JP4154937B2

JP4154937B2 - Hermetic compressor

Info

Publication number: JP4154937B2
Application number: JP2002197054A
Authority: JP
Inventors: 誠片山; 俊造渡壁; 浩業明石; 昭彦窪田; 崇秀長尾; 康祐坪井; 隆志垣内; 健小島
Original assignee: Panasonic Corp; Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Corp; Panasonic Holdings Corp
Priority date: 2002-07-05
Filing date: 2002-07-05
Publication date: 2008-09-24
Anticipated expiration: 2022-07-05
Also published as: JP2004036562A

Description

【０００１】
【発明の属する技術分野】
本発明は、冷蔵庫、エアーコンディショナー、冷凍冷蔵装置等に用いられる密閉形圧縮機に関するものである。
【０００２】
【従来の技術】
近年、家庭用冷凍冷蔵庫等の冷凍装置に使用される密閉型圧縮機については、消費電力の低減や静音化が強く望まれており、冷凍機油の低粘度化や、インバーター駆動による圧縮機の低回転化（例えば、家庭用冷蔵庫の場合、１２００ｒ／ｍｉｎ程度）が進んできている。一方、使用冷媒としてはオゾン破壊係数がゼロであるＲ１３４ａやＲ６００ａに代表される温暖化係数の低い自然冷媒である炭化水素系冷媒の対応が前提となってきている。また、古くから採用されていたシャフトを主軸受けと副軸受けの２ヵ所で保持する両持ち軸受という方法は、摺動ロスを減らし、また運転時の振動を減らす要素技術として有効である。
【０００３】
両持ち軸受という方法を採用した従来の密閉型圧縮機としては、特開昭６１−１１８５７１号公報に記載されているものがある。
【０００４】
以下、図面を参照しながら、上述した従来の密閉型圧縮機について説明する。
【０００５】
図１３は従来の密閉型圧縮機の縦断面図、図１４は従来の密閉形圧縮機の要部上面図である。図１５及び図１６は従来の密閉形圧縮機の要部断面図である。図１３、図１４において１は密閉容器で、２は密閉容器内空間である。密閉容器１内には、巻線部３ａを保有する固定子３と回転子４からなる電動要素５と、電動要素５によって駆動される圧縮要素６を収容する。８は密閉容器１内に貯溜した潤滑油である。
【０００６】
１０はシャフトで、回転子４を圧入固定した主軸部１１および主軸部１１に対し偏心して形成された偏心部１２に加え、主軸部と同軸に設けられた副軸部１３を有する。主軸部１１の内部には同芯ポンプ１４が設けられ一端が潤滑油８中に開口し他端が縦孔部１５と連通しており、縦孔部１５はシャフト１０の上端面へ連通開口している。１６はシリンダブロックで、略円筒形の圧縮室１７を有するとともに主軸部１１を軸支する主軸受１８を有し、上方に副軸部１３を軸支する副軸受１９が固定されており、副軸受１９にはシャフト１０外周部に設けた窪み部１９ａを設けている。２０はピストンでシリンダブロック１６の圧縮室１７に往復摺動自在に挿入され、偏心部１２との間を連結手段２１によって連結されている。
【０００７】
以上のように構成された密閉型圧縮機について以下その動作を説明する。
【０００８】
電動要素５の回転子４はシャフト１０を回転させ、偏心部１２の回転運動が連結手段２１を介してピストン２０に伝えられることでピストン２０は圧縮室１７内を往復運動する。これにより、冷却システム（図示せず）からの冷媒ガスは圧縮室１７内へ吸入・圧縮された後、再び冷却システムへと吐き出されるといったサイクルを繰返す。
【０００９】
ここで、両持ち軸受けの摺動ロス減のメカニズムに関して説明する。
【００１０】
圧縮機運転中にピストン２０の圧縮荷重が連結手段２１を介して偏心部１２へと伝達される。ここで、両持ち軸受タイプはピストンからの圧縮荷重のかかる偏心部１２（作用点）を中心にして上下両方で荷重を受けるため、軸受けには上下でほぼ均等な荷重が配分され、また、内周でこじりが生ずる片持ち軸受けタイプと異なり面当たりとなるため、シャフト１０摺動部の荷重分布が均等となることで面圧が下がり、片持ちタイプよりも摺動長を短くすることができる。その結果、摺動ロスが減少し、圧縮機の効率向上が図れるといった長所を備える。
【００１１】
次に従来の両持ち軸受タイプの給油メカニズムに関して説明する。
【００１２】
図１５において、シャフト１０の回転により、同芯ポンプ１４内の潤滑油８は遠心力により放物線状Ａ１、Ａ２の自由表面をなしながら上方へと汲み上げられ、支流Ａ１の搬送力により縦孔部１５に流入され、主軸１１、偏心部１２、副軸部１３への各摺動部へと順に潤滑される。また、図１６において、縦孔部１５へ汲み上げられた潤滑油８の内、一方は副軸部１３に設けた連通孔１３ａ及び窪み部１９ａをガイドに密閉容器１へ放散（方向Ｂ）され、一方は縦孔部１５上端から密閉容器１へと放散（方向Ｃ）を行なう。これによって各摺動部から受熱した潤滑油８が密閉容器１によって放熱・冷却できる仕組みとなっている。
【００１３】
【発明が解決しようとする課題】
しかしながら上記従来の構成では、副軸部１３を持たない片持ち軸受タイプの密閉型圧縮機と比べて、副軸部１３を備える分の軸方向長さが必然的に必要となり、それに伴い給油通路も長くなる。その結果、潤滑油を上方向へ搬送する時の流路抵抗の増加と高い揚程による潤滑油自体の重量増加による影響から、副軸部１３の摺動部への給油量が不足し、摺動部での潤滑不良が生じやすかった。
【００１４】
また、圧縮機の起動初期等、潤滑油８と同時に冷媒ガスが給油経路内に混入し易い場合において、上記従来の副軸部１３を持つ給油経路の長い構成では、給油通路内でガス留まりが生じることで給油阻害が発生しやすかった。
【００１５】
また、潤滑油８内で冷媒の溶け込み量が多い場合においては、冷媒から気化するガス量も多くなるため、更にガス留まりによる給油阻害を起こしやすくなる。
【００１６】
また、上記従来の構成では、潤滑油が密閉容器へ放散される量が減ることで、放熱効果が減少し、またピストン２０への給油を副軸部１３から放出する潤滑油に依存しているために、ピストン２０とシリンダ１６間の潤滑油によるシール性が低下して体積効率が低下する他、ピストン２０とシリンダ１６の間での異常な摩耗が発生するといった信頼性低下の問題も発生しやすかった。
【００１７】
特に、電源周波数以下の運転周波数で駆動される密閉型電動機においては、同心ポンプ１４内の潤滑油８に働く遠心力が低下して更に給油阻害が発生し易くなる。
【００１８】
本発明は上記従来の課題を解決するもので、エネルギー効率が高く、且つ信頼性の高い密閉型圧縮機を提供することを目的とする。
【００１９】
【課題を解決するための手段】
本発明の請求項１に記載の発明は、シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設けたことで、傾斜ポンプ部では粘性ポンプ部の下端まで揚程が得られ、更に粘性ポンプで発生した上向きの油圧が縦孔部の揚程をまかない、十分な量の潤滑油を安定して搬送することができるという作用を有する。
【００２０】
さらに、縦孔部が下から上に向けてシャフトの回転方向と反対方向に傾斜したものであり、縦孔部においても上向き搬送力を発生させることができ、さらに十分な量の潤滑油の搬送が可能となるという作用を有する。
【００２１】
請求項２に記載の発明は、請求項１記載の発明に、更に、縦孔部が下から上に向けてシャフトの回転中心軸から遠ざかる方向へ傾斜したものであり、縦孔部においても上向き搬送力を発生させることができ、さらに十分な量の潤滑油の搬送が可能となるという作用を有する。
【００２２】
請求項３に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、絞り部は傾斜ポンプ部内に円板状のキャップを挿入係止したことで、組立時の装着による絞り部が回転軸心に対して振れることを防止できるので安定した給油が確保できると共に、絞り部を設けた円筒部を長手方向に備えた構成と比べて安価な構成でシャフト主軸部の長さを短くできるという作用を有する。
【００２３】
請求項４に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、傾斜通路内に平板状のデバイダーを挿入係止されたことを特徴とするものであり、傾斜ポンプ部内で潤滑油の回転方向のすべりが抑制されることで、特に低速回転域における傾斜ポンプ部内で遠心力が潤滑油に有効に働き、より強い上向き搬送力が発生するという作用を有する。
【００２４】
請求項５に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、傾斜ポンプ部の円筒空洞部から縦孔部の上部開口に至る経路上に軸受部を介さずに密閉容器内空間とを連通する少なくとも1つ以上のガス抜き孔を設けたものであり、給油経路の長い給油機構において圧縮機起動時に混入した冷媒ガスや潤滑油内から気化するガス等を有効に密閉容器内空間へ逃がすことで、給油経路内での潤滑油に発生する上向き搬送力を途切れさせないという作用を有する。
【００２５】
請求項６に記載の発明は、請求項１記載から請求項２のいずれか１項に記載の発明に、更に、シャフトの副軸部において、一端が縦孔部に開口し、他端が副軸受の上部または下部で密閉容器内空間とを連通し、前記シャフトの回転に対して遠心力方向に潤滑油放出横孔を穿設したものであり、潤滑油放出横孔内で潤滑油に遠心力が有効に発生するとともに整流されて放出されることで放出方向が一定となり、密閉容器への飛散が確実にされるといった作用を有する。
【００２６】
請求項７に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、一端が縦孔部に開口し、他端が副軸受内周に開口する副軸給油路を有したものであり、副軸部と副軸受との摺動部に確実に給油をすることで信頼性が向上するという作用を有する。
【００２７】
請求項８に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、一端が縦孔部に開口し、他端が副軸受内周と密閉容器内空間との双方に開口した連通共用孔を設けたものであり、加工工数を減らしたシャフトで副軸への給油とピストン及び密閉容器への放出を同じ孔で行うことが出来るといった作用を有する。
【００２８】
請求項９に記載の発明は、請求項１から請求項２のいずれか１項に記載の発明に、更に、一端がシャフト縦孔部上端と連通し、他端がシャフトの回転に対して遠心力方向に湾曲しながら延出し、密閉容器内空間に開口する潤滑油放出部を備えたものであり、縦孔部の潤滑油を吸引し引き上げることで、粘性ポンプ部の潤滑油にも吸引し引き上げることとなり、潤滑油放出部の開口端が遠心力方向へ潤滑油を放出するため、給油量が増加するといった作用を有する。
【００２９】
請求項１０に記載の発明は、密閉容器内に潤滑油を貯溜するとともに電動要素と前記電動要素によって駆動される圧縮要素を収容し、前記圧縮要素は偏芯軸部と前記偏芯軸部を挟んで上下に同軸状に設けた副軸部および主軸部とを有したシャフトと、略円筒形の圧縮室と前記圧縮室の軸心と略直交するように形成され前記主軸部の上半部を軸支する主軸受とを備えたシリンダブロックと、前記シリンダブロックに固定されるか又は一体に形成され前記副軸部を軸支する副軸受と、前記圧縮室内で往復運動するピストンと、前記ピスト
ンと前記偏芯軸部とを連結する連結手段とを備えており、前記シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設け、さらに前記縦孔部の上端を封止する封止部と、一端が前記縦孔部と連通し、他端が前記シャフトの回転に対して遠心力方向に直線的に延出し前記密閉容器内の空間に開口する潤滑油放出部を備えたものであり、傾斜ポンプ部では粘性ポンプ部の下端まで揚程が得られ、更に粘性ポンプで発生した上向きの油圧が縦孔部の揚程をまかない、十分な量の潤滑油を安定して搬送することができるとともに、縦孔部の潤滑油を吸引し引き上げることで潤滑油放出部の開口端が遠心力方向へ延長しながら潤滑油を放出するため、給油経路内の潤滑油を吸引し引き上げることとなり、給油量を増加するといった作用を有する。
【００３０】
請求項１１に記載の発明は、密閉容器内に潤滑油を貯溜するとともに電動要素と前記電動要素によって駆動される圧縮要素を収容し、前記圧縮要素は偏芯軸部と前記偏芯軸部を挟んで上下に同軸状に設けた副軸部および主軸部とを有したシャフトと、略円筒形の圧縮室と前記圧縮室の軸心と略直交するように形成され前記主軸部の上半部を軸支する主軸受とを備えたシリンダブロックと、前記シリンダブロックに固定されるか又は一体に形成され前記副軸部を軸支する副軸受と、前記圧縮室内で往復運動するピストンと、前記ピストンと前記偏芯軸部とを連結する連結手段とを備えており、前記シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設け、さらに前記副軸部外周において、一端が副軸給油路を介して前記縦孔部と連通し下方に向って前記シャフトの反回転方向に傾斜しながら螺旋状に刻設するとともに下端が前記密閉容器内の空間と連通した副軸リード溝を備えたものであり、傾斜ポンプ部では粘性ポンプ部の下端まで揚程が得られ、更に粘性ポンプで発生した上向きの油圧が縦孔部の揚程をまかない、十分な量の潤滑油を安定して搬送することができ、さらに、副軸摺動部への給油を確実に行うことができるとともに、シャフトの回転により潤滑油の粘性を利用して潤滑油が副軸リード溝から密閉容器内へ放出する際、ピストン及び密閉容器へ飛散することでピストンへの給油と密閉容器からの放熱を兼ねることができるといった作用を有する。
【００３１】
請求項１２に記載の発明は、請求項１から請求項１１のいずれか１項に記載の発明に、更に、少なくとも電源周波数以下の運転周波数を含む複数の運転周波数でインバーター駆動されるものであり、低い運転周波数運転においてシャフトの回転数が低下した場合においても傾斜ポンプから粘性ポンプを経て縦孔部への給油経路を通して各摺動部の潤滑油を供給できるといった作用を有する。
【００３２】
請求項１３に記載の発明は、請求項１２に記載された発明に、更に、電源周波数以下の運転周波数には少なくとも３０Ｈｚ以下の運転周波数を含むものであり、３０Ｈｚ以下の低い運転周波数運転においても摺動部への給油を確保することができるといった作用を有する。
【００３３】
【発明の実施の形態】
以下、本発明による密閉型圧縮機の実施例について、図面を参照しながら説明する。な
お、従来と同一構成については、同一符号を付して詳細な説明を省略する。
【００３４】
（実施の形態１）
図１は、本発明の実施の形態１による密閉型圧縮機の縦断面図、図２は、同実施の形態の密閉型圧縮機のシャフト断面図である。図３は同実施の形態の密閉型圧縮機のシャフト下端部拡大図、図４は同実施の形態の密閉型圧縮機のシャフトの回転数と副軸上端から吐出される給油量の関係を示すグラフである。
【００３５】
図１ないし図３において、１０１は密閉容器で、巻線部１０３ａを保有する固定子１０３と回転子１０４からなる電動要素１０５と、電動要素１０５によって駆動される圧縮要素１０６を収容する。１０８は密閉容器１０１内に貯溜した潤滑油である。電動要素５はインバーター（図示せず）によって３０Ｈｚ以下の運転周波数および６０Ｈｚ以上の運転周波数を含む複数の運転周波数で駆動される。
【００３６】
１１０はシャフトで、主軸部１１１と、主軸部１１１と偏心して設けた偏心部１１２と、偏心部１１２を挟んで主軸部１１１と同軸状に設けた副軸部１１３とから形成される。主軸部１１１は上半部１１１ａと下半部１１１ｂとからなり、下半部１１１ｂには回転子１０４を圧入固定してある。１１６はシリンダブロックで、略円筒形の圧縮室１１７を有するとともに主軸部１１１の上半部１１１ａを軸支する主軸受１１８を有し、上方に副軸部１１３を軸支する副軸受１１９が固定されている。なお、圧縮室１１７は主軸受１１８と副軸受１１９に対して略直角となるように配置されている。
【００３７】
１２０はピストンでシリンダブロック１１６の圧縮室１１７に往復摺動自在に挿入され、偏心部１１２との間を連結手段であるコンロッド１２１によって連結されている。
【００３８】
シャフト主軸部１１１の下半部１１１ｂ内には、下端から軸心ＰＣに対して上方に向かい外側にθ１傾斜した円筒空洞で形成した傾斜ポンプ部１３０が設けられている。傾斜ポンプ部１３０の内部には平板状のデバイダー１３３が圧入固定されている。油中開口端にはシャフト１１０の回転軸心ＲＣに導入孔１３４ａを備えた平板状のキャップからなる絞り部１３４が圧入固定されている。
【００３９】
絞り部１３４はばね性を有する材料からなり、ばね性を利用してシャフト１１０内に埋設し、容易に組み込むことができるとともに、他の部品と干渉してずれたりすることのない構成となっている。
【００４０】
シャフト主軸部１１１の上半部１１１ａには、外周に、下端が傾斜ポンプ部１３０の上端近傍と連通し、上方に向かってシャフト１１０の反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部１３１が形成されている。
【００４１】
さらにシャフト１１０の偏芯部１１２から副軸部１１３にかけて、一端が前記粘性ポンプ部１３０上端近傍と連通し、他端が副軸部１１３の上端面近傍に連通開口した縦孔部１３２を設けてある。
【００４２】
縦孔部１３２には、偏心部１１２摺動部への連通孔１１２ａと副軸受１１９内周に開口する副軸給油路１１３ａをそれぞれ備えている。
【００４３】
１３７ａは傾斜ポンプ部１３０上端と密閉容器１０１内の空間１０２とを連通するガス抜き孔、１３７ｃは傾斜ポンプ部１３０中間と密閉容器１０１内の空間１０２とを連通するガス抜き孔、１３７ｂは縦孔部１３２と密閉容器１内の空間１０２とを連通するガス抜き孔である。
【００４４】
尚、本圧縮機に使用される冷媒は、例えばオゾン破壊係数がゼロのＲ１３４ａやＲ６００ａに代表される温暖化係数の低い自然冷媒である炭化水素系冷媒であり、それぞれ相溶性のある潤滑油と組み合わせてある。
【００４５】
以上のように構成された密閉型圧縮機について、以下にその動作を説明する。
【００４６】
電動要素１０５の回転子１０４はシャフト１１０を回転させ、偏心部１１２の回転運動が連結手段１２１を介してピストン１２０に伝えられることでピストン１２０は圧縮室１１７内を往復運動する。この時、シャフト１１０の回転により傾斜ポンプ部１３０内の潤滑油１０８もシャフト１１０と共に回転し、潤滑油１０８には遠心力が作用する。この際、デバイダー１３３は傾斜ポンプ部１３０内での潤滑油１０８の回転方向の滑りを防ぐため、潤滑油はシャフト１１０の回転速度と同じ速さで回転するため、遠心力が有効に発生、作用する。導入孔１３４ａより流入する潤滑油１０８は傾斜ポンプ部１３０内で遠心力方向へ作用力を受け、傾斜ポンプ部１３０の中で上方向Ａと下方向Ｂへ分流するが、下方向Ｂへと押圧された潤滑油１０８は、絞り部１３４によって移動できず、上方向Ｃへの潤滑油の搬送力が主体に発生する。また、傾斜ポンプ部１３０は上方に向かって遠心力方向へ角度θ１傾斜していることから、遠心力が作用する潤滑油１０８は揚力を得て傾斜ポンプ部１３０内を斜め方向に這い上がり、上方向への搬送がなされる。従って、従来例に示した同芯ポンプのように潤滑油１０８が遠心力方向に対して直角上向に搬送するだけの形式と比べて遥かに高い揚程が得られる。
【００４７】
次に、傾斜ポンプ部１３０の上部に至った潤滑油１０８は、粘性ポンプ部１３１へと導入される。粘性ポンプ部１３１のリード溝はシャフト回転方向と逆向きに働く慣性力と同方向に傾斜していることから、潤滑油には新たに上方向への搬送力が働くことになる。これは、従来例で示した上方向の推進力を持たない主軸部１１内の縦孔部１５に較べて遥かに大きな上方向の推進力を得ることができる。粘性ポンプ部１３１上端に至った潤滑油１０８は縦孔部１３２へと導入される。縦孔部１３２内の潤滑油１０８は粘性ポンプ部１３１の上方向の推進力により押上げられ、シャフト１１０上端での開口から潤滑油１０８は放出される。その結果シャフト１１０の各摺動部で最も高い位置に有る副軸部１１３へ給油される。
【００４８】
ところで両持ち軸受タイプの密閉形圧縮機は副軸部１１３を持つ分、シャフト１１０の下部ポンプ部からシャフト１１０上端までの給油経路が片持ちタイプと比べて構造的に延長される。そこで、圧縮機の起動時直後にけるシャフトの給油経路を通過する潤滑油１０８の挙動は、シャフトの回転による攪拌と密閉容器１０１内の減圧により潤滑油中に溶解した冷媒の発泡、気化により傾斜ポンプ部１３０内や粘性ポンプ１３１内にガスが押し留められ易くなり、いわゆるガス噛みによる給油阻害が生じる可能性が高くなる。
【００４９】
しかしながら、この時、傾斜ポンプ部１３０内の発泡等による冷媒ガスにおいてはガス抜き孔１３７ａと１３７ｃからガス抜きを促し、更に粘性ポンプ部１３１や縦孔部１３２で生じた冷媒ガスに関してはガス抜き孔１３７ｂによってそれぞれガス抜きを促すことから、ガス噛みを回避し給油経路が潤滑油で満たされるので、粘性ポンプでの潤滑油の揚力を得ることができ給油不良を防ぐことができる。
【００５０】
本実施の形態によれば、図４に示すように、従来の同芯ポンプ１４を組み合せたタイプではほとんど給油できない、２０ｒ／ｓといった低速域での運転においても確実に、しかも十分な給油量を得ることができることが判明した。また、潤滑油内への冷媒の溶け込み量が多い為、ガス留まりによる給油阻害を起こしやすいＲ６００aやＲ２９０と鉱油の組み合せ、またＲ１３４ａとエステル油の組み合わせにおいても確実に、しかも十分な給油
量を得ることができた。また、上記のような潤滑油内への冷媒の溶け込み量が多い潤滑油と冷媒の組み合わせに加えて潤滑性の低下する粘度８〜１０［ｃｔｓ］といった低粘度の潤滑油を使用した運転においても確実に、しかも十分な給油量を得ることができた。したがって従来の同芯ポンプ１４を組み合せたタイプでは困難な、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、冷凍システムの飛躍的な消費電力低減を図ることができるのである。
（実施の形態２）
図５は本発明の実施の形態２による密閉型圧縮機のシャフト断面図である。図６は同実施の形態における密閉型圧縮機のシャフト上面図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じである。
【００５１】
図５、６において、シャフト１１０は主軸部１１１、偏心部１１２を挟んだ副軸部１１３からなり、主軸部１１１は上半部１１１ａと下半部１１１ｂを有し、下半部１１１ｂ内にはデバイダー１３３、絞り部１３４を備えた傾斜ポンプ部１３０が設けられ、上半部には粘性ポンプ１３１が形成されている。縦孔部１３５は粘性ポンプ部１３０上端近傍と下部１３５ａで連通し、上部１３５ｂでシャフト１１０上端より密閉容器１０１内へ通じている。また、縦孔部１３５には偏心部１１２の摺動部への連通孔１１２ａと副軸部１１３の摺動部への副軸給油路１１３ａをそれぞれ備えている。さらに、縦孔部１３５はシャフト上端に向って遠心力方向へθ２傾斜している。シャフト１１０は下端より傾斜ポンプ部１３０、粘性ポンプ１３１、縦孔部１３５により上端につながる給油経路が形成されている。
【００５２】
以上のように構成された密閉型圧縮機について以下その動作を説明する。したがって、シャフト１１０の回転によって縦孔部１３５の潤滑油は遠心力による上方向推進力を得る事ができ、遠心力に対して直角に立ち上がった縦孔部１３２に較べ、さらに大きな上方向の推進力を得ることができる。その結果、密閉容器への潤滑油の放散量が増加し、放熱性が向上し、また、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、密閉型圧縮機の信頼性が向上する。
（実施の形態３）
図７は本発明の実施の形態３による密閉型圧縮機のシャフト上面図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じであり、シャフトの基本構成は図２又は図５と同じである。
【００５３】
図７において、縦孔部１３６は粘性ポンプ部１３０上端近傍と下部１３６ａで連通し、上部１３６ｂでシャフト１１０上端より密閉容器１０１内へ通じている。さらに、縦孔部１３６はシャフト１１０回転方向と逆向きに働く慣性力と同方向に傾斜している。
【００５４】
以上のような構成による密閉型圧縮機の動作について説明する。シャフト１１０の回転によって粘性ポンプ上端まで汲み上げられた潤滑油１０８は縦孔部１３６の傾斜により上方向への搬送力が働く。その結果、密閉容器への潤滑油の放散量が増加し、放熱性が向上し、また、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、冷凍システムの飛躍的な消費電力低減を図ることができ、また密閉型圧縮機の信頼性が向上する。
縦孔部がシャフト上端に向って遠心力方向へ傾斜し、かつシャフト１１０の反回転方向に傾斜した組み合わせにおいては、相乗効果で更に潤滑油には上方向への搬送力が強く働くこととなる。
【００５５】
（実施の形態４）
図８は、本発明の実施の形態４による密閉型圧縮機のシャフト要部断面図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じであり、シャフトの基本構成は図２又は図５と同じである。
【００５６】
図８において、１３８は、縦孔部１３２と密閉容器１０１内とを連通する潤滑油放出横孔であり、副軸部１１３の上方に設けられている。
【００５７】
以上のような構成による密閉型圧縮機の動作について説明する。まずシャフト１１０の回転によって縦孔部１３２まで搬送された潤滑油１０８は、副軸部１１３の摺動部へと副軸給油路１１３ａを介して給油した後、そこで余った潤滑油が潤滑油放出横孔１３８から密閉容器１０１へと放出される。
【００５８】
この時、従来例で示した構成では、副軸受１９の壁面を伝って密閉容器１への潤滑油放散を行う事を特徴としているために、副軸部１９を持つ給油経路の長い構成においては、縦孔部１５からの給油量も減少することから、シャフト１０上端から潤滑油を放散する勢いが減少し、副軸受１９壁面の表面張力によって密閉容器まで放散できないといった状態が生じる可能性がある。
【００５９】
しかしながら、このような給油経路の長い場合でも、潤滑油放出横孔１３８が放出される潤滑油を整流する効果を発揮し、一ヵ所から分散されないように遠心力方向へと放散（支流Ｄ）できるので、副軸受１１９部壁面への表面張力によって放出潤滑油が分散される事もなく、確実に潤滑油を密閉容器へと放散することができる。従って、潤滑油の冷却が促されて信頼性向上を図る事ができ、また、低周波数運転時のような遠心力が小さく潤滑油の振り出し力が低下している場合においても、潤滑油を密閉容器１０１へと放散できる。
【００６０】
次に、図９は同実施の形態による密閉型圧縮機の他の例によるシャフトの要部断面図である。
【００６１】
図９において、１３９は連通共用孔でシャフトの回転に対して遠心力方向に穿設しており、一端が縦孔部１３２と連通し、他端が副軸受１１９内周と密閉容器１０１内空間との双方に開口している。
【００６２】
シャフト１１０の回転によって縦孔部まで搬送された潤滑油１０８は、連通共用孔１３９を通り、一部は副軸受１１９内周に給油され副軸受１１９と副軸部１１３との摺動部を潤滑し、一部が支流Ｅとして密閉容器１０１内雰囲気に開放されることで潤滑油冷却を行うと共に、ピストン１２０への潤滑によるピストン１２０、シリンダ１１６間との潤滑油シール性の向上による体積効率の向上が図れる。従って、一つの孔で副軸部の潤滑と潤滑油の潤滑油冷却及びピストン１２０摺動部への潤滑油跳ね掛けの共用化が図れるため、加工点数増によるコストアップも回避できるといった、低コストを達成しつつ高効率・高信頼性の圧縮機を提供する事ができる。
【００６３】
（実施の形態５）
図１０は本発明の実施の形態５による密閉型圧縮機のシャフトの要部断面図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じであり、シャフトの基本構成は図２又は図５と同じである。
【００６４】
図１０において、１４０は潤滑油放出部で湾曲させたチューブで形成され、一端が縦孔部１３２上端に圧入開口し、他端はシャフト１１０の回転による遠心力方向に密閉容器１０１内へ延出開口している。
【００６５】
以上のような構成による密閉型圧縮機の動作について説明する。シャフト１１０の回転によって傾斜ポンプ部１３０から縦孔部まで搬送された潤滑油１０８は、潤滑油放出部１４０の遠心力方向へ延出した部分で遠心力が働き、潤滑油を吸引する作用が働く。
【００６６】
この作用によって縦孔部１３２の潤滑油が潤滑油放出部１４０に吸引され、上方向へ引き上げられることで滞溜していた粘性ポンプ部１３２のガスも同時に引き出されるといった効果を持つ。従って、両持ち軸受タイプといった給油経路の長い物でもガス噛みを防止することができ、片持ちタイプと同等の安定した給油特性を確保できる。また、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、冷凍システムの飛躍的な消費電力低減を図ることができ、また密閉型圧縮機の信頼性が向上する。
【００６７】
（実施の形態６）
図１１は実施の形態６による密閉型圧縮機のシャフトの断面図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じであり、シャフトの基本構成は図２又は図５と同じである。
【００６８】
図１１において、１４１は潤滑油放出部で潤滑油放出横孔に圧入し、シャフト１１０の回転による遠心力方向に密閉容器１０１内へ延出開口している。１４１ａは縦孔部１３２上端の封止部でキャップ状の金属プレス部品で形成される。
【００６９】
以上のような構成において、シャフト１１０の回転によって縦孔部まで搬送された潤滑油１０８は、潤滑油放出部１４１へと搬送される。搬送された潤滑油１０８には、潤滑油放出部１４１が遠心力方向へ延出しているため、遠心力が働き潤滑油を吸引する。
【００７０】
この作用によって縦孔部１３２の潤滑油が潤滑油放出部１４１に吸引され、上方向へ引き上げられることで滞溜していた粘性ポンプ部１３２のガスも同時に引き出されるといった効果を持つ。従って、両持ち軸受タイプといった給油経路の長い物でもガス噛みを防止することができ、片持ちタイプと同等の安定した給油特性を確保できる。また、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、冷凍システムの飛躍的な消費電力低減を図ることができ、また密閉型圧縮機の信頼性が向上する。
【００７１】
本構成は、さらに潤滑油放出部が直管といった比較的加工の少ない安価な部品で構成できるため、コスト低減が図れる。
【００７２】
（実施の形態７）
図１２は実施の形態７による密閉型圧縮機のシャフト副軸部の詳細図である。なお、本実施の形態における密閉型圧縮機の基本構成は図１と同じであり、シャフトの基本構成は図２又は図５と同じである。
【００７３】
図１２において、１４２は副軸リード溝で副軸部１１３の外周に刻設され、副軸給油路１１３ａと連通し、副軸部１１３下部に副軸部密閉容器１０１内空間へ開口する開口端１４２ａを有する。リード溝１４２は副軸給油路１１３ａを起点に下方に向かってシャフト１１０の反回転方向に傾斜し、螺旋形状を持つ。
【００７４】
以上のような構成において、シャフト１１０の回転によって縦孔部１３２まで搬送された潤滑油１０８は、まず副軸部１１３の給油路１１３ａへと搬送され、次にリード溝１４２へと送り込まれる。この時リード溝部１４２がシャフト１１０回転方向に対して上向き
の角度を持つことから、潤滑油１０８はリード溝１４２を伝って下方向へと押し出され、密閉容器１０１との連通端１４２ａから支流Ｇに示した如く、密閉容器１０１内へ放出され、放熱とともにピストン１２０への給油を司る。したがってリード溝部１４２の回転に伴い副軸部１１３摺動部全周に亘って潤滑することができ、より副軸部１１３の摺動部の信頼性が向上するとともに低速回転運転時においても、良好な放熱が得られ、またピストン１２０摺動部の潤滑がより確実に行われることで信頼性の高い密閉型圧縮機を得ることができる。また、潤滑油に溶け込みやすい冷媒で低粘度の潤滑油を用いたものや、より低速域における運転が可能となる低い周端数運転における給油もより安定するため、冷凍システムの飛躍的な消費電力低減を図ることができ、また密閉型圧縮機の信頼性が向上する。
【００７５】
【発明の効果】
以上説明したように本発明の請求項１に記載の発明は、シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設けたことで、傾斜ポンプ部では粘性ポンプ部の下端まで揚程が得られ、更に粘性ポンプで発生した上向きの油圧が縦孔部の揚程をまかない、十分な量の潤滑油を安定して搬送することができる。
【００７６】
また請求項２に記載の発明は、請求項１記載の発明に、更に、縦孔部が下から上に向けてシャフトの回転中心軸から遠ざかる方向へ傾斜したものであり、縦孔部においても上向き搬送力を発生させることができ、さらに十分な量の潤滑油の搬送が可能となる。
【００７７】
請求項３に記載の発明は、請求項１記載の発明に、更に、縦孔部が下から上に向けてシャフトの回転方向と反対方向に傾斜したものであり、縦孔部においても上向き搬送力を発生させることができ、さらに十分な量の潤滑油の搬送が可能となる。
【００７８】
請求項４に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、絞り部は傾斜ポンプ部内に円板状のキャップを挿入係止したことで、組立時の装着による絞り部が回転軸心に対して振れることを防止できるので安定した給油が確保できると共に、絞り部を設けた円筒部を長手方向に加えなくた構成と比べて安価な構成でシャフト主軸部の長さを短くできる。
【００７９】
請求項５に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、傾斜通路内に平板状のデバイダーを挿入係止されたことを特徴とするものであり、傾斜ポンプ部内で潤滑油の回転方向のすべりが抑制されることで、特に低速回転域における傾斜ポンプ部内で遠心力が潤滑油に有効に働き、より強い上向き搬送力が発生する。
【００８０】
請求項６に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、傾斜ポンプ部の円筒空洞部から縦孔部の上部開口に至る経路上に軸受部を介さずに密閉容器内空間とを連通する少なくとも1つ以上のガス抜き孔
を設けたものであり、給油経路の長い給油機構において圧縮機起動時に混入した冷媒ガスや潤滑油内から気化するガス等を有効に密閉容器内空間へ逃がすことで、給油経路内での潤滑油に発生する上向き搬送力を途切れさせない。
【００８１】
請求項７に記載の発明は、請求項１記載から請求項３のいずれか１項に記載の発明に、更に、シャフトの副軸部において、一端が縦孔部に開口し、他端が副軸受の上部または下
部で密閉容器内空間とを連通し、前記シャフトの回転に対して遠心力方向に潤滑油放出横孔を穿設したものであり、潤滑油放出横孔内で潤滑油に遠心力が有効に発生するとともに整流されて放出されることで放出方向が一定となり、密閉容器への飛散が確実にされる。
【００８２】
請求項８に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、一端が縦孔部に開口し、他端が副軸受内周に開口する副軸給油路を有したものであり、副軸部と副軸受との摺動部に確実に給油をすることで信頼性が向上する。
【００８３】
請求項９に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、一端が縦孔部に開口し、他端が副軸受内周と密閉容器内空間との双方に開口した連通共用孔を設けたものであり、加工工数を減らしたシャフトで副軸への給油とピストン及び密閉容器への放出を同じ孔で行うことが出来る。
【００８４】
請求項１０に記載の発明は、請求項１から請求項３記載のいずれか１項に記載の発明に、更に、一端がシャフト縦孔部上端と連通し、他端がシャフトの回転に対して遠心力方向に湾曲しながら延出し、密閉容器内空間に開口する潤滑油放出部を備えたものであり、縦孔部の潤滑油を吸引し引き上げることで、粘性ポンプ部の潤滑油にも吸引し引き上げることとなり、潤滑油放出部の開口端が遠心力方向へ潤滑油を放出するため、給油量が増加する。
【００８５】
請求項１１に記載の発明は、請求項１から請求項３のいずれか１項に記載の発明に、更に、シャフト縦孔部の上端を封止する封止部と、一端がシャフト縦孔部と連通し、他端がシャフトの回転に対して遠心力方向に直線的に延出し密閉容器内空間に開口する潤滑油放出部を備えたものであり、縦孔部の潤滑油を吸引し引き上げることで潤滑油放出部の開口端が遠心力方向へ延長しながら潤滑油を放出するため、給油経路内の潤滑油を吸引し引き上げることとなり、給油量を増加する。
【００８６】
請求項１２に記載の発明は、請求項１から請求項３のいずれか１項に記載の発明に、更に、シャフト副軸部外周で、一端が副軸給油路と連通し他端が密閉容器内空間に開口した螺旋状の副軸リード溝を設けたものであり、副軸摺動部への給油を確実に行うことができるとともに、シャフトの回転により潤滑油の粘性を利用して潤滑油が副軸リード溝から密閉容器内へ放出する際、ピストン及び密閉容器へ飛散することでピストンへの給油と密閉容器からの放熱を兼ねることができる。
【００８７】
請求項１３に記載の発明は、請求項１から請求項１２のいずれか１項に記載の発明に、更に、少なくとも電源周波数以下の運転周波数を含む複数の運転周波数でインバーター駆動されるものであり、低い運転周波数運転においてシャフトの回転数が低下した場合においても傾斜ポンプから粘性ポンプを経て縦孔部への給油経路を通して各摺動部の潤滑油を供給できる。
【００８８】
請求項１４に記載の発明は、請求項１３に記載された発明に、更に、電源周波数以下の運転周波数には少なくとも３０Ｈｚ以下の運転周波数を含むものであり、３０Ｈｚ以下の低い運転周波数運転においても摺動部への給油を確保することができる。
【図面の簡単な説明】
【図１】本発明による実施の形態１の密閉型圧縮機の縦断面図
【図２】同実施の形態の密閉型圧縮機のシャフト側面図
【図３】同実施の形態の密閉型圧縮機のシャフト下端部拡大図
【図４】同実施の形態の密閉型圧縮機の給油特性を示す特性図
【図５】本発明による実施の形態２の密閉型圧縮機のシャフト断面図
【図６】同実施の形態の密閉型圧縮機のシャフト上面図
【図７】本発明による実施の形態３の密閉型圧縮機のシャフト上面図
【図８】本発明による実施の形態４の密閉型圧縮機のシャフト要部断面図
【図９】同実施の形態による密閉型圧縮機のシャフト要部断面図
【図１０】本発明による実施の形態５の密閉型圧縮機のシャフト要部断面図
【図１１】本発明による実施の形態６の密閉型圧縮機のシャフト要部断面図
【図１２】本発明による実施の形態７の密閉型圧縮機のシャフト副軸部詳細図
【図１３】従来の密閉型圧縮機の縦断面図
【図１４】従来の密閉型圧縮機の上面図
【図１５】従来の密閉型圧縮機のシャフト下部断面図
【図１６】従来の密閉型圧縮機のシャフト副軸要部断面図
【符号の説明】
１０１密閉容器
１０５電動要素
１０６圧縮要素
１０８潤滑油
１１０シャフト
１１１主軸部
１１２偏芯軸部
１１３副軸部
１１３ａ副軸給油路
１１６シリンダブロック
１１７圧縮機
１１８主軸受
１１９副軸受
１２０ピストン
１２１連結手段
１３０傾斜ポンプ部
１３１粘性ポンプ部
１３２縦孔部
１３５縦孔部
１３６縦孔部
１３７ａガス抜き孔
１３７ｂガス抜き孔
１３７ｃガス抜き孔
１３８潤滑油放出横孔
１３９連通共用孔
１４０潤滑油放出部
１４１潤滑油放出部
１４１ａ封止部
１４２副軸リード溝[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a hermetic compressor used in a refrigerator, an air conditioner, a freezer / refrigerator, and the like.
[0002]
[Prior art]
  In recent years, with regard to hermetic compressors used in refrigeration equipment such as household refrigerator-freezers, reduction of power consumption and noise reduction have been strongly desired.inverterThe rotation of the compressor by driving (for example, about 1200 r / min in the case of a household refrigerator) has been advanced. On the other hand, it is assumed that the refrigerant used is a hydrocarbon refrigerant which is a natural refrigerant having a low global warming coefficient represented by R134a and R600a having an ozone depletion coefficient of zero. In addition, the dual-supported bearing method, in which the shaft, which has been used for a long time, is held at two locations, the main bearing and the sub-bearing, is effective as an elemental technology that reduces sliding loss and reduces vibration during operation.
[0003]
  As a conventional hermetic compressor adopting a method called a double-end bearing, there is one described in Japanese Patent Application Laid-Open No. 61-118571.
[0004]
  Hereinafter, the above-described conventional hermetic compressor will be described with reference to the drawings.
[0005]
  FIG. 13 is a longitudinal sectional view of a conventional hermetic compressor, and FIG. 14 is a top view of the main part of the conventional hermetic compressor. 15 and 16 are cross-sectional views of main parts of a conventional hermetic compressor. In FIGS. 13 and 14, 1 is a sealed container, and 2 is a space in the sealed container. The hermetic container 1 accommodates an electric element 5 including a stator 3 and a rotor 4 having a winding part 3 a and a compression element 6 driven by the electric element 5. Reference numeral 8 denotes lubricating oil stored in the sealed container 1.
[0006]
  Reference numeral 10 denotes a shaft, which includes a main shaft portion 11 into which the rotor 4 is press-fitted and fixed, an eccentric portion 12 formed eccentrically with respect to the main shaft portion 11, and a sub shaft portion 13 provided coaxially with the main shaft portion. A concentric pump 14 is provided inside the main shaft portion 11, one end is opened in the lubricating oil 8, and the other end communicates with the vertical hole portion 15. The vertical hole portion 15 communicates and opens to the upper end surface of the shaft 10. ing. 16 isCylinder blockThe main bearing 18 has a substantially cylindrical compression chamber 17 and supports the main shaft 11, and a sub-bearing 19 that supports the sub-shaft 13 is fixed above the sub-bearing 19. A hollow portion 19a provided on the outer peripheral portion of the shaft 10 is provided. 20 is a pistonCylinder blockIt is inserted into the 16 compression chambers 17 so as to be slidable back and forth, and is connected to the eccentric portion 12 by the connecting means 21.
[0007]
  The operation of the hermetic compressor configured as described above will be described below.
[0008]
  The rotor 4 of the electric element 5 rotates the shaft 10, and the rotational movement of the eccentric portion 12 is transmitted to the piston 20 via the connecting means 21, so that the piston 20 reciprocates in the compression chamber 17. Thereby, the refrigerant gas from the cooling system (not shown) is repeatedly sucked and compressed into the compression chamber 17 and then discharged again to the cooling system.
[0009]
  Here, the mechanism for reducing the sliding loss of the double-end bearing will be described.
[0010]
  During the operation of the compressor, the compression load of the piston 20 is transmitted to the eccentric portion 12 via the connecting means 21. Here, since the double-end bearing type receives the load in both the upper and lower directions centering on the eccentric portion 12 (operation point) to which the compressive load from the piston is applied, a substantially equal load is distributed to the bearing in the upper and lower directions. Unlike the cantilevered bearing type, which causes a twist in the circumference, the load distribution of the sliding portion of the shaft 10 becomes uniform, the surface pressure decreases, and the sliding length can be shortened compared to the cantilevered type. . As a result, the sliding loss is reduced and the compressor can be improved in efficiency.
[0011]
  Next, a conventional oil-feeding mechanism of a double-sided bearing type will be described.
[0012]
  In FIG. 15, the rotation of the shaft 10 causes the lubricating oil 8 in the concentric pump 14 to be pumped upward while forming free surfaces of the parabolic shapes A1 and A2 by centrifugal force, and the vertical hole portion 15 by the conveying force of the tributary A1. To the main shaft 11, the eccentric portion 12, and the sliding portions to the auxiliary shaft portion 13 are lubricated in order. Further, in FIG. 16, one of the lubricating oil 8 pumped up to the vertical hole portion 15 is diffused (direction B) to the sealed container 1 using the communication hole 13a and the recessed portion 19a provided in the auxiliary shaft portion 13 as a guide, One side diffuses (direction C) from the upper end of the vertical hole portion 15 to the sealed container 1. As a result, the lubricating oil 8 received from each sliding portion can be radiated and cooled by the sealed container 1.
[0013]
[Problems to be solved by the invention]
    However, in the above-described conventional configuration, an axial length corresponding to the auxiliary shaft portion 13 is inevitably required as compared with a cantilever bearing type hermetic compressor without the auxiliary shaft portion 13, and accordingly, an oil supply passage is provided. Also gets longer. As a result, the amount of oil supplied to the sliding portion of the sub-shaft portion 13 is insufficient due to the increase in flow resistance when the lubricating oil is conveyed upward and the increase in the weight of the lubricating oil itself due to the high head. Lubrication failure was likely to occur in the part.
[0014]
  Further, when the refrigerant gas is likely to be mixed into the oil supply path simultaneously with the lubricating oil 8 such as at the initial start of the compressor, in the long structure of the conventional oil supply path having the countershaft portion 13, the gas stay is in the oil supply path. Occurrence of refueling was likely to occur.
[0015]
  In addition, when the amount of refrigerant dissolved in the lubricating oil 8 is large, the amount of gas vaporized from the refrigerant also increases, which makes it more likely that oil supply is hindered due to gas retention.
[0016]
  Moreover, in the said conventional structure, the quantity of lubricating oil dissipated to an airtight container reduces, and a heat dissipation effect reduces, and it depends on the lubricating oil which discharge | releases the oil supply to piston 20 from the countershaft part 13. For this reason, the sealing performance by the lubricating oil between the piston 20 and the cylinder 16 is deteriorated and the volume efficiency is lowered, and there is a problem in that the reliability is lowered such that abnormal wear occurs between the piston 20 and the cylinder 16. It was easy.
[0017]
  In particular, in a hermetic motor driven at an operating frequency that is lower than the power supply frequency, the centrifugal force acting on the lubricating oil 8 in the concentric pump 14 is reduced, and oil supply inhibition is more likely to occur.
[0018]
  The present invention solves the above-described conventional problems, and an object thereof is to provide a hermetic compressor having high energy efficiency and high reliability.
[0019]
[Means for Solving the Problems]
  According to a first aspect of the present invention, the shaft has a throttle portion communicating with the lubricating oil at the lower half portion of the main shaft portion at the lower end, and an axial center from the lower end of the main shaft portion toward the outer periphery. An inclined pump portion formed by an inclined cylindrical cavity is provided, and the lower end communicates with the vicinity of the upper end of the inclined pump portion on the outer periphery of the upper half portion of the main shaft portion, while being inclined upward in the counter-rotating direction of the shaft. Provided with a viscous pump part engraved in a spiral shape, one end communicates with the vicinity of the upper end of the viscous pump part from the eccentric shaft part to the auxiliary shaft part, and the other end communicates with the vicinity of the upper end surface of the auxiliary shaft part In the inclined pump section, a sufficient amount of lubricating oil can be obtained so that the lift is obtained up to the lower end of the viscous pump section, and the upward hydraulic pressure generated by the viscous pump does not cover the lift of the vertical hole section. That can be transported stably Having.
[0020]
  Furthermore, the vertical hole portion is inclined in the direction opposite to the rotation direction of the shaft from the bottom to the top, and an upward conveying force can be generated even in the vertical hole portion, and a sufficient amount of lubricating oil is conveyed. Has the effect of becoming possible.
[0021]
  The invention according to claim 2 is the same as that according to claim 1, wherein the vertical hole portion is further inclined from the bottom toward the top and away from the rotation center axis of the shaft, and the vertical hole portion also faces upward. A conveying force can be generated, and a sufficient amount of lubricating oil can be conveyed.
[0022]
  Claim 3The invention according to claim 1 is fromClaim 2In addition, in the invention described in any one of the above, the throttle portion is inserted and locked with a disc-shaped cap in the inclined pump portion, so that the throttle portion due to mounting during assembly swings with respect to the rotation axis. Therefore, stable oil supply can be ensured, and the length of the shaft main shaft portion can be shortened with an inexpensive configuration as compared with the configuration in which the cylindrical portion provided with the throttle portion is provided in the longitudinal direction.
[0023]
  Claim 4The invention according to claim 1 is fromClaim 2In the invention described in any one of the above, a flat divider is inserted and locked in the inclined passage, and slippage in the rotational direction of the lubricating oil is suppressed in the inclined pump portion. Thus, the centrifugal force effectively acts on the lubricating oil in the inclined pump portion particularly in the low speed rotation region, and has a function of generating a stronger upward conveying force.
[0024]
  Claim 5The invention according to claim 1 is fromClaim 2In addition to the invention described in any one of the above, at least one or more communicating with the space in the sealed container on the path from the cylindrical cavity portion of the inclined pump portion to the upper opening of the vertical hole portion without a bearing portion In the oil supply mechanism with a long oil supply path, the refrigerant gas mixed at the start of the compressor and the gas vaporized from the lubricating oil are effectively released to the space inside the sealed container. It has the effect | action which does not interrupt the upward conveyance force which generate | occur | produces in the lubricating oil in.
[0025]
  Claim 6The invention according to claim 1 starts from claim 1.Claim 2In addition to the invention according to any one of the above,Secondary shaft, One end opened to the vertical hole portion, the other end communicated with the space inside the sealed container at the upper or lower portion of the auxiliary bearing, and a lubricating oil discharge lateral hole was drilled in the centrifugal force direction with respect to the rotation of the shaft It has the effect that centrifugal force is effectively generated in the lubricating oil in the lubricating oil discharge lateral hole, and the discharge direction is made constant by being rectified and discharged, and scattering to the sealed container is ensured. .
[0026]
  Claim 7The invention according to claim 1 is fromClaim 2The invention according to any one of the above, further comprising a countershaft oil supply passage having one end opened in the vertical hole portion and the other end opened in the inner periphery of the subbearing. It has the effect that reliability is improved by reliably supplying oil to the sliding portion.
[0027]
  Claim 8The invention according to claim 1 is fromClaim 2In the invention described in any one of the above, a communication common hole having one end opened in the vertical hole portion and the other end opened in both the inner circumference of the auxiliary bearing and the space in the sealed container is provided. The shaft with a reduced processing man-hour has the effect that oil supply to the secondary shaft and discharge to the piston and sealed container can be performed through the same hole.
[0028]
  Claim 9The invention according to claim 1 is fromClaim 2In the invention described in any one of the above, one end communicates with the upper end of the shaft vertical hole, and the other end extends while curving in the direction of the centrifugal force with respect to the rotation of the shaft, and opens into the space inside the sealed container. It is equipped with a lubricating oil discharge part, and by sucking and pulling up the lubricating oil in the vertical hole part, it will also suck up and pull up the lubricating oil in the viscous pump part, and the opening end of the lubricating oil discharge part will move in the direction of centrifugal force Since the lubricating oil is released, the amount of oil supply is increased.
[0029]
  Claim 10The invention described inLubricating oil is stored in a sealed container and an electric element and a compression element driven by the electric element are accommodated, and the compression element is provided coaxially up and down with an eccentric shaft portion and the eccentric shaft portion interposed therebetween. A shaft having a sub-shaft portion and a main shaft portion; a substantially cylindrical compression chamber; and a main bearing that is formed so as to be substantially orthogonal to the axial center of the compression chamber and supports the upper half of the main shaft portion. A cylinder block, a sub-bearing fixed to or integrated with the cylinder block and supporting the sub-shaft, a piston reciprocating in the compression chamber, and the piston
And a connecting means for connecting the eccentric shaft portion to the shaft. The shaft has a lower half portion of the main shaft portion at a lower end of the main shaft portion and a lower end of the main shaft portion. An inclined pump part formed by a cylindrical cavity whose axis is inclined from the lower end toward the outer periphery is provided, and the lower end communicates with the vicinity of the upper end of the inclined pump part on the outer periphery of the upper half of the main shaft part, and the shaft is directed upward. A viscous pump portion engraved in a spiral shape while being inclined in the counter-rotating direction, one end communicating with the vicinity of the upper end of the viscous pump portion from the eccentric shaft portion to the sub shaft portion, and the other end of the sub shaft A vertical hole portion that is open to the vicinity of the upper end surface of the portion, andA sealing part that seals the upper end of the vertical hole part, and one endAboveIt communicates with the vertical hole and the other end isAboveExtends linearly in the direction of centrifugal force with respect to shaft rotationAboveOpen into the space inside the sealed containerLubricating oil discharge partWithIn the inclined pump section, the head can be obtained up to the lower end of the viscous pump section, and the upward hydraulic pressure generated by the viscous pump can stably transport a sufficient amount of lubricating oil that does not cover the lift of the vertical hole section,By sucking and pulling up the lubricating oil in the vertical hole part, the lubricating oil is released while the opening end of the lubricating oil discharge part extends in the centrifugal force direction, so the lubricating oil in the oil supply path is sucked up and pulled up, and the amount of oil supply is reduced. It has the effect of increasing.
[0030]
  Claim 11The invention described inLubricating oil is stored in a sealed container and an electric element and a compression element driven by the electric element are accommodated, and the compression element is provided coaxially up and down with an eccentric shaft portion and the eccentric shaft portion interposed therebetween. A shaft having a sub-shaft portion and a main shaft portion; a substantially cylindrical compression chamber; and a main bearing that is formed so as to be substantially orthogonal to the axial center of the compression chamber and supports the upper half of the main shaft portion. The cylinder block is fixed to or integrally formed with the cylinder block. A secondary bearing that pivotally supports the secondary shaft, a piston that reciprocates in the compression chamber, and a connecting means that connects the piston and the eccentric shaft, the shaft including the main shaft In the lower half of the shaft, there is provided a tilting pump portion formed by a cylindrical cavity having a throttle portion communicating with the lubricating oil at the lower end and an axial center inclined from the lower end of the main shaft portion toward the outer periphery. Provided on the outer periphery of the half portion is a viscous pump portion that has a lower end that communicates with the vicinity of the upper end of the inclined pump portion and is spirally engraved while being inclined upward in the counter-rotating direction of the shaft. One end is connected to the vicinity of the upper end of the viscous pump part, and the other end is provided with a vertical hole part that is open to the vicinity of the upper end surface of the auxiliary shaft part. Communicating with the vertical hole through a countershaft oiling passage The lower end as well as carved spirally while inclined in the counter rotational direction of the shaft towards having a countershaft lead groove communicates with the space in the closed containerIs,In the inclined pump section, the head can be obtained up to the lower end of the viscous pump section, and the upward hydraulic pressure generated by the viscous pump can stably transport a sufficient amount of lubricating oil that does not cover the head of the vertical hole section. ,Oil can be reliably supplied to the countershaft sliding section, and when the lubricating oil is discharged from the countershaft lead groove into the sealed container using the viscosity of the lubricant by rotation of the shaft, the piston and the sealed container It has the effect | action that it can serve as the oil supply to a piston and the thermal radiation from an airtight container by scattering.
[0031]
  Claim 12The invention described inClaims 1 to 11In the invention described in any one of the above, the inverter is driven at a plurality of operation frequencies including at least an operation frequency equal to or lower than the power supply frequency, and even when the rotational speed of the shaft is reduced at a low operation frequency operation It has the effect | action that the lubricating oil of each sliding part can be supplied through the oil supply path | route from an inclination pump to a vertical hole part through a viscous pump.
[0032]
  Claim 13The invention described inClaim 12In addition, the operation frequency below the power supply frequency includes at least an operation frequency of 30 Hz or less, and even in operation at a low operation frequency of 30 Hz or less, it is possible to ensure lubrication to the sliding portion. It has the action.
[0033]
DETAILED DESCRIPTION OF THE INVENTION
  Embodiments of a hermetic compressor according to the present invention will be described below with reference to the drawings. Na
In addition, about the same structure as the past, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.
[0034]
  (Embodiment 1)
  FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention, and FIG. 2 is a sectional view of a shaft of the hermetic compressor according to the first embodiment. FIG. 3 is an enlarged view of the lower end portion of the shaft of the hermetic compressor of the embodiment, and FIG. 4 shows the relationship between the rotational speed of the shaft of the hermetic compressor of the embodiment and the amount of oil supplied from the upper end of the auxiliary shaft. It is a graph.
[0035]
  In FIG. 1 to FIG. 3, reference numeral 101 denotes an airtight container that houses an electric element 105 composed of a stator 103 and a rotor 104 having a winding portion 103 a and a compression element 106 driven by the electric element 105. Reference numeral 108 denotes lubricating oil stored in the sealed container 101. The electric element 5 is driven by an inverter (not shown) at a plurality of operation frequencies including an operation frequency of 30 Hz or less and an operation frequency of 60 Hz or more.
[0036]
  Reference numeral 110 denotes a shaft, which is formed of a main shaft portion 111, an eccentric portion 112 provided eccentrically with the main shaft portion 111, and a sub shaft portion 113 provided coaxially with the main shaft portion 111 with the eccentric portion 112 interposed therebetween. The main shaft portion 111 includes an upper half portion 111a and a lower half portion 111b, and the rotor 104 is press-fitted and fixed to the lower half portion 111b. 116 isCylinder blockThe main bearing 118 has a substantially cylindrical compression chamber 117 and supports the upper half 111a of the main shaft 111, and a sub-bearing 119 that supports the sub-shaft 113 is fixed above. The compression chamber 117 is disposed so as to be substantially perpendicular to the main bearing 118 and the sub bearing 119.
[0037]
  120 is a pistonCylinder block116 is inserted into the compression chamber 117 so as to be slidable back and forth, and is connected to the eccentric portion 112 by a connecting rod 121 as a connecting means.
[0038]
  In the lower half part 111b of the shaft main shaft part 111, an inclined pump part 130 formed of a cylindrical cavity inclined by θ1 outwardly from the lower end with respect to the axis PC toward the upper side is provided. A flat plate-shaped divider 133 is press-fitted and fixed inside the inclined pump unit 130. A throttle portion 134 made of a flat plate-like cap having an introduction hole 134a in the rotational axis RC of the shaft 110 is press-fitted and fixed to the opening end in oil.
[0039]
  The restricting portion 134 is made of a material having a spring property, and is embedded in the shaft 110 using the spring property and can be easily assembled, and does not shift due to interference with other parts. Yes.
[0040]
  The upper half portion 111a of the shaft main shaft portion 111 has a lower end communicating with the vicinity of the upper end of the inclined pump portion 130, and a viscous pump engraved in a spiral shape while being inclined in the counter-rotating direction of the shaft 110 upward. A portion 131 is formed.
[0041]
  Further, from the eccentric part 112 of the shaft 110 to the auxiliary shaft part 113, a vertical hole part 132 having one end communicating with the vicinity of the upper end of the viscous pump part 130 and the other end communicating with the vicinity of the upper end surface of the auxiliary shaft part 113 is provided. is there.
[0042]
  The vertical hole portion 132 is provided with a communication hole 112 a to the eccentric portion 112 sliding portion and a counter shaft oil supply passage 113 a that opens to the inner periphery of the sub bearing 119.
[0043]
  137a is a vent hole for communicating the upper end of the inclined pump part 130 and the space 102 in the sealed container 101;137cIs a vent hole for communicating between the middle of the inclined pump part 130 and the space 102 in the sealed container 101,137bIs a vent hole for communicating the vertical hole 132 and the space 102 in the sealed container 1.
[0044]
  The refrigerant used in the compressor is a hydrocarbon-based refrigerant that is a natural refrigerant having a low global warming coefficient represented by, for example, R134a and R600a having an ozone depletion coefficient of zero. Combined.
[0045]
  The operation of the hermetic compressor configured as described above will be described below.
[0046]
  The rotor 104 of the electric element 105 rotates the shaft 110, and the rotational movement of the eccentric portion 112 is transmitted to the piston 120 via the connecting means 121, so that the piston 120 reciprocates in the compression chamber 117. At this time, the lubricating oil 108 in the inclined pump unit 130 is also rotated together with the shaft 110 by the rotation of the shaft 110, and a centrifugal force acts on the lubricating oil 108. At this time, the divider 133 prevents the lubricating oil 108 from slipping in the rotation direction of the lubricating oil 108 in the inclined pump unit 130. Therefore, the lubricating oil rotates at the same speed as the rotational speed of the shaft 110, so that centrifugal force is effectively generated and acted on. To do. The lubricating oil 108 flowing in from the introduction hole 134a receives an acting force in the direction of the centrifugal force in the inclined pump part 130, and is divided into the upward direction A and the downward direction B in the inclined pump part 130, but is pressed in the downward direction B. The lubricating oil 108 that has been moved cannot be moved by the throttle portion 134, and the lubricating oil conveying force in the upward direction C is mainly generated. In addition, since the inclined pump part 130 is inclined upward by the angle θ1 in the centrifugal force direction, the lubricating oil 108 on which the centrifugal force acts gains lift and moves up in the inclined pump part 130 in an oblique direction. Transport in the direction is made. Therefore, a much higher head can be obtained as compared with the type in which the lubricating oil 108 is conveyed in a direction perpendicular to the centrifugal force direction as in the concentric pump shown in the conventional example.
[0047]
  Next, the lubricating oil 108 that reaches the top of the inclined pump unit 130 is introduced into the viscous pump unit 131. Since the lead groove of the viscous pump 131 is inclined in the same direction as the inertial force acting in the direction opposite to the shaft rotation direction, a new upward conveying force acts on the lubricating oil. This makes it possible to obtain a much larger upward thrust than the vertical hole 15 in the main shaft portion 11 that does not have the upward thrust shown in the conventional example. The lubricating oil 108 reaching the upper end of the viscous pump part 131 is introduced into the vertical hole part 132. The lubricating oil 108 in the vertical hole portion 132 is pushed up by the upward driving force of the viscous pump portion 131, and the lubricating oil 108 is discharged from the opening at the upper end of the shaft 110. As a result, oil is supplied to the countershaft portion 113 located at the highest position in each sliding portion of the shaft 110.
[0048]
  By the way, the double-end bearing type hermetic compressor has a countershaft portion 113, and the oil supply path from the lower pump portion of the shaft 110 to the upper end of the shaft 110 is structurally extended compared to the cantilever type. Therefore, the behavior of the lubricating oil 108 passing through the oil supply path of the shaft immediately after the start of the compressor is inclined by the foaming and vaporization of the refrigerant dissolved in the lubricating oil by the stirring by the rotation of the shaft and the pressure reduction in the sealed container 101. Gas is easily held in the pump unit 130 and the viscous pump 131, and there is a high possibility that oil supply will be hindered by so-called gas biting.
[0049]
  However, at this time, in the refrigerant gas due to foaming or the like in the inclined pump portion 130, the gas vent holes 137a and137cFor venting gas from the viscous pump section 131 and the vertical hole section 132 with respect to the refrigerant gas.137bTherefore, the gas supply is avoided and the oil supply path is filled with the lubricating oil, so that it is possible to obtain the lift of the lubricating oil in the viscous pump and to prevent the oil supply failure.
[0050]
  According to the present embodiment, as shown in FIG. 4, the conventional combination of the concentric pumps 14 can hardly supply oil, and even in an operation in a low speed region such as 20 r / s, a sufficient amount of oil can be supplied. It turns out that you can get. In addition, since the amount of refrigerant dissolved in the lubricating oil is large, the combination of R600a or R290 and mineral oil, which is prone to hindering oil supply due to gas retention, and the combination of R134a and ester oil, ensure sufficient and sufficient oil supply.
I was able to get the amount. In addition, in the operation using a low-viscosity lubricating oil such as a viscosity of 8 to 10 [cts] in which the lubricity is lowered in addition to the combination of the lubricating oil and the refrigerant having a large amount of refrigerant dissolved in the lubricating oil as described above. A sufficient amount of oil could be obtained reliably. Therefore, it is difficult to use the conventional concentric pump 14 in combination, which is easy to dissolve in lubricating oil and uses low-viscosity lubricating oil, and lubrication in low-periphery operation that enables operation in a lower speed range. In order to be stable, the power consumption of the refrigeration system can be dramatically reduced.
(Embodiment 2)
  FIG. 5 is a cross-sectional view of a shaft of a hermetic compressor according to Embodiment 2 of the present invention. FIG. 6 is a top view of the shaft of the hermetic compressor according to the embodiment. The basic configuration of the hermetic compressor in the present embodiment is the same as that shown in FIG.
[0051]
  5 and 6, the shaft 110 includes a main shaft portion 111 and a sub shaft portion 113 sandwiching the eccentric portion 112. The main shaft portion 111 has an upper half portion 111a and a lower half portion 111b, and the lower half portion 111b includes A tilting pump unit 130 including a divider 133 and a throttle unit 134 is provided, and a viscous pump 131 is formed in the upper half. The vertical hole portion 135 communicates with the vicinity of the upper end of the viscous pump portion 130 and the lower portion 135a, and communicates into the sealed container 101 from the upper end of the shaft 110 with the upper portion 135b. Further, the vertical hole portion 135 is provided with a communication hole 112 a to the sliding portion of the eccentric portion 112 and a secondary shaft oil supply passage 113 a to the sliding portion of the secondary shaft portion 113. Further, the vertical hole 135 is inclined by θ2 in the centrifugal force direction toward the upper end of the shaft. In the shaft 110, an oil supply path that is connected from the lower end to the upper end is formed by the inclined pump portion 130, the viscous pump 131, and the vertical hole portion 135.
[0052]
  The operation of the hermetic compressor configured as described above will be described below. Accordingly, the lubricating oil in the vertical hole portion 135 can obtain an upward propulsive force due to the centrifugal force by the rotation of the shaft 110, and the propulsion in the upward direction is larger than the vertical hole portion 132 that rises at right angles to the centrifugal force. You can gain power. As a result, the amount of lubricating oil dissipated in the sealed container is increased, heat dissipation is improved, low-viscosity refrigerants that are easy to dissolve in the lubricating oil, and operation at lower speeds are possible. Since the oil supply in the lower peripheral edge operation becomes more stable, the reliability of the hermetic compressor is improved.
(Embodiment 3)
  FIG. 7 is a top view of the shaft of the hermetic compressor according to the third embodiment of the present invention. The basic configuration of the hermetic compressor in the present embodiment is the same as in FIG. 1, and the basic configuration of the shaft is the same as in FIG. 2 or FIG.
[0053]
  In FIG. 7, the vertical hole portion 136 communicates with the vicinity of the upper end of the viscous pump portion 130 at the lower portion 136a, and communicates into the sealed container 101 from the upper end of the shaft 110 at the upper portion 136b. Further, the vertical hole 136 is inclined in the same direction as the inertial force acting in the direction opposite to the rotation direction of the shaft 110.
[0054]
  The operation of the hermetic compressor configured as described above will be described. The lubricating oil 108 pumped up to the upper end of the viscous pump by the rotation of the shaft 110 has an upward conveying force due to the inclination of the vertical hole 136. As a result, the amount of lubricating oil dissipated in the sealed container is increased, heat dissipation is improved, low-viscosity refrigerants that are easy to dissolve in the lubricating oil, and operation at lower speeds are possible. Therefore, the refueling in the low peripheral edge operation becomes more stable, so that the power consumption of the refrigeration system can be drastically reduced, and the reliability of the hermetic compressor is improved.
In a combination in which the vertical hole portion is inclined in the centrifugal force direction toward the upper end of the shaft and is inclined in the counter-rotating direction of the shaft 110, the lubricating oil further exerts a strong upward conveying force due to a synergistic effect. .
[0055]
  (Embodiment 4)
  FIG. 8 is a cross-sectional view of an essential part of a shaft of a hermetic compressor according to Embodiment 4 of the present invention. The basic configuration of the hermetic compressor in the present embodiment is the same as in FIG. 1, and the basic configuration of the shaft is the same as in FIG. 2 or FIG.
[0056]
  In FIG. 8, reference numeral 138 denotes a lubricating oil discharge lateral hole that communicates the vertical hole portion 132 and the inside of the sealed container 101, and is provided above the auxiliary shaft portion 113.
[0057]
  The operation of the hermetic compressor configured as described above will be described. First, the lubricating oil 108 conveyed to the vertical hole portion 132 by the rotation of the shaft 110 is supplied to the sliding portion of the auxiliary shaft portion 113 through the auxiliary shaft oil supply passage 113a, and then the excess lubricating oil is discharged. It is discharged from the lateral hole 138 to the sealed container 101.
[0058]
  At this time, the configuration shown in the conventional example is characterized in that the lubricating oil is diffused to the sealed container 1 along the wall surface of the auxiliary bearing 19. In addition, since the amount of oil supplied from the vertical hole portion 15 is also reduced, the momentum to dissipate the lubricating oil from the upper end of the shaft 10 is reduced, and there is a possibility that a state in which the airtight container cannot be dissipated due to the surface tension of the wall surface of the auxiliary bearing 19 may occur. .
[0059]
  However, even when such an oil supply path is long, the lubricating oil discharge lateral hole 138 exhibits the effect of rectifying the lubricating oil discharged, and can be dissipated in the centrifugal force direction (branch D) so as not to be dispersed from one place. Therefore, the lubricating oil can be reliably dissipated into the sealed container without being dispersed by the surface tension on the wall surface of the auxiliary bearing 119 part. Therefore, cooling of the lubricating oil is promoted and reliability can be improved, and the lubricating oil is sealed even when the centrifugal force is small and the swinging force of the lubricating oil is low, such as during low frequency operation. It can be released into the container 101.
[0060]
  Next, FIG. 9 is a sectional view of an essential part of a shaft according to another example of the hermetic compressor according to the embodiment.
[0061]
  In FIG. 9, reference numeral 139 denotes a communication common hole which is formed in the direction of the centrifugal force with respect to the rotation of the shaft. One end communicates with the vertical hole portion 132, and the other end communicates with the inner circumference of the auxiliary bearing 119 and the space inside the sealed container 101. Open to both.
[0062]
  The lubricating oil 108 conveyed to the vertical hole portion by the rotation of the shaft 110 passes through the communication common hole 139 and a part thereof is supplied to the inner periphery of the auxiliary bearing 119 to lubricate the sliding portion between the auxiliary bearing 119 and the auxiliary shaft portion 113. In addition, a part of the tributary E is opened to the atmosphere in the sealed container 101 to cool the lubricating oil, and the volumetric efficiency is improved by improving the lubricating oil sealability between the piston 120 and the cylinder 116 by the lubrication to the piston 120. Improvement can be achieved. Therefore, it is possible to share the countershaft lubrication, the lubricating oil cooling, and the splashing of the lubricating oil to the sliding part of the piston 120 with one hole, so that the cost increase due to an increase in the number of machining points can be avoided. It is possible to provide a highly efficient and highly reliable compressor while achieving the above.
[0063]
  (Embodiment 5)
FIG. 10 is a cross-sectional view of a main part of the shaft of the hermetic compressor according to the fifth embodiment of the present invention. The basic configuration of the hermetic compressor in the present embodiment is the same as in FIG. 1, and the basic configuration of the shaft is the same as in FIG. 2 or FIG.
[0064]
  In FIG. 10, 140 isLubricating oil discharge partThe one end is press-fitted and opened at the upper end of the vertical hole portion 132, and the other end extends into the sealed container 101 in the direction of the centrifugal force generated by the rotation of the shaft 110.
[0065]
  The operation of the hermetic compressor configured as described above will be described. The lubricating oil 108 conveyed from the inclined pump part 130 to the vertical hole part by the rotation of the shaft 110 isLubricating oil discharge partA centrifugal force works at a portion extending in the centrifugal force direction of 140, and an action of sucking the lubricating oil works.
[0066]
  By this action, the lubricating oil in the vertical hole portion 132 isLubricating oil discharge partThe gas of the viscous pump unit 132 that has been stagnated by being sucked by 140 and pulled upward has the effect of being drawn out at the same time. Therefore, gas jamming can be prevented even with a long oil supply path such as a double-sided bearing type, and stable oil supply characteristics equivalent to those of the cantilever type can be secured. In addition, a refrigerant that is easy to dissolve in the lubricating oil and uses a low-viscosity lubricating oil or a low-end-of-circumference operation that enables operation at lower speeds is more stable, so drastically reduced power consumption of the refrigeration system In addition, the reliability of the hermetic compressor is improved.
[0067]
  (Embodiment 6)
  FIG. 11 is a cross-sectional view of the shaft of the hermetic compressor according to the sixth embodiment. The basic configuration of the hermetic compressor in the present embodiment is the same as in FIG. 1, and the basic configuration of the shaft is the same as in FIG. 2 or FIG.
[0068]
  In FIG. 11, 141 isLubricating oil discharge partThen, it is press-fitted into the lubricating oil discharge lateral hole and extends into the sealed container 101 in the direction of the centrifugal force due to the rotation of the shaft 110. 141a is a sealing portion at the upper end of the vertical hole portion 132, and is formed of a cap-shaped metal pressed part.
[0069]
  In the configuration as described above, the lubricating oil 108 conveyed to the vertical hole portion by the rotation of the shaft 110 is conveyed to the lubricating oil discharge portion 141. In the conveyed lubricating oil 108,Lubricating oil discharge partSince 141 extends in the centrifugal force direction, the centrifugal force works and sucks the lubricating oil.
[0070]
  By this action, the lubricating oil in the vertical hole portion 132 isLubricating oil discharge partThe gas of the viscous pump unit 132 that has been stagnated by being suctioned by the nozzle 141 and pulled upward is also pulled out at the same time. Therefore, gas jamming can be prevented even with a long oil supply path such as a double-sided bearing type, and stable oil supply characteristics equivalent to those of the cantilever type can be secured. In addition, a refrigerant that is easy to dissolve in the lubricating oil and uses a low-viscosity lubricating oil or a low-end-of-circumference operation that enables operation at lower speeds is more stable, so drastically reduced power consumption of the refrigeration system In addition, the reliability of the hermetic compressor is improved.
[0071]
  This configuration is furtherLubricating oil discharge partHowever, the cost can be reduced because it can be constituted by inexpensive parts such as a straight pipe with relatively little processing.
[0072]
  (Embodiment 7)
  FIG. 12 is a detailed view of the shaft countershaft portion of the hermetic compressor according to the seventh embodiment. The basic configuration of the hermetic compressor in the present embodiment is the same as in FIG. 1, and the basic configuration of the shaft is the same as in FIG. 2 or FIG.
[0073]
  In FIG. 12, reference numeral 142 denotes a countershaft lead groove, which is engraved on the outer periphery of the countershaft portion 113, communicates with the subshaft oil supply passage 113a, and opens at the bottom of the subshaft portion 113 and opens into the space inside the subshaft sealed container 101. 142a. The lead groove 142 is inclined in the counter-rotating direction of the shaft 110 downward from the countershaft oil supply passage 113a and has a spiral shape.
[0074]
  In the configuration as described above, the lubricating oil 108 conveyed to the vertical hole portion 132 by the rotation of the shaft 110 is first conveyed to the oil supply passage 113 a of the auxiliary shaft portion 113 and then fed to the lead groove 142. At this time, the lead groove 142 is upward with respect to the rotation direction of the shaft 110.
Therefore, the lubricating oil 108 is pushed downward through the lead groove 142, and is discharged into the sealed container 101 from the communicating end 142a with the sealed container 101 into the sealed container 101 as shown in the tributary G. Controls refueling of the piston 120. Therefore, as the lead groove 142 rotates, the entire circumference of the sliding portion of the auxiliary shaft 113 can be lubricated, and the reliability of the sliding portion of the auxiliary shaft 113 is further improved and good even during low-speed rotation operation. Heat radiation is obtained, and the sliding portion of the piston 120 is more reliably lubricated, whereby a highly reliable hermetic compressor can be obtained. In addition, a refrigerant that is easy to dissolve in the lubricating oil and uses a low-viscosity lubricating oil or a low-end-of-circumference operation that enables operation at lower speeds is more stable, so drastically reduced power consumption of the refrigeration system In addition, the reliability of the hermetic compressor is improved.
[0075]
【The invention's effect】
  As described above, according to the first aspect of the present invention, the shaft has a throttle portion communicating with the lubricating oil at the lower half portion of the main shaft portion at the lower end and an outer periphery from the lower end of the main shaft portion. An inclined pump part formed by a cylindrical cavity having an inclined axis toward the center is provided, and the lower end communicates with the vicinity of the upper end of the inclined pump part on the outer periphery of the upper half of the main shaft part, and the shaft rotates counterclockwise. A viscous pump part that is spirally engraved in a direction, and has one end communicating with the vicinity of the upper end of the viscous pump part from the eccentric shaft part to the auxiliary shaft part, and the other end above the auxiliary shaft part. By providing a vertical hole part that opens in the vicinity of the end face, the inclined pump part can obtain a lift to the lower end of the viscous pump part, and the upward hydraulic pressure generated by the viscous pump does not cover the lift of the vertical hole part. A stable amount of lubricating oil Can.
[0076]
  Further, the invention according to claim 2 is the same as that according to claim 1, wherein the vertical hole portion is further inclined from the bottom to the top and away from the rotation center axis of the shaft. An upward conveying force can be generated, and a sufficient amount of lubricating oil can be conveyed.
[0077]
  The invention according to claim 3 is the invention according to claim 1, wherein the vertical hole portion is inclined in the direction opposite to the rotation direction of the shaft from the bottom to the top, and the vertical hole portion is also conveyed upward. Force can be generated, and a sufficient amount of lubricating oil can be conveyed.
[0078]
  The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein the throttle portion is inserted and locked with a disk-shaped cap in the inclined pump portion. It is possible to prevent the throttle part from swinging with respect to the rotation axis due to the mounting at the time of assembly, so that stable oil supply can be secured, and the structure is less expensive than the structure in which the cylindrical part provided with the throttle part is not added in the longitudinal direction. The length of the shaft main shaft portion can be shortened.
[0079]
  The invention described in claim 5 is characterized in that, in addition to the invention described in any one of claims 1 to 3, a flat plate divider is inserted and locked in the inclined passage. In addition, since slippage in the rotational direction of the lubricating oil is suppressed in the inclined pump portion, centrifugal force effectively acts on the lubricating oil in the inclined pump portion particularly in the low speed rotation region, and a stronger upward conveying force is generated.
[0080]
  The invention according to claim 6 is the bearing according to any one of claims 1 to 3, further comprising a bearing on a path from the cylindrical cavity portion of the inclined pump portion to the upper opening of the vertical hole portion. At least one vent hole communicating with the space inside the sealed container without passing through the section
In the oil supply mechanism with a long oil supply path, the refrigerant gas mixed at the start of the compressor and the gas vaporized from the lubricating oil are effectively released to the sealed container space, so that the lubricating oil in the oil supply path Do not interrupt the upward conveying force that is generated.
[0081]
  The invention according to claim 7 is the invention according to any one of claims 1 to 3, further comprising a shaft.Secondary shaftOne end opens into the vertical hole and the other end is above or below the auxiliary bearing.
The side wall communicates with the space inside the sealed container, and a lubricating oil discharge lateral hole is formed in the direction of the centrifugal force with respect to the rotation of the shaft. The centrifugal force is effectively applied to the lubricating oil in the lubricating oil discharge side hole. When it is generated and rectified and discharged, the discharge direction becomes constant and scattering to the sealed container is ensured.
[0082]
  The invention according to an eighth aspect is the same as that according to any one of the first to third aspects, wherein the one end is opened in the vertical hole portion and the other end is opened in the inner circumference of the auxiliary bearing. It has a shaft oil supply path, and reliability is improved by reliably supplying oil to the sliding portion between the auxiliary shaft portion and the auxiliary bearing.
[0083]
  The invention according to claim 9 is the invention according to any one of claims 1 to 3, wherein one end is opened in the vertical hole portion, and the other end is in the auxiliary bearing inner periphery and the sealed container. The communication common hole opened in both the space is provided, and the shaft with a reduced number of processing steps can be used to supply oil to the auxiliary shaft and discharge to the piston and the sealed container through the same hole.
[0084]
  The invention according to claim 10 is the invention according to any one of claims 1 to 3, further comprising one end communicating with the upper end of the shaft vertical hole portion and the other end against rotation of the shaft. It has a lubricating oil discharge part that extends while curving in the direction of the centrifugal force and opens into the space inside the sealed container. By sucking and pulling up the lubricating oil in the vertical hole, it is also sucked into the lubricating oil in the viscous pump part. Since the opening end of the lubricating oil discharge part releases the lubricating oil in the centrifugal force direction, the amount of oil supply increases.
[0085]
  According to an eleventh aspect of the present invention, in addition to the invention according to any one of the first to third aspects, a sealing portion that seals the upper end of the shaft vertical hole portion, and one end of the shaft vertical hole portion. The other end extends linearly in the direction of centrifugal force with respect to the rotation of the shaft and opens into the space inside the sealed containerLubricating oil discharge partSince the opening end of the lubricating oil discharge part extends in the centrifugal force direction by sucking and pulling up the lubricating oil in the vertical hole part, the lubricating oil in the oil supply path is sucked in. This will increase the amount of oil.
[0086]
  According to a twelfth aspect of the present invention, in addition to the invention according to any one of the first to third aspects of the present invention, the shaft countershaft portion has an outer periphery, one end communicating with the subshaft oil supply passage, and the other end sealed. It is provided with a spiral countershaft lead groove that opens in the inner space, and can reliably supply oil to the countershaft sliding portion and also uses the viscosity of the lubricant by rotation of the shaft. When discharging into the sealed container from the countershaft lead groove, the oil can be supplied to the piston and radiated from the sealed container by scattering to the piston and the sealed container.
[0087]
  The invention described in claim 13 is driven by an inverter at a plurality of operation frequencies including at least an operation frequency equal to or lower than the power supply frequency in addition to the invention described in any one of claims 1 to 12. Even when the rotational speed of the shaft is reduced in the low operation frequency operation, the lubricating oil of each sliding portion can be supplied from the inclined pump through the viscous pump through the oil supply path to the vertical hole portion.
[0088]
  The invention described in claim 14 includes the invention described in claim 13 and further includes an operation frequency of at least 30 Hz in the operation frequency below the power supply frequency, and also at low operation frequency operation at 30 Hz or less. Oil supply to the sliding part can be ensured.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention.
FIG. 2 is a side view of the shaft of the hermetic compressor according to the embodiment.
FIG. 3 is an enlarged view of the lower end of the shaft of the hermetic compressor according to the embodiment.
FIG. 4 is a characteristic diagram showing an oil supply characteristic of the hermetic compressor according to the embodiment.
FIG. 5 is a sectional view of a shaft of a hermetic compressor according to a second embodiment of the present invention.
6 is a top view of the shaft of the hermetic compressor according to the embodiment. FIG.
FIG. 7 is a top view of a shaft of a hermetic compressor according to a third embodiment of the present invention.
FIG. 8 is a cross-sectional view of a main part of a shaft of a hermetic compressor according to a fourth embodiment of the present invention.
FIG. 9 is a sectional view of an essential part of a shaft of the hermetic compressor according to the embodiment.
FIG. 10 is a cross-sectional view of main parts of a shaft of a hermetic compressor according to a fifth embodiment of the present invention.
FIG. 11 is a cross-sectional view of an essential part of a shaft of a hermetic compressor according to a sixth embodiment of the present invention.
12 is a detailed view of a shaft countershaft portion of a hermetic compressor according to a seventh embodiment of the present invention. FIG.
FIG. 13 is a longitudinal sectional view of a conventional hermetic compressor
FIG. 14 is a top view of a conventional hermetic compressor.
FIG. 15 is a sectional view of a lower part of a conventional hermetic compressor shaft.
FIG. 16 is a cross-sectional view of a main part of a shaft countershaft of a conventional hermetic compressor.
[Explanation of symbols]
101 Airtight container
105 Electric elements
106 Compression element
108 Lubricating oil
110 shaft
111 Spindle part
112 Eccentric shaft
113 Countershaft
113a Countershaft oil supply passage
116 Cylinder block
117 Compressor
118 Main bearing
119 Secondary bearing
120 piston
121 connection means
130 Tilting pump part
131 Viscosity pump
132 Vertical hole
135 Vertical hole
136 Longitudinal hole
137a vent hole
137b vent hole
137c vent hole
138 Lubricating oil discharge horizontal hole
139 Communication hole
140Lubricating oil discharge part
141Lubricating oil discharge part
141a Sealing part
142 Counter shaft lead groove

Claims

密閉容器内に潤滑油を貯溜するとともに電動要素と前記電動要素によって駆動される圧縮要素を収容し、前記圧縮要素は偏芯軸部と前記偏芯軸部を挟んで上下に同軸状に設けた副軸部および主軸部とを有したシャフトと、略円筒形の圧縮室と前記圧縮室の軸心と略直交するように形成され前記主軸部の上半部を軸支する主軸受とを備えたシリンダブロックと、前記シリンダブロックに固定されるか又は一体に形成され前記副軸部を軸支する副軸受と、前記圧縮室内で往復運動するピストンと、前記ピストンと前記偏芯軸部とを連結する連結手段とを備えており、前記シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設け、前記縦孔部は下から上に向けて前記シャフトの回転方向と反対方向に傾斜した密閉型圧縮機。Lubricating oil is stored in a sealed container and an electric element and a compression element driven by the electric element are accommodated, and the compression element is provided coaxially up and down with an eccentric shaft portion and the eccentric shaft portion interposed therebetween. A shaft having a sub-shaft portion and a main shaft portion; a substantially cylindrical compression chamber; and a main bearing that is formed so as to be substantially orthogonal to the axial center of the compression chamber and supports the upper half of the main shaft portion. A cylinder block, a sub-bearing fixed to or integrally formed with the cylinder block and pivotally supporting the sub-shaft portion, a piston reciprocating in the compression chamber, and the piston and the eccentric shaft portion. Connecting means for connecting, and the shaft has a throttle portion communicating with the lubricating oil at the lower half portion of the main shaft portion at the lower end, and the shaft center is inclined from the lower end of the main shaft portion toward the outer periphery. Inclined pump formed by a cylindrical cavity A viscous pump part that is spirally engraved on the outer periphery of the upper half part of the main shaft part, with the lower end communicating with the vicinity of the upper end of the inclined pump part and being inclined upward in the counter-rotating direction of the shaft. A vertical hole portion having one end communicating with the vicinity of the upper end of the viscous pump portion and the other end communicating with the vicinity of the upper end surface of the auxiliary shaft portion from the eccentric shaft portion to the sub shaft portion; The hermetic compressor in which the hole is inclined in the direction opposite to the rotation direction of the shaft from the bottom to the top .

縦孔部は下から上に向けてシャフトの回転中心軸から遠ざかる方向へ傾斜した請求項１に記載の密閉型圧縮機。 The hermetic compressor according to claim 1, wherein the vertical hole portion is inclined in a direction away from the rotation center axis of the shaft from the bottom to the top.

絞り部は円板状の部材からなる請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。The hermetic compressor according to any one of claims 1 to 2 , wherein the throttle portion is made of a disk-shaped member.

傾斜通路内に平板状のデバイダーを挿入係止した請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。The hermetic compressor according to any one of claims 1 to 2 , wherein a flat plate divider is inserted and locked in the inclined passage.

傾斜ポンプ部の円筒空洞部から縦孔部の上部開口に至る経路上に密閉容器内空間と連通する少なくとも１つ以上のガス抜き孔を設けた請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。The at least 1 or more degassing hole connected with the space in the airtight container was provided in the path | route from the cylindrical cavity part of an inclination pump part to the upper opening of a vertical hole part in any one of Claim 1 to 2 The hermetic compressor as described.

シャフトの副軸部において、一端が縦孔部に開口し、他端が副軸受の上部または下部で密閉容器内空間と連通し、前記シャフトの回転に対して遠心力方向に潤滑油放出横孔を穿設した請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。In the countershaft portion of the shaft, one end opens into the vertical hole portion , the other end communicates with the space inside the sealed container at the upper or lower portion of the subbearing, and the lubricating oil discharge horizontal hole in the centrifugal force direction with respect to the rotation of the shaft The hermetic compressor according to any one of claims 1 to 2, wherein a bore is formed.

一端が縦孔部に開口し、他端が副軸受内周に開口する副軸給油路を設けた請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。The hermetic compressor according to any one of claims 1 to 2 , wherein a countershaft oil supply passage having one end opened in the vertical hole portion and the other end opened in the inner periphery of the sub-bearing is provided.

一端が縦孔部に開口し、他端が副軸受内周と密閉容器内空間との双方に開口した連通共用孔を設けた請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。The sealed mold according to any one of claims 1 to 2 , wherein a communication common hole having one end opened in the vertical hole portion and the other end opened in both the inner circumference of the auxiliary bearing and the space in the sealed container. Compressor.

一端がシャフト縦孔部上端と連通し、他端がシャフトの回転に対して遠心力方向に延出し、密閉容器内空間に開口する潤滑油放出部を備えた請求項１から請求項２のいずれか１項に記載の密閉型圧縮機。 3. The lubricating oil discharge part according to claim 1, further comprising a lubricating oil discharge part having one end communicating with an upper end of the shaft vertical hole part and the other end extending in a centrifugal force direction with respect to the rotation of the shaft and opening into the space in the sealed container. The hermetic compressor according to claim 1.

密閉容器内に潤滑油を貯溜するとともに電動要素と前記電動要素によって駆動される圧縮要素を収容し、前記圧縮要素は偏芯軸部と前記偏芯軸部を挟んで上下に同軸状に設けた副軸部および主軸部とを有したシャフトと、略円筒形の圧縮室と前記圧縮室の軸心と略直交するように形成され前記主軸部の上半部を軸支する主軸受とを備えたシリンダブロックと、前記シリンダブロックに固定されるか又は一体に形成され前記副軸部を軸支する副軸受と、前記圧縮室内で往復運動するピストンと、前記ピストンと前記偏芯軸部とを連結する連結手段とを備えており、前記シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設け、さらに前記縦孔部の上端を封止する封止部と、一端が前記縦孔部と連通し、他端が前記シャフトの回転に対して遠心力方向に直線的に延出し前記密閉容器内の空間に開口する潤滑油放出部を備えた密閉型圧縮機。 Lubricating oil is stored in a sealed container and an electric element and a compression element driven by the electric element are accommodated, and the compression element is provided coaxially up and down with an eccentric shaft portion and the eccentric shaft portion interposed therebetween. A shaft having a sub-shaft portion and a main shaft portion; a substantially cylindrical compression chamber; and a main bearing that is formed so as to be substantially orthogonal to the axial center of the compression chamber and supports the upper half of the main shaft portion. A cylinder block, a sub-bearing fixed to or integrally formed with the cylinder block and pivotally supporting the sub-shaft portion, a piston reciprocating in the compression chamber, and the piston and the eccentric shaft portion. Connecting means for connecting, and the shaft has a throttle portion communicating with the lubricating oil at the lower half portion of the main shaft portion at the lower end, and the shaft center is inclined from the lower end of the main shaft portion toward the outer periphery. Inclined pump formed by a cylindrical cavity A viscous pump part that is spirally engraved on the outer periphery of the upper half part of the main shaft part, with the lower end communicating with the vicinity of the upper end of the inclined pump part and being inclined upward in the counter-rotating direction of the shaft. Provided from the eccentric shaft portion to the sub-shaft portion, one end communicated with the vicinity of the upper end of the viscous pump portion, and the other end provided with a vertical hole portion opened in communication with the vicinity of the upper end surface of the sub-shaft portion; and a sealing portion for sealing the top end of the vertical hole portion, one end communicating with said vertical hole portion, the space of the other end is linearly extended out the closed vessel to the centrifugal force direction with respect to the rotation of said shaft A hermetic compressor having an opening for releasing a lubricating oil .

密閉容器内に潤滑油を貯溜するとともに電動要素と前記電動要素によって駆動される圧縮要素を収容し、前記圧縮要素は偏芯軸部と前記偏芯軸部を挟んで上下に同軸状に設けた副軸部および主軸部とを有したシャフトと、略円筒形の圧縮室と前記圧縮室の軸心と略直交するように形成され前記主軸部の上半部を軸支する主軸受とを備えたシリンダブロックと、前記シリンダブロックに固定されるか又は一体に形成され前記副軸部を軸支する副軸受と、前記圧縮室内で往復運動するピストンと、前記ピストンと前記偏芯軸部とを連結する連結手段とを備えており、前記シャフトには、前記主軸部の下半部に、前記潤滑油に連通する絞り部を下端に有するとともに前記主軸部の下端から外周に向かい軸心が傾斜した円筒空洞で形成した傾斜ポンプ部を設け、前記主軸部の上半部外周に、下端が前記傾斜ポンプ部の上端近傍と連通し、上方に向かって前記シャフトの反回転方向に傾斜しながら螺旋状に刻設した粘性ポンプ部を設け、前記偏芯軸部から前記副軸部にかけて、一端が前記粘性ポンプ部上端近傍と連通し、他端が前記副軸部の上端面近傍に連通開口した縦孔部とを設け、さらに前記副軸部外周において、一端が副軸給油路を介して前記縦孔部と連通し下方に向って前記シャフトの反回転方向に傾斜しながら螺旋状に刻設するとともに下端が前記密閉容器内の空間と連通した副軸リード溝を備えた密閉型圧縮機。 Lubricating oil is stored in a sealed container and an electric element and a compression element driven by the electric element are accommodated, and the compression element is provided coaxially up and down with an eccentric shaft portion and the eccentric shaft portion interposed therebetween. A shaft having a sub-shaft portion and a main shaft portion; a substantially cylindrical compression chamber; and a main bearing that is formed so as to be substantially orthogonal to the axial center of the compression chamber and supports the upper half of the main shaft portion. A cylinder block, a sub-bearing fixed to or integrally formed with the cylinder block and pivotally supporting the sub-shaft portion, a piston reciprocating in the compression chamber, and the piston and the eccentric shaft portion. Connecting means for connecting, and the shaft has a throttle portion communicating with the lubricating oil at the lower half portion of the main shaft portion at the lower end, and the shaft center is inclined from the lower end of the main shaft portion toward the outer periphery. Inclined pump formed by a cylindrical cavity A viscous pump part that is spirally engraved on the outer periphery of the upper half part of the main shaft part, with the lower end communicating with the vicinity of the upper end of the inclined pump part and being inclined upward in the counter-rotating direction of the shaft. Provided from the eccentric shaft portion to the sub-shaft portion, one end communicated with the vicinity of the upper end of the viscous pump portion, and the other end provided with a vertical hole portion opened in communication with the vicinity of the upper end surface of the sub-shaft portion; in the auxiliary shaft portion periphery, one end bottom while engraved spirally with inclined downwardly communicating with said vertical hole portion via a countershaft oil supply passage in the counter-rotational direction of the shaft of the sealed container A hermetic compressor with a countershaft lead groove communicating with the space.

少なくとも電源周波数以下の運転周波数を含む複数の運転周波数でインバーター駆動される請求項１から請求項１１のいずれか１項に記載の密閉型圧縮機。The hermetic compressor according to any one of claims 1 to 11 , wherein the hermetic compressor is driven by an inverter at a plurality of operation frequencies including at least an operation frequency equal to or lower than a power supply frequency.

電源周波数以下の運転周波数には少なくとも３０Ｈｚ以下の運転周波数を含む請求項１２記載の密閉型圧縮機。The hermetic compressor according to claim 12 , wherein the operating frequency below the power supply frequency includes an operating frequency of at least 30Hz.