JP3909415B2

JP3909415B2 - Scroll compressor

Info

Publication number: JP3909415B2
Application number: JP2003091047A
Authority: JP
Inventors: 豪土屋; 睦憲松永; 泰成飯塚; 中村　　聡; 優太田原; 俊典安則; 修士長谷川; 慶治田中; 英治佐藤; 功早瀬; 洋一村井; 裕一柳瀬; 和幸藤村
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 2003-03-28
Filing date: 2003-03-28
Publication date: 2007-04-25
Anticipated expiration: 2023-03-28
Also published as: JP2004293531A

Description

【０００１】
【発明の属する技術分野】
本発明は、冷媒、空気、及びその他の圧縮性ガスを取扱うスクロール圧縮機に係り、特に旋回スクロール部材の背面側を構成する空間を中央部空間と外周部空間に圧力的に分離するシール材を備えたスクロール圧縮機に好適なものである。
【０００２】
【従来の技術】
スクロール圧縮機は、冷凍・空調機器用の圧縮機として様々な分野で広く活用されている。他形態の圧縮機に比べて高効率、高信頼性、静音などの優位性を備えた圧縮機と言われている。
【０００３】
従来のスクロール圧縮機としては、例えば特開平８−１２１３６６号公報（特許文献１）に示されたものがある。このスクロール圧縮機は、旋回スクロール部材の反ラップ側シール面と前記シール面に対面するフレームとの間で、前記フレームのリング状溝に保持させたシールリングを設けたものである。このシールリングにより、中心部にあってほぼ吐出圧力に等しい圧力を有すると共に密閉容器内の底部に溜められている潤滑油が上部へ導かれる給油路を開口させた第１の空間と、外周部にあって吸入圧力と吐出圧力の中間の圧力に維持される第２の空間とに分割している。
【０００４】
この分割により、旋回スクロール部材に第1の空間と第２の空間の両方の圧力に応じた圧力を作用させ、旋回スクロール部材を固定スクロール部材に押付けて両者の間をシールする構成としている。また、前記分割により、第１の空間と第２の空間との圧力差に相当する力をシールリングに下側から上側へ作用させてシールリングの上端面と旋回スクロール部材の反ラップ側シール面との間をシールすると共に、同じく前記圧力差に相当する力を内側から外側に作用させてシールリングの外周面とリング状溝の外周面との間でもシールする構成としている。
【０００５】
そして、シールリングの上端面に第１の空間から第２の空間へと差圧により必要最小限の潤滑油を漏洩させる油漏出手段としての溝を設けると共に、第１の空間内の残余の大部分の潤滑油を密閉容器内の圧縮ガスと混合させることなく密閉容器内底部へ戻す油戻し手段を設けている。
【０００６】
係る構成によって、高い軸受信頼性、良好な圧縮効率、低い油上り量を得ることができるようになっている。
【０００７】
また、この従来のスクロール圧縮機においては、クランク軸を滑り軸受で構成された主軸受で回転自在に係合し、この滑り軸受をフレームに第1の空間に対面する側から挿入して装着している。
【０００８】
【特許文献１】
特開平８−１２１３６６号公報
【０００９】
【発明が解決しようとする課題】
係る従来のスクロール圧縮機における固定スクロール部材への旋回スクロール押付け力は、ほぼ吐出圧力に等しい圧力を有する第１の空間と中間の圧力に維持される第２の空間とにより生成する旋回スクロール押上げ力と、圧縮室側で生じる旋回スクロール押下げ力とのバランスにより決定される。従来のスクロール圧縮機では、主軸受として滑り軸受を用いているため、主軸受の外径が小さいものであり、主軸受の外径にほとんど制約されることなく、第１の空間と第２の空間との比率（換言すれば、第１の空間の外径、またはシールリングの内径）をフレームの第１の空間に対面する部分のシールリングの位置を変えることによって任意に設定することができるものであった。しかし、主軸受として滑り軸受を用いているため、軸受信頼性が低いという課題があった。
【００１０】
そこで、軸受信頼性を向上するために、主軸受として転がり軸受を用いることが考えられる。しかし、転がり軸受は滑り軸受に比較してその外径が極めて大きいものであり、従来のスクロール圧縮機の構成において単に転がり軸受を用いる場合には、シールリングの内径を転がり軸受の外径より大きくしなければならない。このため、ほぼ吐出圧力に等しい圧力を有する第1の空間の旋回スクロール部材に作用する範囲が極めて大きくなり、旋回スクロール押上げ力が過剰になって機械摺動損失の増大及び信頼性の低下を招くという新たな課題が生ずる。
【００１１】
本発明の目的は、クランク軸の軸受として転がり軸受を用いて軸受信頼性の向上を図りつつ、固定スクロールへの旋回スクロール押付け力を適正化し、旋回スクロールと固定スクロールとの機械摺動部における機械摺動損失を低減してエネルギー効率の向上を図ると共にその機械摺動部の過剰押付けを抑制して信頼性の向上を図ることができるスクロール圧縮機を得ることにある。
【００１２】
【課題を解決するための手段】
前記目的を達成するために、本発明は、固定スクロール部材及び旋回スクロール部材を組み合わせて圧縮室を形成した圧縮部と、この圧縮部を駆動する駆動部と、前記圧縮部及び前記駆動部を収納する密閉容器とを備えたスクロール圧縮機において、前記旋回スクロール部材と前記駆動部の回転駆動手段とを連結するクランク軸と、前記クランク軸の主軸部を前記回転駆動手段より圧縮室側で支持する主軸支持部と、前記主軸支持部を配設する部材と、前記旋回スクロール部材の背面側を構成する空間をほぼ吐出圧力になる中央部空間とこの中央部空間の圧力より低い圧力となる外周部空間とに圧力的に分離するシール材とを備え、前記クランク軸の偏心ピン部を係合する旋回軸支持部を前記旋回スクロール部材に設け、前記偏心ピン部の端面が前記旋回スクロール部材の背面に正対して前記中央部空間の一部を形成するように前記偏心ピン部を前記旋回軸支持部に係合し、前記中央部空間に潤滑油を供給する給油手段を設けると共に前記中央部空間に供給された潤滑油のほとんどが圧縮室と反対側の前記主軸支持部を通過して前記密閉容器底部に戻されるように構成し、前記主軸支持部として転がり軸受を用いると共に、前記シール材で分離された前記中央部空間の外径を前記転がり軸受の外径より小さく構成したことにある。
【００１３】
前記目的を達成するために、本発明は、固定スクロール部材及び旋回スクロール部材を組み合わせて圧縮室を形成した圧縮部と、この圧縮部を駆動する駆動部と、前記圧縮部及び前記駆動部を収納する密閉容器とを備えたスクロール圧縮機において、前記旋回スクロール部材と前記駆動部の回転駆動手段とを連結するクランク軸と、前記クランク軸の主軸部を前記回転駆動手段より圧縮室側で支持する主軸支持部と、前記主軸支持部を配設する部材と、前記旋回スクロール部材の背面側を構成する空間をほぼ吐出圧力になる中央部空間とこの中央部空間の圧力より低い圧力となる外周部空間とに圧力的に分離するシール材とを備え、前記クランク軸の偏心ピン部を係合する旋回軸支持部を前記旋回スクロール部材に設け、前記偏心ピン部の端面が前記旋回スクロール部材の背面に正対して前記中央部空間の一部を形成するように前記偏心ピン部を前記旋回軸支持部に係合し、前記中央部空間に潤滑油を供給する給油手段を設けると共に前記中央部空間に供給された潤滑油のほとんどが圧縮室と反対側の前記主軸支持部を通過して前記密閉容器底部に戻されるように構成し、前記主軸支持部として転がり軸受を用いると共に、前記旋回スクロール部材と前記主軸支持部を配設する部材との間に介在させた前記シール材の内径を前記転がり軸受の外径より小さく構成したことにある。
【００１４】
【発明の実施の形態】
以下、本発明の幾つかの実施形態のスクロール圧縮機を、図を参照しながら説明する。各実施形態の図における同一符号は同一物または相当物を示す。
【００１５】
本発明の第１実施形態のスクロール圧縮機について、図１及び図２を用いて詳細に説明する。
【００１６】
最初に図１を用いて、本発明の第１実施形態を示すスクロール圧縮機の全体構造に関して説明する。
【００１７】
スクロール圧縮機１は、圧縮部２と駆動部３とを密閉容器１００内に収納して構成されている。本実施形態では、圧縮部２と駆動部３とを上下に配置した縦型スクロール圧縮機である。
【００１８】
圧縮部２は、固定スクロール部材１１０と旋回スクロール部材１２０とフレーム１６０を基本要素として構成されている。フレーム１６０は密閉容器１００に固定され、転がり軸受１０４を配設する部材を構成している。固定スクロール部材１１０は、渦巻状ラップ１１０ａと鏡板１１０ｂと吐出口１１０ｅとを基本構成部分として構成され、フレーム１００にボルトを介して固定されている。ラップ１１０ａは鏡板１１０ｂの一側に垂直に立設されている。旋回スクロール部材１２０は、渦巻状ラップ１２０ａと鏡板１２０ｂと軸支持部１２０ｅと軸支持部端面１２０ｆとを基本構成部分として構成されている。ラップ１２０ａは鏡板１２０ｂの一側に垂直に立設されている。軸支持部１２０ｅは鏡板１２０ｂの他側（反ラップ側）に垂直に突出して形成されている。
【００１９】
固定スクロール部材１１０と旋回スクロール部材１２０を噛合せて構成した圧縮室１３０は、旋回スクロール部材１２０が旋回運動することによりその容積が減少する圧縮動作が行われる。この圧縮動作では、旋回スクロール部材１２０の旋回運動に伴って、作動流体が吸込口１４０、吸込空間１３５を経由して圧縮室１３０へ吸込まれ、吸込まれた作動流体が圧縮行程を経て固定スクロール部材１１０の吐出口１１０ｅから密閉容器１００内の吐出空間１３６に吐出され、さらに吐出口１５０を経由して密閉容器１００から吐出される。これによって、密閉容器１００内の空間は吐出圧力に保たれる。
【００２０】
また、設計圧力比より低い低圧力比運転時に生じる過圧縮を防止するために過圧縮防止手段が設けられている。この過圧縮防止手段は、圧縮室１３０と吐出空間１３６とを連通する通路１３８と、過圧縮になるとこの通路１３８を開く弁１３９とを備えて構成されている。
【００２１】
旋回スクロール部材１２０を旋回駆動する駆動部３は、ステータ１０８及びロータ１０７と、クランク軸１０１と、旋回スクロール部材１２０の自転防止機構の主要部品であるオルダムリング１３４と、フレーム１６０と、転がり軸受１０４、１０５と、旋回軸支持部１０３とを基本要素として構成されている。
【００２２】
ここで、ステータ１０８及びロータ１０７は、回転駆動手段４を構成するものであり、回転駆動手段４を電動機とした場合の構成要素である。クランク軸１０１は主軸部１０１ｂと偏心ピン部１０１ａとを一体に備えて構成されている。
転がり軸受１０４、１０５はクランク軸１０１の主軸部１０１ｂを回転自在に係合する主軸支持部を構成する。旋回軸支持部１０３は、クランク軸１０１の偏芯ピン部１０１ａを回転軸方向であるスラスト方向に移動可能にかつ回転自在に係合するように、旋回スクロール部材１２０に備えられている。
【００２３】
クランク軸１０４の主軸支持部である転がり軸受１０４、１０５は、回転駆動手段４の圧縮室側と反圧縮室側とにそれぞれ配置されている。本発明において、圧縮室側の主軸支持部に転がり軸受１０４を用いることは必須である。しかし、反圧縮室側の主軸支持部には図示のような転がり軸受１０５が望ましいが、すべり軸受やその他の軸支持部材でも良い。
【００２４】
オルダムリング１３４は、旋回スクロール部材１２０とフレーム１６０とにより構成した空間である外周部空間１８２ａに配設されている。オルダムリング１３４に形成した直交する２組のキー部分の１組がフレーム１６０に構成したオルダムリング１３４の受け部であるキー溝１４１を滑動し、残りの１組が旋回スクロールラップ１２０ａの背面側に構成したキー溝を滑動する。これによって、旋回スクロール部材１２０はスクロールラップの立設する方向である軸線方向に垂直な面内を自転せずに旋回運動する。
【００２５】
図１及び図２を用いて、旋回スクロール部材１２０の背面側に構成される空間を圧力的に分離するシール部構造に関して説明する。図２は図１の旋回軸支持部端面１２０ｆ付近の拡大図である。
【００２６】
旋回スクロール部材１２０の背面側に構成される空間は、旋回スクロール部材１２０とフレーム１６０と固定スクロール部材１１０とで囲まれて形成される空間である（以下、背圧室という）。
【００２７】
シール部は、旋回軸支持部端面１２０ｆと、これに対面するフレーム１６０の端面部と、この端面部に構成されたリング状溝１６１と、このリング状溝１６１に配設されたシール材１７２とを備えて構成されている。
【００２８】
ここで、旋回軸支持部端面１２０ｆは、旋回軸支持部１２０ｅの反圧縮室側（回転駆動手段側）に形成された端面であり、軸方向に垂直な面で形成されてシール面を構成している。リング状溝１６１は、転がり軸受１０４の外径より小さい内径を有して形成されている。シール材１７２は、背圧室１８０を中央部空間１８１と外周部空間１８２に圧力的に分離している。これによって、中央部空間１８０の外径は転がり軸受１０４の外径より小さくなっている。中央部空間１８１は、旋回軸支持部１２０ｅと偏心ピン部１０１ａとで構成した空間である中央部空間１８１ａと、旋回軸支持部端面１２０ｆとフレーム１６０の端面とで構成した空間である中央部空間１８１ｂとからなっている。また、外周部空間１８２は、旋回スクロール部材１２０とフレーム１６０とにより構成した空間である外周部空間１８２ａと、旋回スクロール部材１２０とフレーム１６０と固定スクロールにより構成した空間である外周部空間１８２ｂとからなっている。
【００２９】
このように構成を採用できるようにするために、本実施形態では、転がり軸受１０４をフレーム１６０の回転駆動手段側からフレーム１６０へ挿入し、挿入した転がり軸受１０４を軸受押さえ２００で固定する構成となっている。軸受押さえ２００はフレーム１６０と別体に形成されている。なお、簡易構造として、軸受押さえ２００を設けなくとも良い。
【００３０】
軸受押さえ２００はフレーム１６０にボルト２０１により固定されている。このようにボルト固定とすることで、軸受押さえ２００とフレーム１６０との間の隙間２０５、２０６を的確にシールできることから、給油経路１８３からの油漏れを抑制することができる。さらにボルト２０１で固定することから、軸受押さえ２００をフレーム１６０に圧入や焼入れなどで固定する場合に比較して、フレーム１６０のリング状溝１７１や転がり軸受１０４部の変形を極めて小さく抑えることができ、各部の信頼性を確保することができる。
【００３１】
なお、軸受押さえ２００は、フレーム１６０の内側に挿入されて転がり軸受１０４を押さえる部分と、フレーム１６０の回転駆動手段側端面に当接してこれに固定される部分とから構成されている。
【００３２】
また、油上り低減の目的で、バランスウェイト１０９の回転動作による気流の乱れを吐出口１５０付近へ作用させないためにバランスウェイトカバー２０３を設けるが、軸受押さえ２００とバランスウェイトカバー２０３の共締めでフレーム１６０へボルト２０１にて固定しているので、部品点数の低減と省スペース化を図ることができる。なお、バランスウェイトカバー２０３の固定は、フレーム１６０とのボルト共締め固定だけに拘らなくとも良い。バランスウェイトカバー２０３は、ステータのコイルエンドの内径より若干小径の略筒状に形成され、バランスウェイト１０９の周囲を覆ってバランスウェイト１０９の回転動作による気流の乱れを吐出口１５０付近へ作用させないようになっている。
【００３３】
主軸支持部１０４、１０５と旋回軸支持部１０３への給油は、クランク軸１０１内に設けた給油経路１０２と外部給油ポンプ１０６とで行なう。即ち、密閉容器１００の下部空間に溜めた潤滑油１３１を外部給油ポンプ１０６で吸引して給油通路１０２を通して各部へ供給する。
【００３４】
給油経路１０２から供給される潤滑油は、偏心ピン部１０１ａ上部の中央部空間１８１ａに達した後、旋回軸支持部１０３を潤滑し、中央部空間１８１ｂへ流出する。中央部空間１８１ｂへ流出した潤滑油は、旋回軸支持部端面１２０ｆに設けたシール部により、微量の潤滑油が外周部空間１８２へ供給されるものの、ほとんどの潤滑油が転がり軸受１０４を通過し、軸受押さえ２００上面に設けた給油経路１８３、排油パイプ１８４を経て、油溜め１３１へ戻される。これによって、旋回スクロール部材の軸支持部１０３とクランク軸の軸支持部１０４を潤滑する潤滑油を吸込口１４０通過後の作動流体と直接混合しないようにすることが実現できる。なお、給油ポンプとしては、図示していないがクランク軸１０１に構成する偏芯回転動作により実現する遠心ポンプ作用を用いても良い。
【００３５】
外周部空間１８２ａ内に配設したオルダムリング１３４等の摺動部を中央部空間１８１ｂへ供給した潤滑油で潤滑するために、中央部空間１８１ｂと外周部空間１８２ａを断続的あるいは連続的に連通させる小孔１７０、１７１を旋回軸支持部端面１２０ｆに設けてある。なお、スクロール圧縮機１の使用条件にもよるが、シール材１７２を介した油漏れだけで必要油量を確保できる場合には、小孔１７０、１７１は必要としない。小孔１７０、１７１は必要油量を確保できる個数であれば良い。また、常に給油することが必要な場合には、小孔１７０、１７１の大きさをシール材１７２のシート幅を超えた大きさとすることにより、常に給油することを可能としている。
【００３６】
中央部空間１８１と転がり軸受１０４と軸受押さえ２００上面に設けた給油経路１８３と排油パイプ１８４は、ポンプ作用による昇圧作用と軸受部や隙間部通過による減圧作用を受けるものの、ほぼ吐出圧力程度の圧力空間となっている。外周部空間１８２ａと連通している外周部空間１８２ｂは、圧縮途中の圧縮室と連通孔１３７を介して断続的あるいは連続的に連通し、吸込圧と吐出圧の間の中間圧力状態となる。これら吐出圧力及び中間圧力を利用して旋回スクロール鏡板１２０ｂの背面を固定スクロール部材１１０方向へ押上げ、圧縮室１３０の気密性を適確に保持するようになっている。なお、スクロール圧縮機１の圧縮部仕様や運転範囲により必要な旋回スクロール押付力が異なってくるため、外周部空間１８２を、吸込圧と吐出圧との間の中間圧力状態ではなく、吸込圧力状態として構成したほうが良い場合もある。その場合には、外周部空間１８２を吸込側に連通するように構成する。
【００３７】
回転軸方向であるスラスト方向に発生した荷重を受けるために、クランク軸１０１が上方に移動したときの荷重を受けるスラスト受け１９０と、下方に移動したときの荷重を受けるスラスト軸受２０４が配設されている。スラスト受け１９０は、旋回スクロールラップ背面に設けた突起部であり、クランク軸１０１とスラスト受け１９０が接触した時に給油経路１０２を閉塞させないように中央に凹部を設けている。また、クランク軸１０１が最も上方に移動した時に、旋回スクロールの軸支持部端面１２０ｆがクランク軸端部１０１ｃと接触せずに、スラスト受け１９０で偏心ピン部１０１ａの端部を受けるように、中央部空間１８１ａを構成する軸方向隙間と中央部空間１８１ｂを構成する軸方向隙間とが設定されている。スラスト軸受２０４は、軸受押さえ２００上に別部材として配設しても良いし、軸受押さえ２００と同一体として構成しても良い。また、簡易構造としては、軸受押さえ２００を設けなくとも良いが、この時はスラスト軸受２０４に相当する機能をクランク軸１０１の反圧縮室側軸支持部１０５に持たせることが必要である。
【００３８】
本実施形態の効果について説明する。
【００３９】
固定スクロール部材１１０への旋回スクロール部材１２０押付け力は、旋回スクロール部材１２０の背面側に構成する空間であって、概略吐出圧力である中央部空間１８１と概略吐出圧力と概略吸込圧力の間の圧力あるいは概略吸込圧力である外周部空間１８２とにより生成する旋回スクロール押上げ力と、圧縮室で生じる旋回スクロール押下げ力とのバランスにより決定される。軸受信頼性の向上のためにクランク軸１０１の圧縮室側軸支持部に転がり軸受１０４を用いた場合において、シールリング１７２の内径あるいは中央部空間１８１の外径を転がり軸受１０４の外径より小さく構成することができれば、概略吐出圧力である中央部空間１８１領域が小さくなり、旋回スクロール部材１２０への押付け力が過剰となることを防止できる。本実施形態の構成であれば、転がり軸受１０４の外径よりシールリング１７２の内径あるいはフレーム１６０のシート面部に構成したリング状溝１６１の内径を小さく構成できるので、概略吐出圧力である中央部空間１８１の作用する範囲を適正に構成し、広範囲に渡る運転範囲で適正な旋回スクロール押付け力を実現できる。
【００４０】
また、過圧縮防止手段１３８、１３９を併用すると、低圧力比運転時の旋回スクロール押下げ力を低減できるので、低圧力比から高圧力比に渡る広範な運転範囲で必要になる旋回スクロール押付け力の幅を小さくすることが可能となり、さらに適確に広範囲に渡る運転範囲で適正な旋回スクロール押付け力を実現できる。
【００４１】
以上のことから、旋回スクロール部材１２０と固定スクロール部材１１０との機械摺動損失を低減しエネルギー効率の向上を図ることができると共に、旋回スクロール部材１２０と固定スクロール部材１１０との機械摺動部の過剰押付けを抑制し信頼性の向上を図ることができる。
【００４２】
次に、本発明の第２実施形態を図３を用いて説明する。この第２実施形態は、次に述べる通り第１実施形態と相違するものであり、その他の点については第１実施形態と基本的には同一である。
【００４３】
この第２実施形態は、フレーム１６０、軸受押さえ２０３及びバランスウェイトカバー２０３の構成が第１実施形態と相違する。フレーム１６０は、軸受押さえ２０３を挿入する部分を第１実施形態よりも長く形成している。フレーム１６０の回転駆動手段側から転がり軸受１０４をフレーム１６０へ挿入し、軸受押さえ２０３でおさえるという基本構成は第１実施形態と同様であるが、軸受押さえ２０３の外径を転がり軸受１０４の外径と同じに形成し、この軸受押さえ２０３をフレーム１６０へ挿入して転がり軸受１０４を押さえるようにしている。そして、フレーム１６０の内周に設けた溝に嵌めた止め輪４０５で軸受押さえ２０３を固定する。止め輪４０５はＣ形止め輪やベベル型止め輪などを用いる。止め輪４０５を用いることで、軸受押さえ２０３の固定を簡単にすることができ、安価なものとすることができる。
【００４４】
また、バランスウェイトカバー２０３をフレーム１６０にボルト２０１により単独で固定している。このバランスウェイトカバー２０３は、ステータ１０８のコイルエンド部１０８ａまで包含するように設置している。これによって、バランスウェイト１０９の回転動作による気流の乱れをまずステータ１０８のエンドコイル部１０８ａで吸収させ、さらにバランスウェイトカバー２０３で吸収させて吐出口３５０付近へ気流の乱れを確実に作用させないようになっている。なお、第２実施形態のバランスウェイトカバー２０３構成は、第１実施形態へ適用しても効果がある。
【００４５】
次に、本発明の第３実施形態を図４を用いて説明する。この第３実施形態は、次に述べる通り第１実施形態と相違するものであり、その他の点については第１実施形態と基本的には同一である。
【００４６】
この第３実施形態では、フレーム１６０は、圧縮室側に転がり軸受１０４の挿入部を形成すると共に、その入口側に軸受押さえ６００の挿入部を形成している。転がり軸受１０４を圧縮室側からフレーム１６０の挿入部に挿入し、次いで、その上に軸受押さえ６００を圧縮室側からフレーム１６０の挿入部に挿入する。軸受押さえ６００は、転がり軸受１０４の外径より小さく、且つ旋回スクロールの軸支持部１２ｅの内径とほぼ同じ内径で形成してある。軸受押さえ６００の一側端面は転がり軸受１０４の端面に当接してこれを押さえるようになっていると共に、他側端面は旋回スクロールの軸支持部端面１２０ｆに極わずかな間隔で対面している。シールリング５７２を配設するリング状溝５６１を軸受押さえ６００の他側端面に形成している。そして、シールシング５７２をリング状溝５６１に配設し、旋回スクロールの軸支持部端面１２０ｆをシール面としている。
【００４７】
また、軸受押さえ６００をフレーム１６０にボルト６０５を用いて締結している。なお、中央部空間１８０に油をある程度溜めて必要油量を外周部空間１８２へ供給するために、クランク軸側面空間６０２を高精度にしておく必要があり、軸受押さえ６００の高精度位置決め手段としてノックピン（図示せず）を併用している。
【００４８】
この第３実施形態では、別部材の軸受押さえ６００をフレーム１６０に圧縮室側から挿入した構成であるので、軸受押さえ６００とフレーム１６０の挿入面（係合面）をシールする必要があり、軸受押さえ６００の外周部にシール部を配設している。このシール部のシール材６０６を軸受押さえ６００の外周面に形成したシール材挿入溝に挿入されているが、シール材６０６をフレーム５６０の内周面に形成したシール材挿入溝に挿入するようにしても良い。図示したシール材６０６は、Ｏリングであるが、フッ素樹脂やポリイミド系樹脂等からなるシールリングでも良い。
【００４９】
【発明の効果】
以上の実施形態の説明から明らかなように、本発明によれば、クランク軸の軸受として転がり軸受を用いて軸受信頼性の向上を図りつつ、固定スクロールへの旋回スクロール押付け力を適正化し、旋回スクロールと固定スクロールとの機械摺動部における機械摺動損失を低減してエネルギー効率の向上を図ると共にその機械摺動部の過剰押付けを抑制して信頼性の向上を図ることができるスクロール圧縮機を得ることできる。
【図面の簡単な説明】
【図１】本発明の第１実施形態のスクロール圧縮機の縦断面図である。
【図２】図１のスクロール圧縮機の要部縦断面図である。
【図３】本発明の第２実施形態のスクロール圧縮機の要部縦断面図である。
【図４】本発明の第３実施形態のスクロール圧縮機の要部縦断面図である。
【符号の説明】
１…スクロール圧縮機、２…圧縮部、３…駆動部、１００…密閉容器、１０１…クランク軸、１０１ａ…偏心ピン部、１０１ｂ…主軸部、１０２…給油経路、１０６・・・給油ポンプ、１０９…バランスウェイト、１１０…固定スクロール部材、１２０…旋回スクロール部材、１２０ｆ…旋回スクロール軸支持部端面、１３０…圧縮室、１３１・・潤滑油、１３４…オルダムリング、１３５・・・吸込空間、１３６…吐出空間、１６０…フレーム、１６１…リング状溝１７０、１７１…小孔、１７２…シールリング、１８０…背圧室、１８１、１８１ａ、１８１ｂ…中央部空間、１８２、１８２ａ、１８２ｂ…外周部空間、１８３…給油経路、１８４…排油パイプ、２００…軸受押さえ、２０１…ボルト、２０３…バランスウェイトカバー、２０４…スラスト受け、６０５…ボルト。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scroll compressor that handles refrigerant, air, and other compressible gases, and in particular, a sealing material that pressure-separates a space constituting the back side of a revolving scroll member into a central space and an outer peripheral space. It is suitable for the scroll compressor provided.
[0002]
[Prior art]
Scroll compressors are widely used in various fields as compressors for refrigeration and air conditioning equipment. It is said to be a compressor having advantages such as high efficiency, high reliability, and low noise compared to other types of compressors.
[0003]
As a conventional scroll compressor, for example, there is one disclosed in Japanese Patent Laid-Open No. 8-121366 (Patent Document 1). This scroll compressor is provided with a seal ring held in a ring-shaped groove of the frame between the anti-wrap side seal surface of the orbiting scroll member and the frame facing the seal surface. The seal ring has a first space in the center that has a pressure substantially equal to the discharge pressure and that opens an oil supply passage through which the lubricating oil stored in the bottom of the sealed container is guided to the top, and an outer peripheral portion. The second space is divided into a second space maintained at a pressure intermediate between the suction pressure and the discharge pressure.
[0004]
By this division, a pressure corresponding to the pressures of both the first space and the second space is applied to the orbiting scroll member, and the orbiting scroll member is pressed against the fixed scroll member to seal between them. Further, by the division, a force corresponding to a pressure difference between the first space and the second space is applied to the seal ring from the lower side to the upper side, so that the upper end surface of the seal ring and the anti-wrap side seal surface of the orbiting scroll member And a force corresponding to the pressure difference is applied from the inside to the outside to seal between the outer peripheral surface of the seal ring and the outer peripheral surface of the ring-shaped groove.
[0005]
Then, a groove as oil leakage means for leaking a minimum amount of lubricating oil from the first space to the second space from the first space to the second space is provided on the upper end surface of the seal ring, and the remaining amount in the first space is large. An oil return means is provided for returning a portion of the lubricating oil to the bottom of the sealed container without mixing with the compressed gas in the sealed container.
[0006]
With such a configuration, high bearing reliability, good compression efficiency, and low oil upflow can be obtained.
[0007]
Further, in this conventional scroll compressor, the crankshaft is rotatably engaged with a main bearing constituted by a sliding bearing, and the sliding bearing is inserted into the frame from the side facing the first space and mounted. ing.
[0008]
[Patent Document 1]
JP-A-8-121366
[0009]
[Problems to be solved by the invention]
In such a conventional scroll compressor, the orbiting scroll pressing force to the fixed scroll member is generated by the orbiting scroll pushing generated by the first space having a pressure substantially equal to the discharge pressure and the second space maintained at an intermediate pressure. This is determined by the balance between the force and the orbiting scroll pressing force generated on the compression chamber side. In the conventional scroll compressor, since the sliding bearing is used as the main bearing, the outer diameter of the main bearing is small, and the first space and the second are almost not restricted by the outer diameter of the main bearing. The ratio to the space (in other words, the outer diameter of the first space or the inner diameter of the seal ring) can be arbitrarily set by changing the position of the seal ring at the portion facing the first space of the frame. It was a thing. However, since a sliding bearing is used as the main bearing, there is a problem that the bearing reliability is low.
[0010]
Therefore, in order to improve bearing reliability, it is conceivable to use a rolling bearing as the main bearing. However, the outer diameter of a rolling bearing is much larger than that of a sliding bearing. When a rolling bearing is simply used in the configuration of a conventional scroll compressor, the inner diameter of the seal ring is larger than the outer diameter of the rolling bearing. Must. Therefore, the range that acts on the orbiting scroll member in the first space having a pressure substantially equal to the discharge pressure becomes extremely large, and the orbiting scroll pushing force becomes excessive, resulting in an increase in mechanical sliding loss and a decrease in reliability. A new problem arises.
[0011]
An object of the present invention is to improve the bearing reliability by using a rolling bearing as a bearing of a crankshaft, optimize the turning scroll pressing force to the fixed scroll, and improve the machine in the mechanical sliding portion between the turning scroll and the fixed scroll. An object of the present invention is to obtain a scroll compressor capable of reducing the sliding loss and improving the energy efficiency and suppressing the excessive pressing of the sliding portion of the machine and improving the reliability.
[0012]
[Means for Solving the Problems]
In order to achieve the above-mentioned object, the present invention includes a compression unit in which a compression chamber is formed by combining a fixed scroll member and a turning scroll member, a drive unit that drives the compression unit, and the compression unit and the drive unit. In the scroll compressor including the hermetically sealed container, the crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit, and the main shaft portion of the crankshaft are supported on the compression chamber side from the rotation drive means. A main shaft support portion, a member that disposes the main shaft support portion, a central space that substantially discharges the space that forms the back side of the orbiting scroll member, and an outer peripheral portion that has a pressure lower than the pressure of the central space A revolving shaft support portion that engages with an eccentric pin portion of the crankshaft, and is provided on the orbiting scroll member. There engages the eccentric pin portion to form part of the directly opposite to the central portion space on a rear surface of the orbiting scroll member to the pivot support portion, oil supply portion for supplying a lubricating oil to said central portion space And providing Lubricating oil supplied to the central space Most of The main spindle support on the opposite side of the compression chamber Configured to pass through the bottom of the sealed container. In addition, a rolling bearing is used as the main shaft support portion, and the outer diameter of the central space separated by the sealing material is smaller than the outer diameter of the rolling bearing.
[0013]
In order to achieve the above-mentioned object, the present invention includes a compression unit in which a compression chamber is formed by combining a fixed scroll member and a turning scroll member, a drive unit that drives the compression unit, and the compression unit and the drive unit. In the scroll compressor including the hermetically sealed container, the crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit, and the main shaft portion of the crankshaft are supported on the compression chamber side from the rotation drive means. A main shaft support portion, a member that disposes the main shaft support portion, a central space that substantially discharges the space that forms the back side of the orbiting scroll member, and an outer peripheral portion that has a pressure lower than the pressure of the central space A revolving shaft support portion that engages with an eccentric pin portion of the crankshaft, and is provided on the orbiting scroll member. There engages the eccentric pin portion to form part of the directly opposite to the central portion space on a rear surface of the orbiting scroll member to the pivot support portion, oil supply portion for supplying a lubricating oil to said central portion space And providing Lubricating oil supplied to the central space Most of The main spindle support on the opposite side of the compression chamber Configured to pass through the bottom of the sealed container. In addition, a rolling bearing is used as the main shaft support portion, and the inner diameter of the seal material interposed between the orbiting scroll member and the member on which the main shaft support portion is disposed is smaller than the outer diameter of the rolling bearing. It is in.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, scroll compressors according to some embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.
[0015]
A scroll compressor according to a first embodiment of the present invention will be described in detail with reference to FIGS. 1 and 2.
[0016]
First, the overall structure of the scroll compressor according to the first embodiment of the present invention will be described with reference to FIG.
[0017]
The scroll compressor 1 is configured by storing a compression unit 2 and a drive unit 3 in a sealed container 100. In this embodiment, it is a vertical scroll compressor in which the compression unit 2 and the drive unit 3 are arranged vertically.
[0018]
The compression unit 2 is configured with the fixed scroll member 110, the orbiting scroll member 120, and the frame 160 as basic elements. The frame 160 is fixed to the hermetic container 100 and constitutes a member for disposing the rolling bearing 104. The fixed scroll member 110 includes a spiral wrap 110a, an end plate 110b, and a discharge port 110e as basic components, and is fixed to the frame 100 via bolts. The wrap 110a is erected vertically on one side of the end plate 110b. The orbiting scroll member 120 includes a spiral wrap 120a, an end plate 120b, a shaft support portion 120e, and a shaft support portion end face 120f as basic components. The wrap 120a is erected vertically on one side of the end plate 120b. The shaft support portion 120e is formed so as to protrude perpendicularly to the other side (anti-wrap side) of the end plate 120b.
[0019]
The compression chamber 130 configured by meshing the fixed scroll member 110 and the orbiting scroll member 120 is subjected to a compression operation in which the volume is reduced by the orbiting movement of the orbiting scroll member 120. In this compression operation, the working fluid is sucked into the compression chamber 130 through the suction port 140 and the suction space 135 as the orbiting scroll member 120 rotates, and the sucked working fluid passes through the compression stroke and is fixed. 110 is discharged from the discharge port 110 e into the discharge space 136 in the sealed container 100, and is further discharged from the sealed container 100 via the discharge port 150. As a result, the space in the sealed container 100 is maintained at the discharge pressure.
[0020]
Further, an overcompression preventing means is provided in order to prevent overcompression that occurs during operation at a low pressure ratio lower than the design pressure ratio. This overcompression preventing means includes a passage 138 that allows the compression chamber 130 and the discharge space 136 to communicate with each other, and a valve 139 that opens the passage 138 when overcompression occurs.
[0021]
The driving unit 3 that orbits the orbiting scroll member 120 includes a stator 108 and a rotor 107, a crankshaft 101, an Oldham ring 134 that is a main part of the rotation preventing mechanism of the orbiting scroll member 120, a frame 160, and a rolling bearing 104. , 105 and the pivot support 103 are configured as basic elements.
[0022]
Here, the stator 108 and the rotor 107 constitute the rotation driving means 4 and are components when the rotation driving means 4 is an electric motor. The crankshaft 101 is configured by integrally including a main shaft portion 101b and an eccentric pin portion 101a.
The rolling bearings 104 and 105 constitute a main shaft support portion that rotatably engages the main shaft portion 101b of the crankshaft 101. The orbiting shaft support portion 103 is provided in the orbiting scroll member 120 so as to engage the eccentric pin portion 101a of the crankshaft 101 so as to be movable and rotatable in the thrust direction that is the rotation axis direction.
[0023]
Rolling bearings 104 and 105, which are main shaft support portions of the crankshaft 104, are arranged on the compression chamber side and the non-compression chamber side of the rotation driving means 4, respectively. In the present invention, it is essential to use the rolling bearing 104 for the main shaft support portion on the compression chamber side. However, a rolling bearing 105 as shown in the drawing is desirable for the main shaft support portion on the anti-compression chamber side, but a slide bearing or other shaft support member may be used.
[0024]
The Oldham ring 134 is disposed in an outer peripheral space 182 a that is a space formed by the orbiting scroll member 120 and the frame 160. One set of two orthogonal key portions formed on the Oldham ring 134 slides on the key groove 141 which is a receiving portion of the Oldham ring 134 formed on the frame 160, and the other set is on the back side of the orbiting scroll wrap 120a. Slide the configured keyway. As a result, the orbiting scroll member 120 orbits without rotating in a plane perpendicular to the axial direction, which is the direction in which the scroll wrap stands.
[0025]
A seal portion structure that separates the space formed on the back side of the orbiting scroll member 120 in terms of pressure will be described with reference to FIGS. 1 and 2. FIG. 2 is an enlarged view of the vicinity of the end surface 120f of the turning shaft support portion of FIG.
[0026]
The space formed on the back side of the orbiting scroll member 120 is a space formed by being surrounded by the orbiting scroll member 120, the frame 160, and the fixed scroll member 110 (hereinafter referred to as a back pressure chamber).
[0027]
The seal portion includes an end surface 120f of the pivot shaft support portion, an end surface portion of the frame 160 facing the end surface, a ring-shaped groove 161 formed on the end surface portion, and a sealing material 172 disposed in the ring-shaped groove 161. It is configured with.
[0028]
Here, the turning shaft support portion end surface 120f is an end surface formed on the anti-compression chamber side (rotation drive means side) of the turning shaft support portion 120e, and is formed by a surface perpendicular to the axial direction to form a seal surface. ing. The ring-shaped groove 161 is formed to have an inner diameter smaller than the outer diameter of the rolling bearing 104. The sealing material 172 pressure-separates the back pressure chamber 180 into a central space 181 and an outer peripheral space 182. As a result, the outer diameter of the central space 180 is smaller than the outer diameter of the rolling bearing 104. The central space 181 is a central space 181a that is a space constituted by the turning shaft support portion 120e and the eccentric pin portion 101a, a central space that is a space constituted by the turning shaft support portion end face 120f and the end face of the frame 160. 181b. The outer peripheral space 182 includes an outer peripheral space 182a that is a space constituted by the orbiting scroll member 120 and the frame 160, and an outer peripheral space 182b that is a space constituted by the orbiting scroll member 120, the frame 160, and the fixed scroll. It has become.
[0029]
In order to be able to adopt the configuration as described above, in the present embodiment, the rolling bearing 104 is inserted into the frame 160 from the rotation driving means side of the frame 160, and the inserted rolling bearing 104 is fixed by the bearing retainer 200. It has become. The bearing retainer 200 is formed separately from the frame 160. As a simple structure, the bearing retainer 200 may not be provided.
[0030]
The bearing retainer 200 is fixed to the frame 160 with bolts 201. By fixing the bolts in this way, the gaps 205 and 206 between the bearing retainer 200 and the frame 160 can be accurately sealed, so that oil leakage from the oil supply path 183 can be suppressed. Further, since the bearing holder 200 is fixed by the bolt 201, the deformation of the ring-shaped groove 171 and the rolling bearing 104 portion of the frame 160 can be suppressed to a very small level as compared with the case where the bearing retainer 200 is fixed to the frame 160 by press-fitting or quenching. The reliability of each part can be ensured.
[0031]
The bearing retainer 200 includes a portion that is inserted inside the frame 160 and retains the rolling bearing 104, and a portion that contacts and is fixed to the end surface of the frame 160 on the side of the rotational driving means.
[0032]
Further, for the purpose of reducing oil rising, a balance weight cover 203 is provided in order to prevent turbulence of the airflow caused by the rotation operation of the balance weight 109 from acting on the vicinity of the discharge port 150, but the frame is formed by fastening the bearing holder 200 and the balance weight cover 203 together. Since the bolts 201 are fixed to 160, it is possible to reduce the number of parts and save space. The balance weight cover 203 may be fixed not only by fixing the bolts to the frame 160 together with the bolts. The balance weight cover 203 is formed in a substantially cylindrical shape that is slightly smaller in diameter than the inner diameter of the coil end of the stator, and covers the periphery of the balance weight 109 so that airflow turbulence caused by the rotation of the balance weight 109 does not act on the vicinity of the discharge port 150. It has become.
[0033]
Oil supply to the main shaft support portions 104 and 105 and the turning shaft support portion 103 is performed by an oil supply path 102 provided in the crankshaft 101 and an external oil supply pump 106. That is, the lubricating oil 131 stored in the lower space of the sealed container 100 is sucked by the external oil pump 106 and supplied to each part through the oil supply passage 102.
[0034]
The lubricating oil supplied from the oil supply path 102 reaches the central space 181a above the eccentric pin portion 101a, and then lubricates the turning shaft support portion 103 and flows out to the central space 181b. The lubricating oil that has flowed into the central space 181b is supplied to the outer peripheral space 182 by the seal portion provided on the end surface 120f of the turning shaft support portion, but most of the lubricating oil passes through the rolling bearing 104. Then, the oil is returned to the oil sump 131 through an oil supply path 183 and an oil drain pipe 184 provided on the upper surface of the bearing retainer 200. Accordingly, it is possible to prevent the lubricating oil that lubricates the shaft support portion 103 of the orbiting scroll member and the shaft support portion 104 of the crankshaft from being directly mixed with the working fluid after passing through the suction port 140. In addition, as an oil supply pump, although not shown in figure, you may use the centrifugal pump effect | action implement | achieved by the eccentric rotation operation | movement comprised in the crankshaft 101. FIG.
[0035]
In order to lubricate the sliding portion such as the Oldham ring 134 disposed in the outer peripheral space 182a with the lubricating oil supplied to the central space 181b, the central space 181b and the outer peripheral space 182a communicate intermittently or continuously. Small holes 170 and 171 are provided in the end surface 120f of the pivot shaft support portion. Although depending on the use conditions of the scroll compressor 1, the small holes 170 and 171 are not necessary when the required amount of oil can be secured only by oil leakage through the sealing material 172. The number of the small holes 170 and 171 may be any number that can secure the required amount of oil. Further, when it is necessary to always supply oil, the size of the small holes 170 and 171 is made larger than the sheet width of the sealing material 172, so that it is possible to always supply oil.
[0036]
The oil supply passage 183 and the oil discharge pipe 184 provided on the upper surface of the central space 181, the rolling bearing 104, and the bearing retainer 200 are subjected to a pressure increasing action by the pump action and a pressure reducing action by passing the bearing part and the gap part, but the discharge pressure is almost the same. It is a pressure space. The outer peripheral space 182b communicating with the outer peripheral space 182a is intermittently or continuously communicated with the compression chamber in the middle of compression through the communication hole 137, and becomes an intermediate pressure state between the suction pressure and the discharge pressure. By utilizing these discharge pressure and intermediate pressure, the back surface of the orbiting scroll end plate 120b is pushed up toward the fixed scroll member 110, so that the airtightness of the compression chamber 130 is appropriately maintained. In addition, since the required orbiting scroll pressing force differs depending on the compression part specification and operation range of the scroll compressor 1, the outer peripheral space 182 is not in the intermediate pressure state between the suction pressure and the discharge pressure, but in the suction pressure state. It may be better to configure as In that case, the outer peripheral space 182 is configured to communicate with the suction side.
[0037]
In order to receive a load generated in the thrust direction which is the rotation axis direction, a thrust receiver 190 which receives a load when the crankshaft 101 moves upward and a thrust bearing 204 which receives a load when moved downward are disposed. ing. The thrust receiver 190 is a protrusion provided on the back of the orbiting scroll wrap, and has a recess in the center so that the oil supply path 102 is not blocked when the crankshaft 101 and the thrust receiver 190 come into contact with each other. Further, when the crankshaft 101 is moved to the uppermost position, the shaft support portion end surface 120f of the orbiting scroll is not in contact with the crankshaft end portion 101c, so that the thrust receiver 190 receives the end portion of the eccentric pin portion 101a. An axial gap constituting the partial space 181a and an axial gap constituting the central space 181b are set. The thrust bearing 204 may be disposed as a separate member on the bearing retainer 200 or may be configured as the same body as the bearing retainer 200. Further, as a simple structure, the bearing holder 200 need not be provided, but at this time, the function corresponding to the thrust bearing 204 needs to be provided to the anti-compression chamber side shaft support portion 105 of the crankshaft 101.
[0038]
The effect of this embodiment will be described.
[0039]
The orbiting scroll member 120 pressing force to the fixed scroll member 110 is a space formed on the back side of the orbiting scroll member 120, and is a pressure between the central space 181 that is an approximate discharge pressure, and an approximate discharge pressure and an approximate suction pressure. Alternatively, it is determined by the balance between the orbiting scroll pushing force generated by the outer peripheral space 182 that is the approximate suction pressure and the orbiting scroll pushing force generated in the compression chamber. When the rolling bearing 104 is used for the compression chamber side shaft support portion of the crankshaft 101 in order to improve the bearing reliability, the inner diameter of the seal ring 172 or the outer diameter of the central space 181 is smaller than the outer diameter of the rolling bearing 104. If it can be configured, the central space 181 region, which is the approximate discharge pressure, becomes small, and it is possible to prevent the pressing force to the orbiting scroll member 120 from becoming excessive. According to the configuration of the present embodiment, the inner diameter of the seal ring 172 or the inner diameter of the ring-shaped groove 161 formed in the seat surface portion of the frame 160 can be made smaller than the outer diameter of the rolling bearing 104. The range in which 181 acts is appropriately configured, and an appropriate orbiting scroll pressing force can be realized in a wide range of operation.
[0040]
Further, when the overcompression preventing means 138 and 139 are used in combination, the orbiting scroll pressing force at the time of low pressure ratio operation can be reduced. Therefore, the orbiting scroll pressing force required in a wide operating range from the low pressure ratio to the high pressure ratio. It is possible to reduce the width of the orbit, and it is possible to achieve an appropriate orbiting scroll pressing force in a wide range of operation.
[0041]
From the above, the mechanical sliding loss between the orbiting scroll member 120 and the fixed scroll member 110 can be reduced and the energy efficiency can be improved, and the mechanical sliding portion between the orbiting scroll member 120 and the fixed scroll member 110 can be improved. It is possible to suppress excessive pressing and improve reliability.
[0042]
Next, a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment as described below, and is basically the same as the first embodiment in other points.
[0043]
The second embodiment is different from the first embodiment in the configuration of the frame 160, the bearing retainer 203, and the balance weight cover 203. The frame 160 has a portion where the bearing retainer 203 is inserted longer than the first embodiment. The basic configuration in which the rolling bearing 104 is inserted into the frame 160 from the rotational driving means side of the frame 160 and is held by the bearing holder 203 is the same as that of the first embodiment, but the outer diameter of the bearing holder 203 is the outer diameter of the rolling bearing 104. The bearing holder 203 is inserted into the frame 160 to hold the rolling bearing 104. Then, the bearing retainer 203 is fixed by a retaining ring 405 fitted in a groove provided on the inner periphery of the frame 160. As the retaining ring 405, a C-shaped retaining ring or a bevel-type retaining ring is used. By using the retaining ring 405, the bearing holder 203 can be fixed easily and inexpensively.
[0044]
Further, the balance weight cover 203 is fixed to the frame 160 by a bolt 201 alone. The balance weight cover 203 is installed so as to include the coil end portion 108a of the stator 108. As a result, the turbulence of the air flow caused by the rotation operation of the balance weight 109 is first absorbed by the end coil portion 108a of the stator 108, and further absorbed by the balance weight cover 203 so that the turbulence of the air flow does not act reliably in the vicinity of the discharge port 350. It has become. Note that the configuration of the balance weight cover 203 of the second embodiment is effective even when applied to the first embodiment.
[0045]
Next, a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment as described below, and is basically the same as the first embodiment in other points.
[0046]
In the third embodiment, the frame 160 forms an insertion portion for the rolling bearing 104 on the compression chamber side, and also forms an insertion portion for the bearing retainer 600 on the inlet side. The rolling bearing 104 is inserted into the insertion portion of the frame 160 from the compression chamber side, and then the bearing holder 600 is inserted into the insertion portion of the frame 160 from the compression chamber side. The bearing retainer 600 is formed with an inner diameter that is smaller than the outer diameter of the rolling bearing 104 and substantially the same as the inner diameter of the shaft support portion 12e of the orbiting scroll. One end face of the bearing retainer 600 abuts and presses against the end face of the rolling bearing 104, and the other end face faces the shaft support end face 120f of the orbiting scroll with a very small interval. A ring-shaped groove 561 in which the seal ring 572 is disposed is formed on the other end surface of the bearing retainer 600. Then, a sealing single 572 is disposed in the ring-shaped groove 561, and the shaft support portion end surface 120f of the orbiting scroll is used as a sealing surface.
[0047]
Further, the bearing holder 600 is fastened to the frame 160 using bolts 605. Note that the crankshaft side space 602 needs to be highly accurate in order to accumulate a certain amount of oil in the central space 180 and supply the required amount of oil to the outer peripheral space 182, and as a highly accurate positioning means for the bearing retainer 600, A knock pin (not shown) is also used.
[0048]
In the third embodiment, since the bearing retainer 600 as a separate member is inserted into the frame 160 from the compression chamber side, it is necessary to seal the insertion surface (engagement surface) of the bearing retainer 600 and the frame 160. A seal portion is disposed on the outer periphery of the presser 600. The seal material 606 of the seal portion is inserted into the seal material insertion groove formed on the outer peripheral surface of the bearing retainer 600, but the seal material 606 is inserted into the seal material insertion groove formed on the inner peripheral surface of the frame 560. May be. The illustrated sealing material 606 is an O-ring, but may be a sealing ring made of a fluororesin or a polyimide resin.
[0049]
【The invention's effect】
As is clear from the above description of the embodiment, according to the present invention, a rolling bearing is used as the bearing of the crankshaft to improve the bearing reliability, and the turning scroll pressing force to the fixed scroll is optimized, and the turning Scroll compressor capable of improving energy efficiency by reducing mechanical sliding loss in the mechanical sliding portion between the scroll and the fixed scroll, and improving reliability by suppressing excessive pressing of the mechanical sliding portion Can get.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.
2 is a longitudinal sectional view of a main part of the scroll compressor of FIG. 1. FIG.
FIG. 3 is a longitudinal sectional view of an essential part of a scroll compressor according to a second embodiment of the present invention.
FIG. 4 is a longitudinal sectional view of an essential part of a scroll compressor according to a third embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Scroll compressor, 2 ... Compression part, 3 ... Drive part, 100 ... Airtight container, 101 ... Crankshaft, 101a ... Eccentric pin part, 101b ... Main shaft part, 102 ... Oil supply path, 106 ... Oil supply pump, 109 ... balance weight, 110 ... fixed scroll member, 120 ... orbiting scroll member, 120f ... orbiting scroll shaft support portion end face, 130 ... compression chamber, 131 ··· lubricating oil, 134 ... Oldham ring, 135 ... suction space, 136 ... Discharge space, 160 ... frame, 161 ... ring-shaped groove 170, 171 ... small hole, 172 ... seal ring, 180 ... back pressure chamber, 181, 181a, 181b ... central space, 182, 182a, 182b ... outer peripheral space, 183 ... Oil supply path, 184 ... Oil drain pipe, 200 ... Bearing retainer, 201 ... Bolt, 203 ... Balance weight cover, 04 ... the thrust bearing, 605 ... bolt.

Claims

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
A turning shaft support portion for engaging the eccentric pin portion of the crankshaft is provided on the turning scroll member;
Engaging the eccentric pin portion with the orbiting shaft support portion so that an end surface of the eccentric pin portion directly faces the back surface of the orbiting scroll member and forms a part of the central space;
As most of the lubricating oil supplied to the central portion space is returned to the closed bottom of the container through the main shaft support portion opposite to the compression chamber provided with an oil supply means for supplying a lubricating oil to said central portion space To configure
While using a rolling bearing as the spindle support part,
A scroll compressor characterized in that an outer diameter of the central space separated by the sealing material is made smaller than an outer diameter of the rolling bearing.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
A turning shaft support portion for engaging the eccentric pin portion of the crankshaft is provided on the turning scroll member;
Engaging the eccentric pin portion with the orbiting shaft support portion so that an end surface of the eccentric pin portion directly faces the back surface of the orbiting scroll member and forms a part of the central space;
As most of the lubricating oil supplied to the central portion space is returned to the closed bottom of the container through the main shaft support portion opposite to the compression chamber provided with an oil supply means for supplying a lubricating oil to said central portion space To configure
While using a rolling bearing as the spindle support part,
A scroll compressor characterized in that an inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing.

The scroll compressor according to claim 1 or 2, wherein a member for disposing the main shaft support portion is constituted by a frame fixed to the hermetic container, and a rolling bearing insertion portion is provided on the rotation driving means side of the frame, The rolling bearing is inserted into the rolling bearing insertion portion of the frame from the rotational drive means side and mounted, and the orbiting scroll support member that engages the eccentric pin portion of the crankshaft is provided on the orbiting scroll member, and the orbiting shaft support The surface perpendicular to the axial direction, which is the end surface of the portion, is used as one seal surface, the end surface on the compression chamber side of the frame facing the seal surface is used as the other seal surface, and a ring-shaped groove is formed in the other seal surface. And a seal compressor is provided in the ring-shaped groove.

4. The scroll press according to claim 1, wherein the bearing press is formed by a member different from a member for disposing the main shaft support portion and fixed to the member for disposing the main shaft support portion with a bolt. The cylindrical bearing is used as the main shaft support portion and the thrust bearing toward the rotational drive means acting on the inner ring of the cylindrical rolling bearing mounted on the crankshaft is received by the bearing holder. A scroll compressor characterized by that.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates the space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
Lubricating oil stored at the bottom of the sealed container;
An oil supply path for supplying the lubricating oil to the spindle support part,
While using a rolling bearing as the spindle support part,
Forming an inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the main shaft support portion is disposed smaller than an outer diameter of the rolling bearing;
The lubricating oil is supplied to the central space, and most of the lubricating oil supplied to the central space is configured to return to the bottom of the sealed container through the rolling bearing,
The rolling bearing is pressed by a bearing pressing member separate from the member for disposing the spindle support portion, and a part of the lubricating oil path returning to the bottom of the hermetic container is formed on the rolling bearing side of the bearing pressing. Scroll compressor characterized by.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
The rolling bearing is inserted and arranged from the compression chamber side of the member that arranges the rolling bearing,
A scroll compressor characterized in that a separate bearing retainer is disposed from the side of the compression chamber of a member for disposing the rolling bearing so as to retain the rolling bearing.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
A thrust force to said rotary drive means side of the crank shaft is arranged to receive in bearings retainer,
A scroll compressor having a sealing function on a joint surface between the bearing retainer and the member on which the rolling bearing is disposed.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
Hold the rolling bearing with a bearing holder that is a separate member from the member that disposes the spindle support,
A scroll compressor characterized in that a bolt is used for fastening between the bearing retainer and the member on which the rolling bearing is disposed.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
A thrust force to said rotary drive means side of the crank shaft is arranged to receive in bearings retainer,
A scroll compressor characterized in that a bolt is used for fastening between the bearing retainer and the member on which the rolling bearing is disposed.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
Hold the rolling bearing with a bearing holder that is a separate member from the member that disposes the spindle support,
A balance weight cover is disposed on the rotational drive means side of the member for disposing the rolling bearing;
Bolts are used to fasten the bearing holder and the member for disposing the rolling bearing,
The scroll weight compressor, wherein the balance weight cover is fixed to a member on which the rolling bearings are disposed in common with the bolts.

In a scroll compressor provided with a compression section in which a compression chamber is formed by combining a fixed scroll member and an orbiting scroll member, a drive section that drives the compression section, and a sealed container that houses the compression section and the drive section,
A crankshaft connecting the orbiting scroll member and the rotation drive means of the drive unit;
A main shaft support portion for supporting the main shaft portion of the crankshaft on the compression chamber side from the rotation driving means;
A member for disposing the main shaft support;
A sealing material that pressure-separates a space constituting the back side of the orbiting scroll member into a central space that is substantially a discharge pressure and an outer peripheral space that is a pressure lower than the pressure of the central space;
While using a rolling bearing as the spindle support part,
An inner diameter of the sealing material interposed between the orbiting scroll member and a member on which the spindle support portion is disposed is smaller than an outer diameter of the rolling bearing;
A thrust force to said rotary drive means side of the crank shaft is arranged to receive in bearings retainer,
A balance weight cover is disposed on the rotational drive means side of the member for disposing the rolling bearing;
Bolts are used to fasten the bearing holder and the member for disposing the rolling bearing,
The scroll weight compressor, wherein the balance weight cover is fixed to a member on which the rolling bearings are disposed in common with the bolts.