に関するものである。DETAILED DESCRIPTION OF THE INVENTION This invention relates to the structure of a rotor used in a variable rotation speed compressor that operates by changing the rotation speed.

〔従来技術〕[Prior art]

特に家庭用ルームニアコンディショナに空調負荷（こ応
じて圧縮機の回転数を増減させ空調能力を制御するもの
がある。年間空調負荷に伴う回転数制御箱１ｍは大幅で
あり圧縮機の信頼性が大きな問題となる。特に高速運転
時に圧縮機内の潤滑油が冷媒と共に圧縮機外へ流出し圧
縮機内の油面が低発明 本骨噂は高速運転時に、圧縮機内の潤滑油の圧縮機の外
へ流出量を低下させ曲面低下を防止する従来の一般的な
圧縮機の構造を第１図に示す。In particular, some home room conditioners control the air conditioning capacity by increasing or decreasing the rotation speed of the compressor according to the air conditioning load (according to the air conditioning load).The rotation speed control box 1m required for the annual air conditioning load is large, and the reliability of the compressor is affected. Especially during high-speed operation, the lubricating oil inside the compressor flows out of the compressor together with the refrigerant, resulting in a low oil level inside the compressor.The main rumor is that during high-speed operation, the lubricating oil inside the compressor leaks out of the compressor together with the refrigerant. FIG. 1 shows the structure of a conventional general compressor that reduces the flow rate to the compressor and prevents the curved surface from decreasing.

ケース上内の上部に電動部２を下部に８Ｅ縮機構部Ｊを
配設し潤滑油４はケース上の底部に貯溜する。An electric motor part 2 is arranged in the upper part of the case, and an 8E compression mechanism part J is arranged in the lower part, and lubricating oil 4 is stored in the bottom part of the case.

固定子５はケース上に固定され回転子６はクランク・紬
７の上部に固定されている。圧縮室はシリンダ９、上ベ
アリング８．下ベアリングｌＯによって形成され、クラ
ンク軸７の回転によりクランク軸７の偏心部７′に回転
自在に嵌入したローラ１２が偏心公転し仕切板（図示せ
ず）により高庄と低圧を区切り冷媒ガスを圧縮する構造
となっている。The stator 5 is fixed on the case, and the rotor 6 is fixed on the upper part of the crank pongee 7. The compression chamber is a cylinder 9, an upper bearing 8. The roller 12 formed by the lower bearing IO and rotatably fitted into the eccentric portion 7' of the crankshaft 7 revolves eccentrically as the crankshaft 7 rotates, and a partition plate (not shown) separates high pressure and low pressure, thereby discharging the refrigerant gas. It has a compressible structure.

圧縮されたガスはＤサイセンサ１３内に吐出サレ−破線
の矢印の様に下ベアリング１０、シリンダ９゜ウニベア
リング８のガス通路を通ってケース上内に解放される。The compressed gas is discharged into the D size sensor 13, passes through the gas passage of the lower bearing 10, the cylinder 9.degree. sea urchin bearing 8, and is released into the case as indicated by the broken line arrow.

シャフト７には給油用スパイラル溝１４が設置ＥＫれ上
ベアリング８の潤滑を行なっている。回転子６の上下端
は端絡環１５．１６がありシャフト７の偏心部７′及び
ローラ１２が偏心公転することによる遠心力と平衡する
ように端絡環１５．１６に切欠環１７．１８が取付けら
れている。この従来の構造で高速運転した場合、多量の
潤滑油がＤパイプ１９より吐出され油面４が低下してし
まう原因として給油スパイラル溝１４の設計が低速時に
も充分なる給油が可能なようにしであるため高速時には
非常に多量な潤滑油が給油スパイラル１４を流れ出口１
４′より流出し回転子６が高速で回転しているため端絡
環１５の内側を通過し破線の矢印の様に流れる。第２図
に示す様に切欠環１７は端絡環１５に固着され高速で回
転するため前記破線の矢印の様に流出した潤滑油が切欠
環１７の側面２１に激しく衝突し微細化され霧状になり
冷媒ガスの流れに乗りＤパイプ１９より流出することが
発見された。他の主な原因として、上線されたガスの中
には多量の潤滑油を含んでいるが上ベアリング８のガス
通路より破線の矢印の如く流出した冷媒ガスが前記切欠
環１７に衝突し霧状に微細化しケース上に届まることな
くＤパイプ１９より流出する。更に突出した切欠環１７
が高速で回転しているため冷媒ガスのうず流が発生しそ
れにより油面４が攪乱されしぶきが発生へ流出してしま
う原因は主に回転子６の下部にバする。端絡環１５の円
周の一部を厚さ方向に凸部１５′を形成し、凸部１５′
の内径、外径、高さ寸法か同一で円周長さか端絡環１５
の凸部１５’以外の円周長さとほぼ同一でかつ必要に応
じて前記凸部１５′の比重と異なる材質の切欠環２０を
第４図に示すようにほぼ隙間なく取付けるようにしたも
のである、一般に端絡環１５にはアルミニウムを。A spiral groove 14 for oil supply is installed on the shaft 7 to lubricate the EK upper bearing 8. The upper and lower ends of the rotor 6 have end rings 15.16, and cut-out rings 17.18 are provided on the end rings 15.16 to balance the centrifugal force caused by eccentric rotation of the eccentric portion 7' of the shaft 7 and the roller 12. is installed. When operating at high speed with this conventional structure, a large amount of lubricating oil is discharged from the D pipe 19, causing the oil level 4 to drop.The reason for this is that the design of the oil supply spiral groove 14 allows for sufficient oil supply even at low speeds. Therefore, at high speeds, a very large amount of lubricating oil flows through the oil supply spiral 14 to the outlet 1.
Since the rotor 6 is rotating at a high speed, it flows out from the end ring 15 and flows as shown by the broken line arrow. As shown in FIG. 2, the notched ring 17 is fixed to the end ring 15 and rotates at high speed, so the lubricating oil that flows out as shown by the broken arrow violently collides with the side surface 21 of the notched ring 17 and is atomized into mist. It was discovered that the refrigerant gas flowed out from the D pipe 19 due to the flow of refrigerant gas. Another main cause is that the overlined gas contains a large amount of lubricating oil, but the refrigerant gas that flows out from the gas passage of the upper bearing 8 as shown by the broken arrow collides with the notch ring 17 and forms a mist. The particles become fine and flow out from the D pipe 19 without reaching the top of the case. Further protruding cutout ring 17
Since the rotor rotates at a high speed, a swirling flow of refrigerant gas is generated, which disturbs the oil level 4 and causes splashes to flow out, mainly at the lower part of the rotor 6. A protrusion 15' is formed in a part of the circumference of the end ring 15 in the thickness direction, and the protrusion 15'
The inner diameter, outer diameter, and height dimensions are the same, and the circumference length or end ring 15
As shown in FIG. 4, a cut-out ring 20 having a circumferential length that is approximately the same as the length of the circumference other than the convex portion 15' and made of a material different from the specific gravity of the convex portion 15', if necessary, is attached with almost no gap. Generally, the end ring 15 is made of aluminum.

切欠環２０には亜鉛合金黄銅等を用い両者の比重差によ
って不平衡量を設定することができる。以上の如くの工
夫により、第２図に示す切欠環１７の側面２１が端絡環
１５の凸Ｒ１５’により隠れ高速回転時潤滑油が微細化
され冷媒の流れに乗り圧混動機の回転子の端絡環の円周
の一部分を端絡環の厚さ方向に凸部とし、他の円周部分
に内径、外径、厚さが前記凸部とほぼ同一寸法で比重が
端絡環と異なる切欠環をほぼすき間なく取り付けたので
前記切欠環の側面が前記凸部側面により隠され高速回転
時に上ベアリングの給油スパイラル溝より流出した潤滑
油や上ベアリングのガス通路から流出する冷媒ガスに混
入した潤滑油を微細化し。The notched ring 20 is made of zinc alloy brass or the like, and the amount of unbalance can be set based on the difference in specific gravity between the two. With the above-mentioned device, the side surface 21 of the notched ring 17 shown in FIG. A part of the circumference of the end ring is a convex part in the thickness direction of the end ring, and another part of the circumference has an inner diameter, an outer diameter, and a thickness that are approximately the same as the convex part, but a specific gravity that is different from that of the end ring. Since the notched ring was installed with almost no gaps, the side surface of the notched ring was hidden by the side surface of the convex part, and during high speed rotation, the lubricating oil flowing out from the oil supply spiral groove of the upper bearing and the refrigerant gas flowing out from the gas passage of the upper bearing were mixed in. Refine lubricating oil.

霧状にして冷媒ガスの流れに伴ってＤパイプより１′＋
：船祷の八へ流出させるＩＪを犬１臨に減少させる効果
がある。更に曲面の攪乱も減少するため潤滑油の流出が
減少する。1'+ from the D pipe with the flow of refrigerant gas.
: It has the effect of reducing the IJ flowing to Funai no Hachi to Inu 1 Rin. Furthermore, the disturbance of the curved surface is reduced, which reduces lubricant leakage.

【図面の簡単な説明】[Brief explanation of drawings]

第４図は第３図をＰ方向から見た図、第５図は切欠環の
図である。 ユ・・・ケース、Ａ・・パ屯動部、旦・・・圧縮機構部
、４・・・潤滑油曲面、５・・・固定子、６・・・回転
子、７・・・クランクシャフト、７′・・・偏心部、８
・・・上ベアリング、９・・・シリン＃−，１０・・・
下ベアリング、１２・・・ローラ、１３・・・Ｄサイセ
ンサ、１４・・・給油用スパイラル溝、１４′・・・出
口、１５・・・端絡環、１６・・・端絡環。 １７・・・切欠環、１８・・・切欠環、１９・・・Ｄパ
イプ。 ２０・・・切欠環、２１・・・側面、１５′・・・凸部
。FIG. 4 is a view of FIG. 3 viewed from direction P, and FIG. 5 is a view of the notched ring. U...Case, A...Packing section, D...Compression mechanism section, 4...Lubricating oil curved surface, 5...Stator, 6...Rotor, 7...Crankshaft , 7'... Eccentric part, 8
...Upper bearing, 9...Cylinder #-, 10...
Lower bearing, 12... Roller, 13... D size sensor, 14... Spiral groove for oil supply, 14'... Outlet, 15... End ring, 16... End ring. 17... Notched ring, 18... Notched ring, 19... D pipe. 20... Notch ring, 21... Side surface, 15'... Convex portion.

Claims (1)

【特許請求の範囲】[Claims] 必要に応じて回転数を変化させ低速から高速の広範囲で
運転する回転数可変圧縮機で電動機の回転子の端絡環の
円周の一部分を端絡環の厚さ方向に凸部とし、他の円周
部分に内径、外径、厚さが前記凸部とほぼ同一寸法で比
重が端絡環と異なる切欠環をほぼすき間なく取りつけた
ことを特徴とする回転数可変圧縮機の回転子の構造。A variable rotation speed compressor that operates over a wide range from low speed to high speed by changing the rotation speed as necessary, has a part of the circumference of the end ring of the motor rotor as a convex part in the thickness direction of the end ring, and other parts. A rotor for a variable rotation speed compressor, characterized in that a notched ring having an inner diameter, an outer diameter, and a thickness that are approximately the same as those of the convex portion and having a specific gravity different from that of the end ring is attached almost without gaps to the circumferential portion of the rotor. structure.